JP2016188005A - Stroke simulator and fluid pressure generator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a stroke simulator which easily changes reaction force characteristics without increasing significant cost increase, and to provide a fluid pressure generator.SOLUTION: A stroke simulator 40 includes: a substrate 10 having a cylinder hole 41 having a closed bottom; a piston 42 inserted into the cylinder hole 41; a lid member 45 which closes an opening part of the cylinder hole 41; an elastic member which is disposed between the piston 42 and the lid member 45 and compressively deformed according to operation of a brake controller to generate a reaction force; and an electromagnetic actuator 450 attached to the substrate 10. The electromagnetic actuator 450 includes a pressing part which extends in a compression direction of the elastic member and may compress the elastic member.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a stroke simulator and a hydraulic pressure generator used for vehicles.

2. Description of the Related Art Conventionally, for example, a stroke simulator used in a by-wire type hydraulic pressure generator is described in Patent Document 1.
The stroke simulator of Patent Document 1 includes a first return spring, a second return spring, and a bush as a configuration for obtaining reaction force characteristics.
The elastic coefficient of the second return spring is set larger than the elastic coefficient of the first return spring. The elastic coefficient of the bush is set smaller than the elastic coefficient of the second return spring.

  According to the stroke simulator of Patent Document 1, when the operation amount of the brake operation member is large, the second return spring is mainly compressed and deformed. When the operation amount of the brake operation member is intermediate, the bush is compressed and deformed in parallel with the compressive deformation of the first return spring. As a result, the reaction force characteristic in the range near the switching point where the reaction force characteristic switches from the first return spring to the second return spring becomes the sum of the reaction force characteristics of the first return spring and the bush and becomes gentle. Therefore, the uncomfortable feeling at the time of brake operation can be alleviated in the vicinity of the switching point.

JP 2012-206711 A

  However, in the hydraulic pressure generator of Patent Document 1, when changing the reaction force characteristics of the stroke simulator so as to be soft or hard as a whole, for example, components such as return springs and bushes are different from each other with different characteristics. It is necessary to redesign the stroke simulator configuration. For this reason, there existed a subject that the change of reaction force characteristic will lead to a significant cost increase.

  It is an object of the present invention to provide a stroke simulator and a hydraulic pressure generator that can easily change the reaction force characteristics without incurring a significant cost increase.

  The stroke simulator of the present invention, which was created to solve such a problem, is a stroke simulator that applies a pseudo operation reaction force to a brake operator. The stroke simulator includes a base body having a bottomed cylinder hole, a piston inserted into the cylinder hole, and a lid member that closes an opening of the cylinder hole. The stroke simulator is disposed between the piston and the lid member, and an elastic member that generates a reaction force by being compressed and deformed according to the operation of the brake operator, and an electromagnetic actuator attached to the base body, It has. The electromagnetic actuator includes a pressing portion that extends in a compression direction of the elastic member and can compress the elastic member.

  In such a stroke simulator, when the electromagnetic actuator is operated, the pressing portion extends in the compression direction of the elastic member, and the elastic member is compressed. As a result of applying a load to the elastic member by this compression, the reaction force characteristic of the stroke simulator is changed. That is, according to the present invention, the reaction force characteristic of the stroke simulator can be changed only by operating the electromagnetic actuator.

  Moreover, when the said press part is a rod, it is good for the said rod to be arrange | positioned in the axial direction of the said cylinder hole. If it does in this way, a rod will move by operation of an electromagnetic actuator, and an elastic member will be pressed. As a result of applying a load to the elastic member by this pressing, the reaction force characteristic of the stroke simulator is changed. That is, according to the present invention, the reaction force characteristic of the stroke simulator can be changed with a simple configuration in which the elastic member is pressed by the rod.

  Further, when the electromagnetic actuator is disposed on the bottom side of the cylinder hole, the rod may be configured to press the elastic member via the electro-piston. If it does in this way, since it is comprised from the first and pushes a piston, an elastic member can be suitably pressed with a rod, without interposing a new receiving member etc. Therefore, an increase in cost can be suppressed.

  Moreover, the piston can be stably pressed by the rod by arranging the rod coaxially with the piston. Moreover, layout property also improves by arrange | positioning coaxially.

  The electromagnetic actuator includes a fixed core fixed to the base, a movable core provided to be movable with respect to the fixed core, and a coil that moves the movable core to the fixed core side, The rod may be configured to move integrally with the movable core. If it does in this way, the reaction force characteristic of an elastic member can be changed suitably by the electromagnetic simple structure which does not require a rotation conversion mechanism etc. when using a gear etc.

  Further, when the piston is formed in a substantially bottomed cylindrical shape, it is preferable that at least a part of the fixed core is accommodated in a space formed inside the piston. If it does in this way, at least one part of an electromagnetic actuator can be arranged and overlapped inside a piston, and space saving can be attained.

  Further, when the rod is movably supported on the fixed core via a seal member, a fluid pressure chamber formed in the cylinder hole and a region formed inside the electromagnetic actuator by the seal member; Should be partitioned liquid-tight. If it does in this way, the field where brake fluid does not flow in in an electromagnetic actuator can be formed.

  Moreover, it is good to provide the recessed part to which the said fixed core is attached to the bottom part of the said cylinder hole in the side part of the said base | substrate. If it does in this way, an electromagnetic actuator can be arranged near a piston, and space saving can be attained.

  The fixed core is preferably fixed to the base via a holding member. If it does in this way, the freedom degree of an installation position will increase. For example, the electromagnetic actuator can be installed using the structure originally provided in the stroke simulator.

  The hydraulic pressure generator includes a master cylinder that generates hydraulic pressure to be applied to a wheel brake by operation of the brake operator, and a slave that generates hydraulic pressure by an electric actuator that is driven according to an operation amount of the brake operator. And a cylinder. As described above, it is preferable to use a stroke simulator for a hydraulic pressure generating device including a master cylinder and a slave cylinder.

  Moreover, it is good to provide the operation input part which receives the operation input for operating the said electromagnetic actuator. If it does in this way, when there is a driver | operator's request | requirement by the operation input part, simulator characteristics can be changed easily.

  According to the present invention, it is possible to obtain a stroke simulator and a hydraulic pressure generator that can easily change the reaction force characteristics without causing a significant cost increase.

It is a mimetic diagram showing a vehicular brake system using a fluid pressure generator to which a stroke simulator concerning a 1st embodiment of the present invention is applied. It is a side view showing the fluid pressure generating device concerning a 1st embodiment of the present invention. It is a top view which similarly shows a hydraulic-pressure generator. It is a front view which similarly shows a hydraulic-pressure generator. It is a longitudinal cross-sectional view which follows the AA line of FIG. It is an expanded longitudinal cross-sectional view of the stroke simulator with which a hydraulic pressure generator is equipped. It is the schematic diagram which showed arrangement | positioning of the board | substrate along the BB line of FIG. (A) is a characteristic diagram showing a reaction force characteristic at normal time when the electromagnetic actuator is not operated, (b) is a characteristic diagram of a stroke simulator when the electromagnetic actuator is operated, and (c) is a characteristic diagram of (a). It is the figure which arranged and showed the characteristic view of (b). (A) (b) is explanatory drawing which shows operation | movement of a stroke simulator. It is explanatory drawing which shows the operation knob of an input device. It is an expansion longitudinal cross-sectional view of the stroke simulator with which the hydraulic-pressure generator which concerns on 2nd Embodiment of this invention is equipped. It is a figure which shows the stroke simulator which concerns on 3rd Embodiment of this invention, (a) is a longitudinal cross-sectional view, (b) is an expanded longitudinal cross-sectional view of an electromagnetic actuator part. It is a figure which shows the stroke simulator which concerns on 4th Embodiment of this invention, (a) is a longitudinal cross-sectional view, (b) is an enlarged longitudinal cross-sectional view of an electromagnetic actuator part.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings as appropriate. In the description of each embodiment, the same constituent elements are denoted by the same reference numerals, and redundant descriptions are omitted.

(First embodiment)
1st Embodiment demonstrates as an example the case where the hydraulic-pressure generator of this invention is applied to the brake system S for vehicles shown in FIG.
FIG. 1 schematically shows the overall configuration of the vehicle brake system S, and the arrangement of the devices shown in FIG. 1 is different from the arrangement of the devices shown in FIGS.

  As shown in FIG. 1, the vehicle brake system S includes a by-wire brake system that operates when a prime mover (such as an engine or an electric motor) is started, and a hydraulic system that operates when the prime mover is stopped. It is equipped with both brake systems.

The vehicle brake system S includes a hydraulic pressure generator 1 that generates a brake hydraulic pressure in accordance with an operation amount of a brake pedal BP (brake operator), and a hydraulic pressure controller 2 that supports stabilization of vehicle behavior. I have.
The vehicle brake system S can be mounted not only on a vehicle using only an engine (internal combustion engine) as a power source, but also on a hybrid vehicle using a motor together, an electric vehicle using only a motor as a power source, and a fuel cell vehicle. .

