JP4706291B2 - Stroke simulator for brake equipment - Google Patents

Description

  The present invention relates to a stroke simulator for a brake device of a vehicle, and in particular, at least one elastic member for applying a stroke according to an operation force to a brake operation member has a substantially truncated cone shape having a large diameter end and a small diameter end. It is related with the stroke simulator for brake devices comprised by the rubber lump.

  Patent Document 1 below describes a stroke simulator configured between both ends of a pedal rod that interlocks a rod piston of a master cylinder and a brake pedal. This stroke simulator is composed of a cylinder interlocked with the rod piston, a piston sliding in the cylinder interlocked with the brake pedal, and an elastomer member compressed by the piston and the cylinder. The elastomer member has closed cells, and is an elastomer block having a truncated cone shape having a small-diameter end on the piston side and a large-diameter end on the opposite side.

Patent Document 2 below describes a stroke accumulator used in a booster that boosts a master cylinder that operates a brake or clutch of an automobile with fluid pressure. The stroke accumulator includes a fixed cylindrical accumulator body, a first piston slidably fitted to the accumulator body and defining a pressure accumulating chamber between one end wall of the accumulator body, and the first piston. A plurality of second pistons fitted to the accumulator main body so as to be slidable by a predetermined stroke on the side opposite to the pressure accumulating chamber, and the spring constants for urging these second pistons toward the first piston are made different. A plurality of springs and a buffer compressed between the second piston and the other second piston adjacent to the second piston or the other end wall of the accumulator body when each second piston moves a predetermined stroke to the opposite side of the first piston. It is composed of rubber. The buffer rubber is a substantially truncated cone-shaped rubber lump having a large-diameter end opposite to the first piston and a small-diameter end opposite to the first piston.
Japanese Patent Laid-Open No. 10-167042 Japanese Patent Laid-Open No. 3-45456

  By the way, the end face of the piston that compresses the elastomer mass and the rubber mass from the small diameter end side is formed into a flat surface, and when the ratio of the length to the diameter of the elastomer mass and the rubber mass is increased, the assembled elastomer mass There is a possibility that a large amount of misalignment may occur between the piston side end face of the elastomer lump or rubber lump and the end face of the piston facing it due to the inclination of the rubber lump and the low dimensional accuracy of each part of the elastomer lump or rubber lump. There is. If there is a large amount of misalignment between the piston-side end surface of the elastomer block or rubber block and the end surface of the piston facing it, the bias of the load applied to the end surface of the small diameter end during compression of the elastomer block or rubber block will increase. The elastomer lump and rubber lump may be excessively bent and deformed during compression of the elastomer lump and rubber lump, and the elastomer lump and rubber lump may be damaged such as cracks.

  Therefore, the present invention provides an input piston coupled to the brake operation member, and a stroke corresponding to the brake operation force that is compressed by the operation force transmitted from the brake operation member via the input piston. At least one elastic member to be applied, and the elastic member is a stroke simulator for a brake device configured by a substantially truncated cone-shaped rubber lump having a large-diameter end and a small-diameter end, It is an object of the present invention to provide a stroke simulator for a brake device configured such that a rubber lump is not excessively bent and deformed at the time of compression so that damage does not occur.

In order to achieve the above object, a brake simulator for a brake device according to the present invention includes an input piston coupled to a brake operation member and a transmission from the brake operation member via the input piston. At least one elastic member that is compressed by the applied brake operation force and applies a stroke corresponding to the brake operation force to the brake operation member, the elastic member having a large-diameter end and a small-diameter end. In the stroke simulator for a brake device configured by a head cone-shaped rubber lump, a rubber lump addition facing the end surface of the small-diameter end of the rubber lump among a pair of rubber lump pressurizing surfaces for compressing the rubber lump. Misalignment between the end surface of the small diameter end of the rubber mass and the pressure surface of the rubber mass due to engagement with the small diameter end of the rubber mass on the pressure surface Is a recess formed to limit below a predetermined amount Rutotomoni, large diameter of the rubber mass is obtained by the fact that is pressed into the hole to be incorporated with the rubber mass.

In the brake simulator stroke simulator according to claim 1, as described in claim 2, a rubber lump pressurizing piston is arranged adjacent to the small diameter end side of the rubber lump, and the rubber lump provided the rubber lump pressure surface the pressure piston, may be the recess in the rubber mass pressing surface is formed.

  In the brake simulator stroke simulator according to claim 2, the rubber lump and the rubber lump pressurizing piston are arranged coaxially with respect to the input piston in front of the input piston. It is good also as being done.

  Further, in the brake simulator stroke simulator according to claim 2, as described in claim 4, a fluid pressure chamber that generates fluid pressure according to an operation force applied to the brake operation member is the input piston. The rubber lump pressurizing piston may be driven by the hydraulic pressure of the hydraulic pressure chamber.

  In the stroke simulator for a brake device according to claim 1, the engagement between the end surface of the small-diameter end of the rubber lump and the recess of the rubber lump pressurizing surface facing the end surface causes the small-diameter end of the rubber lump and the rubber lump pressurizing surface to The misalignment amount is regulated to a predetermined amount or less. This predetermined amount is set so that the rubber lump is not excessively bent and deformed when the rubber lump is compressed, so that the rubber lump is not excessively bent and deformed when the rubber lump is compressed. Damage such as cracks does not occur in the mass.