  The hydraulic pressure generator 1 includes a base body 10, a master cylinder 20 that uses a brake pedal BP as a drive source, a slave cylinder 30 that uses an electric motor 36 as a drive source, and a stroke simulator 40 that applies an operation reaction force to the brake pedal BP. And a control device 50 (see FIG. 3).

  In addition, each direction in the following description is set for convenience in describing the hydraulic pressure generating device 1, but generally coincides with a direction when the hydraulic pressure generating device 1 is mounted on a vehicle. The hydraulic pressure generator 1 is disposed in front of the brake pedal BP, and the rear surface 10c (see FIG. 2) of the base body 10 of the hydraulic pressure generator 1 faces the brake pedal BP. The movement direction of the pedal rod BP1 when the brake pedal BP is depressed is the front (front end side), and the movement direction of the pedal rod BP1 when the brake pedal BP returns is the rear (rear end side) (FIG. 2). reference). Furthermore, the direction perpendicular to the moving direction (front-rear direction) of the pedal rod BP1 is the left-right direction (see FIG. 3).

  The base 10 is made of a metal material and includes a substantially rectangular parallelepiped main body 10a and a protrusion 10i (see FIG. 5). Three cylinder holes 21, 31, 41 and a plurality of hydraulic pressure paths 11a, 11b, 12, 14a, 14b are formed in the main body 10a. Further, as shown in FIG. 3, various components such as a reservoir 26 and an electric motor 36 are attached to the base 10. A pedal rod BP1 is disposed on the rear surface 10c side of the base body 10.

A solenoid valve 13, a first switching valve 15a, a second switching valve 15b, pressure sensors 18a and 18b, and a stroke sensor 19 are attached to the right side surface 10h (one surface, see FIG. 3) of the main body 10a as functional components. And the control apparatus 50 which cooperates with these functional components is attached to the right side surface 10h.
An electromagnetic actuator 450 is attached to the right side surface 10h of the main body 10a. The electromagnetic actuator 450 functions as a characteristic changing mechanism that can change the reaction force characteristic of the stroke simulator 40.
These functional parts and the electromagnetic actuator 450 are mounted in a plurality of mounting holes 10m and 10n (partially shown) opened on the right side surface of the main body 10a.

  As shown in FIG. 5, the protruding portion 10 i protrudes from the substantially central portion of the right side surface 10 h of the main body portion 10 a. The protrusion 10i has a cylindrical shape. The protruding portion 10 i is accommodated in a housing cover 52 that is attached to the housing 51 of the control device 50.

  As shown in FIG. 1, the cylinder hole 21 is a bottomed cylindrical hole. The axis of the cylinder hole 21 extends in the front-rear direction. The cylinder hole 21 opens in the rear surface 10c of the main body 10a.

As shown in FIG. 5, the cylinder hole 31 is a bottomed cylindrical hole that is spaced apart from the cylinder hole 21. The axis of the cylinder hole 31 extends in the left-right direction and intersects the axis of the cylinder hole 21 three-dimensionally. The cylinder hole 31 opens in the left side surface 10g (other surface) of the main body 10a.
The bottom surface 31a of the cylinder hole 31 is disposed in the protruding portion 10i. That is, the bottom of the cylinder hole 31 is disposed in the protruding portion 10 i and is accommodated in the housing 51 of the control device 50.

  As shown in FIG. 5, the cylinder hole 41 is a bottomed cylindrical hole that is spaced apart from the cylinder hole 21 and the cylinder hole 31. The axis of the cylinder hole 41 is parallel to the axis of the cylinder hole 31. That is, the stroke simulator 40 is arranged on the base body 10 in parallel with the slave cylinder 30. Similar to the cylinder hole 31, the cylinder hole 41 opens in the left side surface 10g of the main body 10a.

  In the present embodiment, a cylinder hole 31 and a cylinder hole 41 are arranged below and vertically below the cylinder hole 21. When the axis of the cylinder hole 31 and the axis of the cylinder hole 41 are projected onto a horizontal plane passing through the axis of the cylinder hole 21, the axis of the cylinder hole 31 and the axis of the cylinder hole 41 are orthogonal to the axis of the cylinder hole 21. ing.

  The master cylinder 20 is a hydraulic pressure generating means that generates a hydraulic pressure by converting a pedal effort when the brake pedal BP is depressed to a brake hydraulic pressure. As shown in FIG. 1, the master cylinder 20 includes two pistons 22 and 23 (secondary piston and primary piston) inserted into the cylinder hole 21, and two elastic members 24 and 25 accommodated in the cylinder hole 21. It is equipped with.

  A bottom surface side pressure chamber 21c is formed between the bottom surface 21a of the cylinder hole 21 and the piston 22 (secondary piston) on the bottom surface 21a side. An elastic member 24 made of a coil spring is accommodated in the bottom side pressure chamber 21c.

  An opening-side pressure chamber 21d is formed between the piston 22 on the bottom surface 21a side and the piston 23 (primary piston) on the opening 21b side. An elastic member 25 made of a coil spring is accommodated in the opening side pressure chamber 21d.

  The pedal rod BP1 of the brake pedal BP is inserted into the cylinder hole 21 through the opening 21b. The front end (front end) of the pedal rod BP1 is connected to the rear end of the piston 23 on the opening 21b side. Accordingly, the piston 23 on the opening 21b side is connected to the brake pedal BP (see FIG. 1) via the pedal rod BP1. Both pistons 22 and 23 slide in the cylinder hole 21 in response to the depression force of the brake pedal BP, and pressurize the brake fluid in the bottom side pressure chamber 21c and the opening side pressure chamber 21d.

As shown in FIG. 1, a reservoir 26 is connected to the cylinder hole 21. The reservoir 26 is a container that stores brake fluid, and is attached to the upper surface 10d of the main body 10a. The two liquid supply portions 26a and 26a protruding from the lower surface of the reservoir 26 are inserted into the two reservoir union ports 17 and 17 formed on the upper surface 10d of the main body portion 10a.
On the bottom surfaces of the two reservoir union ports 17 and 17, communication holes 17a and 17a communicating with the inner peripheral surface of the cylinder hole 21 are opened.
A hose 26c extending from a main reservoir (not shown) is connected to the liquid supply pipe 26b of the reservoir 26.

  The slave cylinder 30 generates hydraulic pressure by driving the electric motor 36 (electric actuator) according to the operation amount of the brake pedal BP. The hydraulic pressure generated in the slave cylinder 30 (hereinafter referred to as “generated hydraulic pressure”) acts on the wheel brakes FL, RR, RL, FR (see FIG. 1).

  1 and 5, the slave cylinder 30 includes two pistons 32 and 33 inserted into the cylinder hole 31, two elastic members 34 and 35 accommodated in the cylinder hole 31, an electric motor 36, and the like. It is equipped with.

  A bottom pressure chamber 31c is formed between the bottom surface 31a of the cylinder hole 31 and the piston 32 on the bottom surface 31a side. An elastic member 34 made of a coil spring is accommodated in the bottom side pressure chamber 31c.

An opening-side pressure chamber 31d is formed between the piston 32 on the bottom 31a side and the piston 33 on the opening 31b side. An elastic member 35 made of a coil spring is accommodated in the opening-side pressure chamber 31d.
Brake fluid is supplied from the reservoir 26 into the cylinder hole 31 through a fluid supply path (not shown).

The electric motor 36 is an electric servo motor that is driven and controlled by the control device 50. The electric motor 36 is attached to the left side surface 10g of the main body 10a.
The electric motor 36 includes a coil portion 36a and a rotating portion 36c supported by a bearing 36b. A magnet 36d is attached to the rotating portion 36c.
A drive transmission unit 37 is provided inside the rotation unit 36c. The drive transmission unit 37 converts the rotational driving force of the electric motor 36 into a linear axial force. The drive transmission unit 37 includes a piston rod 37a that is in contact with the piston 33, and a plurality of balls 37b that are disposed between the piston rod 37a and the rotation unit 36c. A spiral thread groove is formed on the outer peripheral surface of the piston rod 37a, and a plurality of balls 37b are accommodated in the thread groove so as to be able to roll. The tip of the piston rod 37a (the portion facing the piston 33) is formed in a substantially hemispherical shape (see FIG. 5). The rotating part 36c is screwed into the plurality of balls 37b. Thus, the ball screw mechanism is provided between the rotating portion 36c and the piston rod 37a.

  A rotation angle sensor (not shown) is attached to the electric motor 36. The detection value of the rotation angle sensor is input to the control device 50. The control device 50 calculates the drive amount of the slave cylinder 30 based on the detection value of the rotation angle sensor.

When the rotating portion 36c of the electric motor 36 rotates, a linear axial force is applied to the piston rod 37a by the ball screw mechanism provided between the rotating portion 36c and the piston rod 37a, and the piston rod 37a moves in the front-rear direction. Move forward and backward.
When the piston rod 37a moves to the piston 33 side, the piston 33 receives the input from the piston rod 37a and moves forward (moves in the pressurizing direction) in the cylinder hole 31, and thereby the bottom side pressure chamber 31c and the opening side pressure chamber. The brake fluid in 31d is pressurized. When the piston rod 37a moves to the side opposite to the piston 33, the piston 33 moves backward (moves in the pressure reducing direction) in the cylinder hole 31 by the urging force of the elastic member 35 (elastic member 34), and the pressure on the bottom side The brake fluid in the chamber 31c and the opening side pressure chamber 31d is depressurized.

  The electric motor 36 is accommodated in a motor case 38. As shown in FIG. 5, the motor case 38 has a bottomed cylindrical shape. A flange portion 38 a is formed at the edge of the opening of the motor case 38. As shown in FIG. 2, the flange portion 38 a has a bulging portion 38 b that bulges downward in a substantially semicircular shape. The bulging portion 38 b extends below the electric motor 36 and covers the opening (lid member 45) facing the cylinder hole 41 of the stroke simulator 40.

  As shown in FIG. 2, the motor case 38 is fixed to the left side surface 10g of the base 10 using a plurality of fixing screws 38c (four in this embodiment). A seal member 39 is interposed between the flange portion 38 a and the left side surface 10 g of the base body 10. The seal member 39 has a shape along the edge of the motor case 38, and includes a circular portion 39a and a semicircular portion 39b continuous with the circular portion 39a. The circular portion 39 a is a portion along the outer periphery of the electric motor 36. The semicircular portion 39b is a portion along the opening of the cylinder hole 41 (lid member 45). That is, the seal of the electric motor 36 and the seal of the stroke simulator 40 can be performed with one seal member 39. The seal member 39 is attached to a concave groove 39c (see FIG. 6) formed in the left side surface 10g of the base body 10.

  The stroke simulator 40 is a device that generates a pseudo operation reaction force (brake reaction force) and applies it to the brake pedal BP. As shown in FIG. 6, the stroke simulator 40 includes a simulator main body 400 and an electromagnetic actuator 450. The simulator body 400 includes a cylinder hole 41, a simulator piston 42 (hereinafter simply referred to as “piston 42”), two large and small first return springs (first elastic members) 43 that urge the piston 42, and a second return. A spring (second elastic member) 44, a lid member 45, and a rubber bush 47 are provided.

  The cylinder hole 41 includes a small-diameter cylindrical first cylinder hole 41a and a large-diameter cylindrical second cylinder hole 41b. A cylindrical partition wall 41c is formed inside the second cylinder hole 41b with a gap therebetween. The first cylinder hole 41a is formed inside the partition wall 41c. A piston 42 is accommodated in the first cylinder hole 41a. A hydraulic chamber 401 defined by the piston 42 is formed in the first cylinder hole 41a. A branch hydraulic pressure path 12 (see FIG. 1) is connected to the hydraulic pressure chamber 401 via a port (not shown), and the brake fluid flows through the branch hydraulic pressure path 12.

  An annular groove 41c1 is formed on the inner wall of the partition wall 41c. For example, a silicone rubber cup seal 41d is fitted into the annular groove 41c1. The cup seal 41d seals a gap formed between the inner wall of the partition wall 41c and the piston 42. Thereby, the first cylinder hole 41a is divided into the hydraulic chamber 401 side and the second cylinder hole 41b side by the liquid tightness exhibited by the cup seal 41d. The brake fluid flowing into the hydraulic pressure chamber 401 does not leak to the left side (second cylinder hole 41b side) from the cup seal 41d. With this configuration, the hydraulic pressure of the brake fluid flowing into the hydraulic pressure chamber 401 can be effectively applied to the pressing of the piston 42. An O-ring may be used instead of the cup seal 41d.

  A cylindrical groove 402a is formed in the bottom 402 of the first cylinder hole 41a (the bottom 41B of the cylinder hole 41). The skirt portion 42b of the piston 42 is disposed in the groove portion 402a. In the bottom portion 402, a recess 10n is formed from the right side surface 10h of the main body 10a. A communication hole 403 that communicates with the recess 10 n is formed in the bottom 402. The communication hole 403 communicates coaxially with the cylinder hole 41.

  The piston 42 can be displaced (slid) in the left-right direction in the first cylinder hole 41a. The piston 42 includes a body part 42a, a skirt part 42b, and an extension part 42c. As shown in FIG. 6, the right surface of the trunk portion 42a is in contact with the bottom portion 402 of the first cylinder hole 41a in an initial state where no brake fluid is applied to the hydraulic pressure chamber 401. Further, the left surface of the trunk portion 42 a functions as a receiving surface that receives the right end portion of the first return spring 43. Moreover, the left surface of the trunk | drum 42a functions as a receiving surface which contacts the rubber bush 47 mentioned later and receives reaction force.

  The skirt part 42b extends rightward from the peripheral part of the trunk part 42a and has a cylindrical shape. The skirt portion 42b is located in the groove portion 402a of the bottom portion 402 of the first cylinder hole 41a in the initial state of the piston 42 where no brake fluid is applied to the hydraulic pressure chamber 401.

  The extending part 42c extends leftward from the peripheral edge of the left end of the body part 42a and has a cylindrical shape. A part of the first return spring 43, a part of the rubber bush 47, and a part of the spring receiving member 46 are disposed inside the extending part 42c.

  The first return spring 43 is a coil spring having a first elastic coefficient K1 (spring constant). The first return spring 43 is disposed between the body portion 42 a of the piston 42 and the spring receiving member 46 along the inner wall of the extending portion 42 c of the piston 42.

  The second return spring 44 is a coil spring having a second elastic coefficient K2 (spring constant) larger than the first elastic coefficient K1 of the first return spring 43. The second return spring 44 is disposed between the spring receiving member 46 and the lid member 45 along the inner wall of the second cylinder hole 41b.

  The spring receiving member 46 is a connecting member that connects the first return spring 43 and the second return spring 44. The spring receiving member 46 includes an annular flange receiving portion 46a, a substantially cylindrical side wall portion 46b extending leftward from the flange receiving portion 46a, and a top wall portion 46c covering the top portion of the side wall portion 46b. . The flange receiving portion 46 a serves to receive the right end of the second return spring 44. The side wall portion 46b and the top wall portion 46c form a bottomed cylindrical portion. The side wall part 46b is arrange | positioned at the outer surface side of the partition 41c. The top wall portion 46 c serves to receive the left end of the first return spring 43. The top wall portion 46 c is formed with a recess 46 d that enters the inside of the first return spring 43. A rubber bush 47 is attached to the end of the recess 46d.

  The rubber bush 47 has a third elastic coefficient K3 (spring constant) that is smaller than the second elastic coefficient K2 (spring constant) of the second return spring 44. The rubber bush 47 is accommodated inside the first return spring 43 (extension portion 42c of the piston 42). This makes it possible to effectively use a limited space and to arrange the rubber bush 47 in parallel with the first return spring 43. As will be described later, the rubber bush 47 is compressed and deformed in parallel with the compressive deformation of the first return spring 43.

  The opening 41b1 of the second cylinder hole 41b is expanded in diameter. A lid member 45 is fixed to the opening 41b1 by fitting. A circumferential groove 45 a is formed in the fitting portion 45 c of the lid member 45, and an annular seal member 45 b attached to the circumferential groove 45 a seals between the opening 41 b 1 and the lid member 45. The lid member 45 serves to receive the left end of the second return spring 44. A locking ring 45d is fitted in the opening 41b1. The lid member 45 is prevented from falling off by the locking ring 45d. As described above, the lower portion of the lid member 45 is covered with the bulging portion 38 b of the motor case 38.

  The electromagnetic actuator 450 presses the first return spring 43 and the second return spring 44, which are elastic members of the stroke simulator 40, in a compressing direction. The electromagnetic actuator 450 is accommodated in the housing 51 of the control device 50. That is, the electromagnetic actuator 450 protrudes from the right side surface 10 h of the base body 10. The housing 51 also functions as a cover member that covers the electromagnetic actuator 450.

  The electromagnetic actuator 450 includes a fixed core 451, a movable core 452, a coil unit 453, and a rod (pressing part) 454. The electromagnetic actuator 450 is inserted into a cylindrical concave portion 10 n provided on the right side surface 10 h of the base 10.

  The recess 10n is formed in the bottom 41B of the cylinder hole 41 of the stroke simulator 40, and is recessed so as to cut out the bottom 402 of the first cylinder hole 41a. Thereby, the bottom side of the recess 10 n is located inside the skirt portion 42 b of the piston 42. Thus, a part of the electromagnetic actuator 450 (the left part of the fixed core 451) is accommodated (overlapped) inside the skirt portion 42b of the piston 42. Further, the recess 10 n is formed coaxially with the cylinder hole 41. The right side of the communication hole 403 is open at the center of the bottom 10n1 of the recess 10n. The recess 10n communicates with the first cylinder hole 41a through the communication hole 403.