  FIG. 1 is a diagram showing a configuration of a master cylinder MC provided with a stroke simulator SM1 for a brake device according to a first embodiment of the present invention. In FIG. 1, the master cylinder MC includes a fixed housing 10. A stepped cylinder hole 12 is formed in the housing 10. The stepped cylinder hole 12 includes a small-diameter portion 12a located between the front and rear ends, a medium-diameter portion 12b located on the front side of the small-diameter portion, a large-diameter portion 12c located on the rear side of the small-diameter portion 12a, and a large-diameter portion 12c. A maximum diameter portion 12d located on the rear side is provided. An annular groove 14 is formed on the inner periphery of the housing 10 between the front and rear ends of the large diameter portion 12 c of the cylinder hole 12. In FIG. 1, the left is the front and the right is the rear.

  The housing 10 has a port 16 for connecting to a reservoir RS (see FIG. 3) for storing brake fluid under atmospheric pressure, and a wheel cylinder WC (FIG. 3) for applying brake torque to the wheel. Port 18 is formed for connection. A seal member 20 positioned near the rear end of the small diameter portion 12a of the cylinder hole 12 is mounted on the inner periphery of the housing 10. The seal member 20 is an annular seal member having a cup shape in cross section.

  A compression coil spring for returning the master piston 22, the stopper 24 and the master piston 22 to a return position (position shown in FIG. 1) where the rear end of the master piston contacts the stopper 24 in the cylinder hole 12 of the housing 10. 26 is incorporated. The stopper 24 is fixed to the housing 10 by screw engagement with the inner periphery of the housing 10 at the outer periphery thereof. The seal member 20 mounted on the inner periphery of the housing 10 seals the sliding gap between the outer periphery of the master piston 22 and the inner periphery of the housing 10, and accordingly, the front end wall of the stepped cylinder hole 12 and the master piston 20 A master hydraulic chamber 28 is formed between the two.

  The master piston 22 has a large-diameter rear end portion, a large-diameter central portion, a small-diameter portion located between the rear-end portion and the central portion, and a small-diameter portion located in front of the large-diameter central portion. It has. Ring-shaped sealing members 30 and 32 having a cup-shaped cross section are mounted on the rear end portion of the large diameter of the master piston 22 and the central portion of the large diameter, respectively. The seal member 30 seals a sliding gap between the outer periphery of the master piston 22 and the inner periphery of the housing 10, and prevents the brake fluid from leaking out of the housing 10. On the other hand, when the master piston 22 is located at the return position, the seal member 32 is located on the inner circumference side of the annular groove 14 and away from the inner circumference of the housing 10, but the master piston 22 moves forward from the return position. When sliding and the sliding amount reaches a predetermined amount d1, the gap between the outer periphery of the master piston 22 and the inner periphery of the housing 10 is sealed by contacting the inner periphery of the housing 10.

  The master piston 22 is formed with a radial hole 34 located on the right side of the seal member 20 of the housing 10 when the master piston 22 is located at the return position. The hole 34 is always in communication with the master hydraulic chamber 28, and is communicated / blocked with respect to the port 16 by the seal member 20 according to the sliding of the master piston 22. That is, when the master piston 22 is located at the return position, the hole 34 communicates with the port 16, but when the master piston 22 slides forward from the return position and the sliding amount reaches the predetermined amount d2. It is blocked from the port 16 by the seal member 20. The predetermined amount d2 is smaller than the predetermined amount d1.

  A stepped cylinder hole 36 is formed in the master piston 22. The master piston 22 is formed with a radial hole 38 located behind the large-diameter central portion. The stepped cylinder hole 36 includes a front small diameter portion 36a and a rear large diameter portion 36b. In the stepped cylinder 36, a rubber lump 40, a rubber lump pressurizing piston 42, and a compression coil constituting the stroke simulator SM1. A spring 44 and an input piston 46 are incorporated. The rubber mass 40 is formed in a substantially truncated cone shape having a front large-diameter end 40 a and a rear small-diameter end 40 b, and is incorporated in the small-diameter portion 36 a of the stepped cylinder hole 36. Is press-fitted into the front end portion of the small diameter portion 36 a of the stepped cylinder hole 36.

  The rubber lump pressurizing piston 42 is slidably incorporated in the small diameter portion 36a of the stepped cylinder hole 36, and the front end face thereof has a small diameter end 40b of the rubber lump 40, as shown in FIGS. The amount of misalignment between the small diameter end 40b of the rubber lump 40 and the front end surface of the rubber lump pressurizing piston is set so that the rubber lump 40 is not excessively bent and deformed when the rubber lump 40 is compressed. A recess 42a is formed to restrict the amount to a predetermined amount or less. As shown in FIGS. 1 and 2, a groove 42b is formed on the outer periphery of the rubber lump pressurizing piston so as to always communicate the inside of the small diameter portion 36a of the stepped cylinder hole 36 with the inside of the large diameter portion 36b. The inside of the large diameter portion 36 b of the stepped cylinder hole 36 is always in communication with the hole 38.