  The fixed core 451 also serves as a housing that accommodates the rod 454, and is formed of a cylindrical member having a through hole 451c penetrating left and right. The fixed core 451 is composed of a body portion 451a fixed to the base body 10, and a core portion 451b that is formed with an outer diameter narrower than the body portion 451a and extends rightward. The body part 451a is caulked and fixed by plastically flowing the peripheral edge of the opening of the recess 10n into the circumferential groove 451e of the body part 451a and forming a plastic deformation part around the body part 451a. The fixed core 451 is made of a magnetic material and attracts the movable core 452 when excited by the coil unit 453.

  An O-ring 455 that functions as a seal member and a locking ring 456 that prevents and locks the O-ring 455 are accommodated inside the opening at the left end of the through hole 451c. The O-ring 455 seals a gap formed between the body portion 451a and the rod 454. This seal prevents the brake fluid in the hydraulic chamber 401 of the stroke simulator 40 from entering the region inside the electromagnetic actuator 450 that is on the right side of the O-ring 455. That is, the electromagnetic actuator 450 has a structure (dry structure) in which the inner region on the right side of the O-ring 455 is not filled with brake fluid.

  A bottomed cylindrical guide tube 457 is fitted to the core portion 451b from the right side. The guide tube 457 is fixed to the core portion 451b by welding. A movable core 452 is accommodated inside the guide tube 457. The core part 451b guides the left and right movement of the movable core 452.

  The movable core 452 is a solid member made of a magnetic material. The movable core 452 is disposed in the guide cylinder 457 on the right side of the fixed core 451 and the rod 454 (on the opposite side of the piston 42 across the fixed core 451). When the fixed core 451 is excited, the movable core 452 is attracted to the fixed core 451 and moves (moves) in the moving direction. A convex portion 452a that protrudes with a circular contour is formed at the center of the left end surface of the movable core 452. The convex portion 452a has a diameter smaller than that of the through hole 451c, and can enter the through hole 451c when the movable core 452 moves. The right end portion of the rod 454 is in contact with the convex portion 452a.

  The rod 454 is a rod-like member that is inserted into the through hole 451c of the fixed core 451, and can move left and right in the through hole 451c. As shown in FIG. 5, the left end portion of the rod 454 protrudes into the communication hole 403 on the left side of the fixed core 451. The rod 454 moves into the hydraulic chamber 401 of the stroke simulator 40 when the movable core 452 is excited by the coil unit 453 and pushes the piston 42 to the left. The left end surface of the rod 454 may be brought into contact with the right surface of the body 42a of the piston 42 at the initial position before moving forward, or may be opposed to the right surface of the body 42a with a slight gap. Also good.

  The coil unit 453 includes a resin bobbin 453a having a cylindrical portion surrounding the guide cylinder 457, a coil 453b wound around the bobbin 453a, and a yoke 453c disposed outside the bobbin 453a and forming a magnetic path. ing. The bobbin 453a is integrally formed with a protrusion 453d that protrudes on the opposite side of the base 10. A connection terminal 458 made of a coil spring is attached to the protrusion 453d. The connection terminal 458 is electrically connected to a terminal (not shown) of the control board P. As a result, the electromagnetic actuator 450 can operate by receiving a signal directly from the control board P.

  The control board P is accommodated in the control device 50. Functional components such as the first switching valve 15a and the pressure sensor 18a are electrically connected to the control board P. As shown in FIG. 7, the outer shape of the control board P is formed in a substantially square shape so as to follow the shape of the right side surface 10 h (see FIG. 5) of the base body 10. A circular hole P1 is formed in the central portion of the control board P so that the protruding portion 10i of the base body 10 can be inserted. That is, the circular hole P1 functions as an insertion hole for inserting the protruding portion 10i. In addition, it is good to make the opening edge part of the circular hole P1 contact the outer peripheral surface of the protrusion part 10i partially or entirely. When contact is made in this way, the heat generated in the control board P can be radiated through the protrusion 10i. Thereby, the temperature rise of the control board P can be suitably avoided.

  As shown in FIGS. 3 to 5, the control device 50 includes a housing 51. A housing cover 52 is attached to the housing 51. The housing 51 is a resin box attached to the right side surface 10h of the base 10 via a seal member 51a (see FIG. 6). A control board P (see FIGS. 5 and 6) as an electrical component is accommodated in the housing 51. In the housing 51, a stroke sensor 19, a solenoid valve 13, a first switching valve 15a, a second switching valve 15b, a solenoid valve 15c, both pressure sensors 18a and 18b, and an electromagnetic actuator projecting from the right side surface 10h of the base body 10 are provided. 450 is accommodated. In the housing 51 and the housing cover 52, the protruding portion 10i of the base body 10 is accommodated. The housing cover 52 is attached to the housing 51 via a seal member 51b (see FIG. 6).

  The axis of each solenoid valve 13, the first switching valve 15a, the second switching valve 15b, and the solenoid valve 15c and the axis of the electromagnetic actuator 450 are arranged in parallel. It should be noted that the shaft centers of the pressure sensors 18a and 18b and the shaft center of the electromagnetic actuator 450 are also arranged in parallel.

  The control device 50 operates the motor 36, the electromagnetic valve 13, and the first switching valve based on information obtained from various sensors such as the pressure sensors 18a and 18b and the stroke sensor 19 and a program stored in advance. 15a, the second switching valve 15b, and the operation of the electromagnetic valve 15c are controlled.

  Further, the control device 50 controls the operation of the electromagnetic actuator 450 in accordance with the request of the driver (operator). In this embodiment, an input device for operating the electromagnetic actuator 450 is provided. FIG. 10 is a diagram illustrating an example of the input device. As shown in FIG. 10, the input device is disposed on the side of the handle 61 in the dashboard 60 of the driver's seat of the vehicle, and includes an operation panel 62 and an operation knob 63 provided on the operation panel 62. ing. The operation knob 63 is rotatable and has a normal reaction force characteristic that does not operate the electromagnetic actuator 450 (indicated by “S” in the figure: software) and a reaction force characteristic that activates the electromagnetic actuator 450 (reference numeral in the figure). It is possible to switch between “H” and “Hard”.

Next, each hydraulic pressure path formed in the substrate 10 will be described.
The two main hydraulic pressure paths 11a and 11b are hydraulic pressure paths starting from the cylinder hole 21 of the master cylinder 20, as shown in FIG.
The first main hydraulic pressure passage 11 a communicates with the bottom pressure chamber 21 c of the master cylinder 20. The second main hydraulic pressure passage 11 b communicates with the opening-side pressure chamber 21 d of the master cylinder 20. Pipes Ha and Hb reaching the hydraulic pressure control device 2 are connected to the two output ports 16 and 16 which are the end points of both the main hydraulic pressure paths 11a and 11b.

  A stroke sensor 19 is attached to the master cylinder 20. The stroke sensor 19 is a magnetic sensor that magnetically detects the position of the rod P1 of the brake pedal BP. A magnet (not shown) is attached to the rod P1. The stroke sensor 19 detects the position of the rod P1 by detecting the fluctuation of the magnetic field due to the movement of the rod P1. Furthermore, the stroke sensor 19 outputs a detection signal indicating the position of the rod P1 to the control device 50 (see FIGS. 3 to 5). The control device 50 detects the depression amount of the brake pedal BP based on information from the stroke sensor 19.

The branch hydraulic pressure path 12 is a hydraulic pressure path from the second main hydraulic pressure path 11 b to the hydraulic pressure chamber 401 of the stroke simulator 40. That is, the cylinder hole 21 of the master cylinder 20 and the cylinder hole 41 of the stroke simulator 40 communicate with each other via the second main hydraulic pressure path 11 b and the branch hydraulic pressure path 12.
The branch hydraulic pressure passage 12 is provided with a normally closed solenoid valve as the solenoid valve 13. The solenoid valve 13 can communicate with the cylinder hole 21 and the cylinder hole 41 in a non-communication state.

  The first series passage 14 a and the second communication passage 14 b are hydraulic pressure paths starting from the cylinder hole 31 of the slave cylinder 30. The first series passage 14a communicates with the first main hydraulic pressure passage 11a. The second communication passage 14b communicates with the second main hydraulic pressure passage 11b.

  In the first main hydraulic pressure passage 11a, a first switching valve 15a, which is a two-position three-port three-way valve, is provided at a connection portion with the first series passage 14a. Further, in the second main hydraulic pressure passage 11b, a second switching valve 15b, which is a two-position three-port three-way valve, is provided at a connection portion with the second communication passage 14b.

The first switching valve 15a is a solenoid valve, and in the first position (initial state) when not energized, the upstream side (master cylinder 20 side) and the downstream side (output port 16 side) of the first main hydraulic pressure passage 11a. ), The first series passage 14a and the first main hydraulic passage 11a are shut off.
Further, the first switching valve 15a, in the second position at the time of energization, shuts off the upstream side and the downstream side of the first main hydraulic pressure passage 11a, and the first series passage 14a and the first main hydraulic pressure passage 11a. It communicates with the downstream side.

The second switching valve 15b is a solenoid valve, and in the first position (initial state) when not energized, the upstream side (master cylinder 20 side) and the downstream side (output port 16 side) of the second main hydraulic pressure passage 11b. The second communication passage 14b and the second main hydraulic pressure passage 11b are shut off.
Further, the second switching valve 15b, in the second position at the time of energization, blocks the second communication path 14b and the second main hydraulic pressure path 11b while blocking the upstream side and the downstream side of the second main hydraulic pressure path 11b. It communicates with the downstream side.

  A normally open electromagnetic valve 15c is provided in the first series passage 14a. The electromagnetic valve 15c can block the communication state of the first series passage 14a.

  The two pressure sensors 18a and 18b detect the magnitude of the brake fluid pressure. Information acquired by both pressure sensors 18a and 18b is output to the control device 50 (see FIGS. 3 to 5).

The first pressure sensor 18 a is disposed upstream of the first switching valve 15 a and detects the brake fluid pressure generated in the master cylinder 20.
The second pressure sensor 18b is disposed on the downstream side of the second switching valve 15b. When the second communication path 14b communicates with the downstream side of the second main hydraulic pressure path 11b, the second pressure sensor 18b is connected to the slave cylinder 30. The generated brake fluid pressure is detected.

The hydraulic pressure control device 2 has a configuration capable of executing various hydraulic pressure controls such as anti-lock brake control and behavior stabilization control by appropriately controlling the brake hydraulic pressure applied to each wheel cylinder W of the wheel brake. And is connected to each wheel cylinder W through a pipe.
Although illustration is omitted, the hydraulic control device 2 includes a hydraulic unit provided with an electromagnetic valve, a pump, etc., a motor for driving the pump, a control unit for controlling the electromagnetic valve, the motor, etc. I have.

  Next, a change in the reaction force of the stroke simulator 40 will be described in detail while roughly explaining the operation of the vehicle brake system S. Hereinafter, the change in the reaction force of the stroke simulator 40 will be described by taking as an example a case where the amount of operation of the brake pedal BP is large (a case where compression deformation of the second return spring 44 is mainly performed).

  In the vehicle brake system S, when the system is activated, the normally closed electromagnetic valve 13 of the branch hydraulic pressure path 12 is opened. In this state, the hydraulic pressure generated in the master cylinder 20 by the operation of the brake pedal BP is transmitted to the stroke simulator 40 without being transmitted to the wheel cylinder W. Then, the hydraulic pressure in the hydraulic chamber 401 increases, and the piston 42 moves (advances) toward the lid member 45 against the urging forces of the first return spring 43, the rubber bush 47, and the second return spring 44. Thus, the stroke of the brake pedal BP is allowed, and a pseudo operation reaction force is applied to the brake pedal BP.

  Further, when the stroke sensor 19 detects that the brake pedal BP has been operated, the first switching valve 15a and the second switching valve 15b are excited (become the second position). Accordingly, the downstream side (wheel brake side) of the first main hydraulic pressure passage 11a and the first series passage 14a communicate with each other, and the downstream side (wheel brake side) of the second main hydraulic pressure passage 11b and the second communication passage 14b. Leads to. That is, the master cylinder 20 and the wheel cylinder W are disconnected (non-communication state), and the slave cylinder 30 is in communication with the hydraulic pressure control device 2 (wheel cylinder W).

When the stroke sensor 19 detects the depression of the brake pedal BP, the electric motor 36 of the slave cylinder 30 is driven by the control device 50, and the pistons 32 and 33 of the slave cylinder 30 move to the bottom surface 31a side. The brake fluid in the bottom side pressure chamber 31c and the opening side pressure chamber 31d is pressurized.
The control device 50 compares the generated hydraulic pressure of the slave cylinder 30 (the hydraulic pressure detected by the pressure sensor 18b) with the hydraulic pressure output from the master cylinder 20 (the hydraulic pressure corresponding to the operation amount of the brake pedal BP). Then, the rotational speed of the electric motor 36 is controlled based on the comparison result. In this way, the hydraulic pressure generating device 1 increases the hydraulic pressure.

  The hydraulic pressure generated in the slave cylinder 30 is transmitted to each wheel cylinder W via the hydraulic pressure control device 2, and when each wheel cylinder W is activated, a braking force is applied to each wheel.

  When the depression of the brake pedal BP is released, the electric motor 36 of the slave cylinder 30 is reversely driven by the control device 50, and the pistons 32 and 33 are returned to the electric motor 36 side by the elastic members 34 and 35. As a result, the pressure in the hydraulic chambers 31c and 31d is lowered, and the operation of each wheel cylinder W is released.

FIG. 8A is a characteristic diagram showing a reaction force characteristic of the stroke simulator 40 in a normal state where the electromagnetic actuator 450 is not operating. As the reaction force characteristic, the stroke amount (mm) of the brake pedal BP and the generated load are shown. The relationship with (N, reaction force) is shown.
In FIG. 8A, a region A shows a reaction force characteristic by the first return spring 43. Region B shows the reaction force characteristic of the rubber bush 47. A region C shows a reaction force characteristic by the second return spring 44.

  As described above, when the brake pedal BP is operated, the hydraulic pressure generated in the master cylinder 20 acts on the hydraulic pressure chamber 401 of the stroke simulator 40 through the branch hydraulic pressure path 12. Then, the piston 42 is moved forward by the applied hydraulic pressure, and the first return spring 43 is gradually compressed and deformed. A reaction force is generated by this compression deformation, and the load gradually increases as the stroke amount increases (area A).

  Thereafter, when the compression deformation of the first return spring 43 proceeds, the piston 42 contacts the rubber bush 47, and in addition to the compression deformation of the first return spring 43, the rubber bush 47 is compressed and deformed in parallel. Due to this compression deformation, a load is generated by adding the reaction force of the rubber bush 47 to the reaction force of the first return spring 43. As a result, as shown by a region B in FIG. 8A, the reaction force characteristic in the range near the switching point where the reaction force characteristic switches from the first return spring 43 to the second return spring 44 gradually changes.

  Thereafter, when the compression deformation of the rubber bush 47 proceeds, the tip end portion 42f of the piston 42 comes into contact with the opposing portion of the top wall portion 46c of the spring receiving member 46, and the spring receiving member 46 is pushed in the advancing direction. Then, the second return spring 44 is compressed and deformed via the spring receiving member 46. Due to this compression deformation, a load is generated by adding the reaction force of the second return spring 44 to the reaction force of the first return spring 43 and the rubber bush 47. As a result, as shown in FIG. 8A, the reaction force characteristic shifts from the region B to the region C, and in addition to the load in the region B, a load by the second return spring 44 is applied, thereby increasing the stroke amount. The reaction force characteristics change greatly.

Next, a change in the reaction force characteristics when the operation knob 63 (see FIG. 10) of the input device is operated by the driver and the electromagnetic actuator 450 is operated will be described.
When the operation knob 63 is rotated by the driver after the system is started, an operation signal is transmitted to the control device 50, and the coil unit 453 of the electromagnetic actuator 450 is excited by the control device 50. By this excitation, as shown in FIG. 9A, the movable core 452 is attracted toward the fixed core 451 side. By this suction, the rod 454 moves together with the movable core 452 to the piston 42 side, and the piston 42 is pushed in the advancing direction (left direction) by the rod 454. Then, the first return spring 43 is pushed by the piston 42 and is compressed and deformed, and a load is applied to the first return spring 43 in advance. Although a load is also applied to the second return spring 44 via the spring receiving member 46, the second elastic coefficient K2 of the second return spring 44 is larger than the first elastic coefficient K1 of the first return spring 43. Therefore, only the first return spring 43 is compressed and deformed.

FIG. 8B is a graph showing the reaction force characteristics of the stroke simulator 40 when the electromagnetic actuator 450 is operated.
In FIG. 8B, a region A1 is a reaction force characteristic by the first return spring 43. In the area A1, since the piston 42 moves forward from a state in which the load is applied to the first return spring 43 by the electromagnetic actuator 450 in advance, the stroke amount in the area A shown in FIG. A predetermined load is reached with a small stroke amount.

  Thereafter, in the region B1, as described above, the piston 42 contacts the rubber bush 47, and the rubber bush 47 is compressed and deformed in parallel in addition to the compression deformation of the first return spring 43. Due to this compression deformation, a load is generated by adding the reaction force of the rubber bush 47 to the reaction force of the first return spring 43. As a result, the reaction force characteristic in the range near the switching point at which the reaction force characteristic switches from the first return spring 43 to the second return spring 44 changes gradually.

  Thereafter, in the region C1, the piston 42 pushes the spring receiving member 46 in the advance direction in the same manner as described above, and the second return spring 44 is compressed and deformed. Due to this compressive deformation, a load is generated by adding the reaction force of the second return spring 44 to the reaction force of the first return spring 43 and the rubber bush 47, and the reaction force characteristic changes by the load.

  FIG. 8C is a graph showing the reaction force characteristics shown in FIGS. 8A and 8B side by side. As shown in FIGS. 8A to 8C, the stroke amount in the region A1 in which the electromagnetic actuator 450 is operated is normal when the electromagnetic actuator 450 is not operated. It becomes shorter than the stroke amount in the area A. Therefore, when the electromagnetic actuator 450 is operated, the reaction force characteristic changes from the region A1 to the region B1 at a relatively early stage (relatively short stroke amount) from the start of operation of the brake pedal BP. Along with this, the change in the reaction force characteristic from the region B1 to the region C1 is also accelerated. Therefore, when the electromagnetic actuator 450 is operated, a larger reaction force characteristic can be obtained even with the same stroke than when the electromagnetic actuator 450 is not operated.

  When the operation of the brake pedal BP is released, the piston 42 is retracted by the reaction force of the first return spring 43, the rubber bush 47, and the second return spring 44, and the piston 42 is returned to the initial position.

  The hydraulic pressure control device 2 appropriately controls the brake hydraulic pressure applied to each wheel cylinder W of the wheel brake so that the deceleration matches the reaction force characteristic when the electromagnetic actuator 450 is operated as described above. To do. That is, when it is determined that the electromagnetic actuator 450 is operated by the driver, the control unit corrects the control amount of the slave cylinder 30 with respect to the pedal stroke, and controls the brake hydraulic pressure. This provides a brake feeling that does not give the driver a sense of incongruity.

  According to the present embodiment described above, reaction force characteristics can be easily achieved by operating the electromagnetic actuator 450 without causing a significant increase in cost such as replacement of components of the stroke simulator 40 with those having different characteristics. Can be changed. In addition, fewer parts are added to change the reaction force characteristics, which can be realized at low cost.

  Further, since the electromagnetic actuator 450 is arranged on the bottom 41B side of the cylinder hole 41, the piston 42 can be easily pressed by projecting the rod 454 from the bottom 41B side. Therefore, the configuration for changing the reaction force characteristic is simple, and the cost can be reduced. Further, the electromagnetic actuator 450 can be efficiently laid out using the space on the bottom 41B side of the cylinder hole 41. Further, since the piston 42 is pushed so as to move originally, the first return spring 43 can be suitably pushed by the rod 454 without using a new receiving member or the like. Therefore, an increase in cost can be suppressed.

Further, since the rod 454 is disposed coaxially with the piston 42, the piston 42 can be stably pressed by the rod 454. Moreover, layout property also improves by arrange | positioning coaxially.
The rod 454 and the piston 42 are not limited to be arranged coaxially, and may be arranged in parallel as long as the piston 42 can be pressed by the rod 454.

  Further, since the electromagnetic actuator 450 has a simple configuration including the fixed core 451, the movable core 452, the coil unit 453, and the rod 454, the reaction force characteristics can be easily changed without causing a significant cost increase. Can do. Further, the reaction force characteristic of the first return spring 43 can be suitably changed by a simple electromagnetic structure that does not require a rotation conversion mechanism or the like as in the case of using a gear or the like.

  In addition, since a part of the fixed core 451 is accommodated inside the piston 42, a part of the electromagnetic actuator 450 can be accommodated (overlapped) inside the piston 42, thereby saving space. Can do.

  Further, the O-ring 455 provided in the electromagnetic actuator 450 can positively form a region where brake fluid does not flow into the electromagnetic actuator 450, so that air hardly remains in a region on the left side of the O-ring 455. Therefore, it is possible to suitably prevent the brake feeling from being lowered.

  Further, since the concave portion 10n is provided in the bottom 41B of the cylinder hole 41 on the right side surface 10h of the base body 10, the fixed core 451 can be easily fixed while being positioned at a desired position using the concave portion 10n. Therefore, it is excellent in assemblability. Further, the electromagnetic actuator 450 can be disposed close to the piston 42, and space saving can be achieved.

  In addition, it is preferable to use the stroke simulator 40 of the present embodiment for the hydraulic pressure generator 1 including the master cylinder 20 and the slave cylinder 30 that is driven according to the operation amount of the brake pedal BP.

  Further, since the electromagnetic actuator 450 can be operated by operating the operation knob 63, the simulator characteristics can be easily changed when requested by the driver using the operation knob 63.

  Furthermore, a part of the electromagnetic actuator 450 can be accommodated using the housing 51 attached to the base 10. Therefore, the electromagnetic actuator 450 can be efficiently laid out in the hydraulic pressure generator 1. This contributes to the miniaturization of the hydraulic pressure generator 1.

  In addition, since the shaft center of the electromagnetic valve 13 and the like and the shaft center of the electromagnetic actuator 450 are arranged in parallel, they can be efficiently laid out in the housing 51.

  Further, since the electromagnetic valve 13 and the like and the electromagnetic actuator 450 are electrically connected to the same control board P, the configuration is simplified, and the electromagnetic valve 13 and the electromagnetic actuator 450 are efficiently installed in the housing 51. Can be laid out well.

  In addition, since the stroke simulator 40 is arranged in parallel with the slave cylinder 30, the stroke simulator 40 and the slave cylinder 30 having a relatively long length can be laid out efficiently.

(Second Embodiment)
A stroke simulator provided in the hydraulic pressure generating apparatus according to the second embodiment will be described with reference to FIG. In the first embodiment, the electromagnetic actuator 450 (see FIG. 5) has an O-ring 455 (see FIG. 5) and has a dry structure. However, in the present embodiment, the O-ring 455 is excluded and the electromagnetic actuator is removed. The brake fluid enters the 450A (wet structure).

  As shown in FIG. 11, a support portion 451 f that slidably supports the rod 454 is formed to protrude from the left end opening of the through hole 451 c. A gap through which brake fluid can flow is formed between the support surface of the support portion 451f and the outer peripheral surface of the rod 454. By this gap, the communication hole 403 (hydraulic pressure chamber 401) communicates with a region formed inside the electromagnetic actuator 450A. Thus, the electromagnetic actuator 450A has a wet structure in which the brake fluid enters.

  According to the present embodiment described above, the same functions and effects as those described in the first embodiment can be obtained. In addition, since the electromagnetic actuator 450A has a wet structure, the O-ring 455 used in the dry structure is eliminated, and the sliding resistance is reduced correspondingly, thereby realizing smooth sliding of the rod 454. it can.

(Third embodiment)
A stroke simulator provided in the hydraulic pressure generator of the third embodiment will be described with reference to FIG. The stroke simulator 40A of the present embodiment has a cylinder hole 71 extending in the front-rear direction of the base body 10 constituting the hydraulic pressure generator. Moreover, it has a substantially cylindrical piston 72.

The stroke simulator 40A of this embodiment is incorporated in the hydraulic pressure generator 1 as in the first and second embodiments.
As shown in FIG. 12A, the stroke simulator 40 </ b> A is configured by incorporating components into a main body 70 formed on the base body 10. An electromagnetic actuator 450 is incorporated in the bottom part 70a of the main body part 70, as in the first and second embodiments.

  The stroke simulator 40 </ b> A has a substantially cylindrical first cylinder hole 71 a and second cylinder hole 71 b as cylinder holes 71. A piston 72 that is displaceable (slidable) is provided in the first cylinder hole 71a. A hydraulic chamber 71c is formed in the first cylinder hole 71a. The hydraulic pressure chamber 71c is connected to the branch hydraulic pressure path 12 (see FIG. 1) via a port (not shown). The second cylinder hole 71b has a larger diameter than the first cylinder hole 71a, and has a coiled first return spring 73 and a coiled second return spring having a larger elastic coefficient (spring constant). 74 is arranged. The first cylinder hole 71a and the second cylinder hole 71b are filled with brake fluid.

  An annular groove 71d is formed on the inner wall of the first cylinder hole 71a. A cup seal 71e made of, for example, silicone rubber is fitted in the annular groove 71d. The cup seal 71e seals a gap formed between the inner wall of the first cylinder hole 71a and the piston 72. Thereby, the first cylinder hole 71a is partitioned into the hydraulic chamber 71c side and the second cylinder hole 71b side by the liquid tightness exhibited by the cup seal 71e. The brake fluid flowing into the hydraulic pressure chamber 71c does not leak to the front side (second cylinder hole 71b side) of the cup seal 71e. With this configuration, the hydraulic pressure of the brake fluid flowing into the hydraulic pressure chamber 71 c can be effectively applied to the pressure of the piston 72. An O-ring may be used instead of the cup seal 71e.

  The piston 72 includes a body portion 72a, a front projecting portion 72b, and a rear projecting portion 72c. The trunk | drum 72a is exhibiting the column shape. The outer peripheral diameter of the trunk portion 72a is slightly smaller than the inner peripheral diameter of the first cylinder hole 71a. The front protrusion 72b is integrally formed on the front side of the body 72a. The outer surface of the peripheral edge of the front protrusion 72b constitutes a spring receiving surface 72b1. The spring receiving surface 72b1 is a portion that receives the first return spring 73 via the first spring seat member 75a. A cylindrical portion of the first spring seat member 75a is fitted on the front projecting portion 72b.

  The rear protrusion 72c is integrally formed on the rear side of the body 72a. The rear protrusion 72c is formed symmetrically with the front protrusion 72b. That is, when the piston 72 is assembled in the first cylinder hole 71a with the rear protrusion 72c on the front side, the rear protrusion 72c can be used as the front protrusion 72b. Therefore, the piston 72 can be assembled to the first cylinder hole 71a without worrying about the front and rear assembly directions. The rear protrusion 72c is disposed in contact with the entire hole edge of the communication hole 403 so as to close the communication hole 403.

  The first spring seat member 75a is formed to have a bottomed cylindrical portion whose front side is closed, and has a substantially cup shape. The first spring seat member 75a is fixed to the piston 72 in a state where the opening of the cylindrical portion is closed by the front projecting portion 72b.

  A second spring seat member 75b is disposed on the front side facing the first spring seat member 75a. The second spring seat member 75b is formed to have a bottomed cylindrical portion whose front side is closed, and has a substantially cup shape. The second spring seat member 75 b functions as a connecting member that connects the first return spring 73 and the second return spring 74. The second spring seat member 75 b has a flange portion that receives the rear end side of the second return spring 74. Further, the second spring seat member 75 b has a top wall portion that receives the front end side of the first return spring 73. The first return spring 73 and the second return spring 74 are arranged in series via the second spring seat member 75b.

  A rubber bushing 76 is provided on the rear surface of the top wall portion of the second spring seat member 75b. The rubber bush 76 is housed inside the first return spring 73 and is disposed in parallel with the first return spring 73. The first spring seat member 75a and the second spring seat member 75b are connected by a connecting pin 77 so as not to be detached.

  On the front side facing the second spring seat member 75b, a lid member 78 that is attached so as to enter the inside of the second return spring 74 is disposed. The lid member 78 is fitted and fixed in the opening of the second cylinder hole 71b. An engagement groove 78a is formed around the lid member 78, and an annular seal member 78b attached to the engagement groove 78a seals between the lid member 78 and the opening of the second cylinder hole 71b in a liquid-tight manner. With this configuration, the brake fluid filling the cylinder hole 71 is prevented from leaking from between the opening of the second cylinder hole 71 b and the lid member 78. The lid member 78 receives the front end side of the second return spring 74 on the rear end side.

  As shown in FIG. 12B, the electromagnetic actuator 450 has the same configuration as that described in the first embodiment. The electromagnetic actuator 450 is mounted in a recess 10p formed in the rear surface 10c of the main body 10a.

  The electromagnetic actuator 450 presses the first return spring 73 and the second return spring 74, which are elastic members of the stroke simulator 40A, in the direction in which the electromagnetic actuator 450 is compressed (the forward direction as the advance direction). The electromagnetic actuator 450 is accommodated in a housing 80 attached to the rear surface 10c of the main body 10a. In other words, the space in the housing 80 is preferably used to project from the rear surface 10c of the base body 10. The housing 80 also functions as a cover member that covers the electromagnetic actuator 450. The housing 80 is fixedly attached to the rear surface 10c of the main body 10a with a bolt 84 via a seal member 83.

  The recess 10p is formed in the bottom 70a of the cylinder hole 71 of the stroke simulator 40A, and is recessed in the bottom of the first cylinder hole 71a. The recess 10 p is formed coaxially with the cylinder hole 71. The rear side of the communication hole 403 is open at the center of the bottom 10p1 of the recess 10p. The recess 10p communicates with the first cylinder hole 71a through the communication hole 403.

  Also in this embodiment, an O-ring 455 that functions as a seal member and a locking ring 456 that prevents and locks the O-ring 455 are accommodated inside the opening at the front end of the through hole 451c. The seal of the O-ring 455 prevents the brake fluid in the hydraulic chamber 71c of the stroke simulator 40A from entering a region inside the electromagnetic actuator 450 that is on the rear side of the O-ring 455. That is, the electromagnetic actuator 450 has a dry structure in which the brake fluid is not filled in the inner region on the rear side of the O-ring 455.

  The left end portion of the rod 454 protrudes into the communication hole 403 on the front side of the fixed core 451. The rod 454 moves into the hydraulic chamber 71c of the stroke simulator 40A when the movable core 452 is excited by the coil unit 453, and pushes the piston 72 forward. The left end surface of the rod 454 may be brought into contact with the rear surface of the rear projecting portion 72c of the piston 72 at an initial position before moving forward, or opposed to the rear surface of the rear projecting portion 72c with a slight gap. You may let them.

  A connection terminal 458 of the coil unit 453 is connected to a bus bar 81 provided in the housing 80. As shown in FIG. 12A, the end of the bus bar 81 is disposed in a connector portion 82 provided on the housing 80.

  Also in this embodiment, when the driver operates the operation knob 63 (see FIG. 10) of the input device after the system is started, the liquid generated in the master cylinder 20 (see FIG. 1) when the brake pedal BP is operated. The pressure acts on the hydraulic chamber 71 c of the stroke simulator 40 </ b> A through the branch hydraulic pressure path 12. Then, the piston 72 is moved forward by the applied hydraulic pressure, and the first return spring 73 is gradually compressed and deformed. A reaction force is generated by this compression deformation, and the load gradually increases as the stroke amount increases (region A in FIG. 8).

  Thereafter, when the compression deformation of the first return spring 73 proceeds, the piston 72 comes into contact with the rubber bush 76, and in addition to the compression deformation of the first return spring 73, the rubber bush 76 is compressed and deformed in parallel. Due to this compressive deformation, a load is generated by adding the reaction force of the rubber bush 76 to the reaction force of the first return spring 73. As a result, the reaction force characteristics in the vicinity of the switching point where the reaction force characteristics switch from the first return spring 73 to the second return spring 74 change gradually.

  Thereafter, when the compression deformation of the rubber bushing 76 proceeds, the flange portion of the first spring seat member 75a comes into contact with the flange portion of the second spring seat member 75b, and the second spring seat member 75b is pushed in the advancing direction. Then, the second return spring 74 is compressed and deformed via the second spring seat member 75b. Due to this compression deformation, a load is generated by adding the reaction force of the second return spring 74 to the reaction force of the first return spring 73 and the rubber bush 76. As a result, the reaction force characteristic changes greatly (from region B to region C in FIG. 8A).

Next, a change in the reaction force characteristics when the operation knob 63 (see FIG. 10) of the input device is operated by the driver and the electromagnetic actuator 450 is operated will be described.
When the coil unit 453 of the electromagnetic actuator 450 is excited after the system is activated, the movable core 452 is attracted toward the fixed core 451 side, and the piston 72 is advanced by the rod 454 that moves together with the movable core 452. It is pushed in the moving direction (forward direction). Then, the first return spring 73 is pressed by the piston 42 and is compressed and deformed, and a load is applied to the first return spring 73 in advance. Although a load is also applied to the second return spring 74 via the second spring seat member 75b, the elastic coefficient of the second return spring 44 is larger than the elastic coefficient of the first return spring 73. Only one return spring 73 is compressed and deformed.

  Thus, since the piston 72 moves forward from a state in which a load has been applied to the first return spring 73 in advance, the first return spring 73 has a predetermined stroke amount less than the normal stroke amount. The load is reached (see FIG. 8B, region A1).

  Thereafter, in the same manner as described above, the piston 72 comes into contact with the rubber bush 76, and in addition to the compression deformation of the first return spring 73, the rubber bush 76 is compressed and deformed in parallel. Due to this compressive deformation, a load is generated by adding the reaction force of the rubber bush 76 to the reaction force of the first return spring 73. Thereby, the reaction force characteristic in the range near the switching point where the reaction force characteristic switches from the first return spring 73 to the second return spring 74 changes gradually (see FIG. 8B, region B1).

  Thereafter, in the same manner as described above, the piston 72 pushes the second spring seat member 75b in the advancing direction, and the second return spring 74 is compressed and deformed. Due to this compressive deformation, a load is generated by adding the reaction force of the second return spring 74 to the reaction force of the first return spring 73 and the rubber bush 76, and the reaction force characteristic changes greatly (FIG. 8B). , See region C1).

  Also in the present embodiment, the stroke amount of the brake pedal BP when the electromagnetic actuator 450 is operated is shorter than the stroke amount of the brake pedal BP at the normal time when the electromagnetic actuator 450 is not operated. Therefore, the reaction force characteristic by the second return spring 74 can be obtained at a relatively early stage from the start of operation of the brake pedal BP.

  According to this embodiment described above, the same function and effect as those described in the first embodiment can be obtained. That is, by operating the electromagnetic actuator 450, it is possible to easily change the reaction force characteristics without causing a significant increase in cost such as replacement of components of the stroke simulator 40A with those having different characteristics.

  In the present embodiment, the electromagnetic actuator 450 has a dry structure using the O-ring 455. However, the present invention is not limited to this, and a wet structure in which the brake fluid enters the electromagnetic actuator 450 by eliminating the O-ring 455. It is good. In this case, toughness against rust and the like inside the electromagnetic actuator 450 is improved. Further, since the O-ring 455 is eliminated, the sliding resistance is reduced correspondingly, and smooth sliding of the rod 454 can be realized.

(Fourth embodiment)
A stroke simulator provided in the hydraulic pressure generator of the fourth embodiment will be described with reference to FIG. The stroke simulator 40B of the present embodiment is obtained by partially changing the components of the stroke simulator 40A described in the third embodiment. This embodiment is different from the third embodiment in that a bottomed cylindrical piston 90 is provided, and an electromagnetic actuator 450 is disposed inside the piston 90.

  As shown in FIG. 13A, the piston 90 has a cylindrical body portion 91 and a bottom portion 92 provided continuously to the body portion 91. A front protrusion 92 a is integrally formed on the front side of the bottom 92. A substantially cylindrical extending portion 93 extending rearward is formed at the center of the rear surface of the bottom portion 92. An electromagnetic actuator 450 is disposed behind the extending portion 93. The electromagnetic actuator 450 is disposed so as to overlap the inside of the body portion 91 of the piston 90 so that the entire electromagnetic actuator 450 is accommodated in the main body portion 10a.

  The electromagnetic actuator 450 is attached to the main body 10 a via a holding member 95. As shown in FIG. 13B, the holding member 95 includes a cylindrical portion 95a and a bottomed portion 95b continuous with the cylindrical portion 95a. The rear end portion 95e of the cylindrical portion 95a is press-fitted and fixed to a step portion 71a1 formed inside the rear end of the first cylinder hole 71a. The cylindrical portion 95a is disposed inside the body portion 91 of the piston 90 with a space therebetween, so that it does not interfere with the sliding of the piston 90.

  A recessed portion 95 c to which the electromagnetic actuator 450 is attached is formed in the bottomed portion 95 b of the holding member 95. The recessed portion 95c faces the extending portion 93 of the piston 90, and is formed coaxially with the first cylinder hole 71a. A communication hole 95g that communicates with the hydraulic chamber 71c is formed at the center of the bottom 95f of the recess 95c. The rear end portion of the extending portion 93 is in contact with the opening edge of the front end of the communication hole 95g.

  The electromagnetic actuator 450 is attached to the holding member 95 from the rear opening side so that the whole is accommodated inside the holding member 95. And the electromagnetic actuator 450 is accommodated in the main-body part 10a so that it may be covered by the housing 80B attached to the rear surface 10c of the main-body part 10a. The housing 80B is attached and fixed to the rear surface 10c of the main body portion 10a with a bolt 84 via a seal member 83. The housing 80B is provided with a bus bar 81a. The front end of the bus bar 81a extends into the first cylinder hole 71a and is connected to the coil unit 453 of the electromagnetic actuator 450. The rear end portion of the bus bar 81a is disposed in a connector portion 82a provided in the housing 80B.

  In this embodiment, when the coil unit 453 of the electromagnetic actuator 450 is excited after the system is activated, the movable core 452 is attracted toward the fixed core 451 side, and is moved by the rod 454 that moves integrally with the movable core 452. The piston 90 is pushed in the moving direction (forward direction). Then, as in the third embodiment, a load is applied to the first return spring 73 in advance.

  Also in the present embodiment, the stroke amount of the brake pedal BP when the electromagnetic actuator 450 is operated is shorter than the stroke amount of the brake pedal BP at the normal time when the electromagnetic actuator 450 is not operated. Therefore, the reaction force characteristic by the second return spring 74 can be obtained at a relatively early stage from the start of operation of the brake pedal BP.

  According to this embodiment described above, the same function and effect as those described in the first embodiment can be obtained. That is, by operating the electromagnetic actuator 450, it is possible to easily change the reaction force characteristics without incurring a significant cost increase such as replacing components of the stroke simulator 40B with those having different characteristics.

Further, since the electromagnetic actuator 450 can be fixed to the base body 10 (main body portion 10a) via the holding member 95, the degree of freedom of the installation position is increased. For example, the electromagnetic actuator 450 can be installed using the structure originally provided in the stroke simulator 40B.
Further, since substantially the entire electromagnetic actuator 450 is accommodated inside the first cylinder hole 71a, the amount of protrusion to the rear side surface of the main body 10a can be minimized, and the main body 10a can be reduced in size and space. Can be achieved. In addition, since most of the electromagnetic actuator 450 can be disposed so as to overlap the inside of the piston 90, space saving in the main body 10a can be achieved. Further, since the inside of the piston 90 is thinned, the weight can be reduced. In addition, the slidability is improved by reducing the weight of the piston 90.

  In this embodiment, the electromagnetic actuator 450 has a dry structure using the O-ring 455, but the present invention is not limited to this, and a wet structure in which the brake fluid enters the electromagnetic actuator 450 without the O-ring 455 being used. It is good.

  In each of the above-described embodiments, the piston 42 (72, 90) is pushed by the electromagnetic actuator 450. However, the present invention is not limited to this, and the first return spring 43 (73) may be directly pushed and deformed. Good. Further, the first return spring 43 (73) may be compressed and deformed by being pushed by the electromagnetic actuator 450 from the lid member 45 (78) side.

  In each of the above embodiments, the first return spring 43 (73) is compressed and deformed to change the reaction force characteristic. However, the present invention is not limited to this, and the second return spring 44 (74) The reaction force characteristic may be changed by compressing and deforming the electromagnetic actuator 450. Further, the first return spring 43 (73), the rubber bush 47 (76), and the second return spring 44 (74) may be compressed and deformed by the electromagnetic actuator 450 to change the reaction force characteristics. .

  Moreover, in each said embodiment, although it was set as the structure by which a part of electromagnetic actuator 450 is accommodated in the housing 51 grade | etc., It is not restricted to this, The whole electromagnetic actuator 450 is accommodated in the housing 51 grade | etc.,. It may be configured.

  In each of the above embodiments, the electromagnetic actuator 450 may be configured such that the rod 454 protrudes linearly by the operation of the operation knob 63 or the like. Moreover, you may comprise so that the rod 454 may protrude in multiple steps.

DESCRIPTION OF SYMBOLS 10 Base body 10n Concave part 40 Stroke simulator 41 Cylinder hole 41B Bottom part 42 Piston 43 1st return spring (elastic member)
44 Second return spring (elastic member)
45 Lid member 50 Control device 51 Housing 63 Operation knob (operation input unit)
95 Holding member 401 Hydraulic chamber 450 Electromagnetic actuator 451 Fixed core 452 Movable core 453 Coil assembly 453b Coil 454 Rod 455 O-ring (seal member)
BP Brake pedal (brake operator)
P Control board (board)

Claims (11)

A stroke simulator that applies a pseudo reaction force to the brake operator,
A base body having a bottomed cylinder hole;
A piston inserted into the cylinder hole;
A lid member for closing the opening of the cylinder hole;
An elastic member that is disposed between the piston and the lid member and generates a reaction force by being compressed in accordance with an operation of the brake operator;
An electromagnetic actuator attached to the substrate,
The electromagnetic actuator includes a pressing portion that extends in a compression direction of the elastic member to compress the elastic member. The stroke simulator according to claim 1,
The pressing portion is a rod;
A stroke simulator characterized in that the rod is arranged in the axial direction of the cylinder hole. In the stroke simulator according to claim 1 or 2,
The electromagnetic actuator is disposed on the bottom side of the cylinder hole,
The rod simulator presses the elastic member through the piston. The stroke simulator according to any one of claims 1 to 3,
A stroke simulator characterized in that the rod is arranged coaxially with the piston. The stroke simulator according to any one of claims 1 to 3,
The electromagnetic actuator is
A fixed core fixed to the base, a movable core provided movably with respect to the fixed core, and a coil for generating an electromagnetic force for moving the movable core toward the fixed core.
A stroke simulator characterized in that the rod moves integrally with the movable core. The stroke simulator according to claim 5,
The piston is formed in a substantially bottomed cylindrical shape,
At least a part of the fixed core is accommodated in a space formed inside the piston. In the stroke simulator according to claim 5 or 6,
The rod is movably supported on the fixed core via a seal member,
The stroke simulator characterized in that the seal member partitions a fluid pressure chamber formed in the cylinder hole and a region formed inside the electromagnetic actuator in a liquid-tight manner. The stroke simulator according to any one of claims 5 to 7,
A stroke simulator characterized in that a concave portion to which the fixed core is attached is provided at a bottom portion of the cylinder hole at a side portion of the base body. The stroke simulator according to any one of claims 5 to 7,
The stroke simulator characterized in that the fixed core is fixed to the base via a holding member. A hydraulic pressure generator using the stroke simulator according to any one of claims 1 to 9,
A master cylinder that generates a hydraulic pressure to be applied to a wheel brake by operating the brake operator;
A fluid pressure generating apparatus comprising: a slave cylinder that generates fluid pressure by an electric actuator that is driven according to an operation amount of the brake operator. The hydraulic pressure generator according to claim 10,
A hydraulic pressure generating apparatus comprising an operation input unit that receives an operation input for operating the electromagnetic actuator.

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