  The pair of rubber mass pressurizing surfaces in claim 1 corresponds to the front end surface of the rubber mass pressurizing piston 42 and the front end surface of the stepped cylinder hole 36.

  The compression coil spring 44 is interposed between the rubber mass pressurizing piston 42 and the input piston 46, and the input piston 46 slides forward from the return position (position shown in FIG. 1) with respect to the master piston 22. Compressed. When the compression amount of the compression coil spring 44 reaches a predetermined compression amount d3, a contact relationship is generated between the front end of the input piston 46 and the rear end of the rubber mass pressurizing piston 42. The return position of the input piston 46 with respect to the master piston 22 is defined by an annular stopper 48 attached to the inner periphery of the rear end portion of the master piston 22. A seal member 50 that seals a sliding gap between the outer periphery of the large diameter portion 46 a and the inner periphery of the master piston 22 is attached to the large diameter portion 46 a of the input piston 46. The small diameter portion 46b of the input piston 46 extends rearward from the rear end of the large diameter portion 46a through the center hole of the stopper 24, and is connected to a brake pedal BP that is a brake operation member.

  The master cylinder MC configured as described above is connected as shown in FIG. 3 to form a vehicle hydraulic brake device. In FIG. 3, a port (port 18 shown in FIG. 1) of the master cylinder MC is connected to a wheel cylinder (typically represented by WC) of each wheel via a normally open electromagnetic on-off valve NO. A hydraulic pressure source PG that generates and outputs a predetermined hydraulic pressure regardless of the driver's brake operation is connected to the hydraulic pressure path between the on-off valve NO and the wheel cylinder WC.

  The hydraulic pressure source PG includes an electric motor M controlled by an electronic control unit ECU, and a hydraulic pump HP driven by the electric motor M. The input side thereof is connected to the reservoir RS, and the output side is connected to the accumulator AC. Has been. A pressure sensor Sps is connected to the output side of the hydraulic pressure source PG, and the detected pressure of the pressure sensor Sps is monitored by the electronic control unit ECU. Based on this monitoring result, the electric motor M is controlled by the electronic control unit ECU so that the hydraulic pressure of the accumulator AC is maintained at a pressure between a predetermined upper limit value and a lower limit value.

  The accumulator AC is connected to the hydraulic pressure path between the electromagnetic on-off valve NO and the wheel cylinder WC via the normally closed first proportional electromagnetic valve SV1, and the output hydraulic pressure of the hydraulic pressure source PG is adjusted. It is configured to be pressurized and supplied to the wheel cylinder WC. Further, the hydraulic pressure path between the electromagnetic opening / closing valve NO and the wheel cylinder WC is connected to the reservoir RS via a normally closed second proportional electromagnetic valve SV2, and the hydraulic pressure in the wheel cylinder WC is reduced and adjusted. It is comprised so that it may be pressed. Thus, the hydraulic pressure control means PC is constituted by the hydraulic pressure source PG, the first and second proportional solenoid valves SV1 and SV2, the electronic control unit ECU, and the following sensors.

  In FIG. 3, a pressure sensor Smc is connected to a hydraulic pressure path between the master cylinder MC and the electromagnetic opening / closing valve NO, and a hydraulic pressure sensor Swc is connected to the hydraulic pressure path between the electromagnetic opening / closing valve NO and the wheel cylinder WC. It is connected. The brake pedal BP is provided with a stroke sensor BS for detecting the stroke, and the detection signals from these sensors are input to the electronic control unit ECU. These sensors monitor the output hydraulic pressure of the master cylinder MC, the brake hydraulic pressure of the wheel cylinder WC, and the stroke of the brake pedal BP. Furthermore, sensors (typically represented by SN) such as wheel speed sensors and acceleration sensors used for various controls such as anti-lock control are provided, and detection signals from these sensors SN are also input to the electronic control unit ECU. Is configured to do.

  Next, the operation of the vehicle hydraulic brake device using the master cylinder provided with the brake simulator stroke simulator according to the embodiment of the present invention will be described. First, when the operation of the brake pedal BP is started when the hydraulic pressure control means PC is normal, the start of the brake pedal operation is detected by the stroke sensor BS, and the electromagnetic on-off valve NO in FIG. The communication between the cylinder MC and the wheel cylinder WC is cut off, and the hydraulic pressure corresponding to the brake operation amount is supplied from the hydraulic pressure source PG to the wheel cylinder WC based on the detection values of the stroke sensor BS and the pressure sensor Smc. That is, the drive currents of the first proportional solenoid valve SV1 and the second proportional solenoid valve SV2 are appropriately controlled so that the brake fluid pressure in the wheel cylinder WC detected by the pressure sensor Swc becomes the target brake fluid pressure. . Thus, the hydraulic pressure corresponding to the operation of the brake pedal BP is supplied to the wheel cylinder WC by the hydraulic pressure control means PC.

  In this case, in the master cylinder MC, the brake operating force applied to the input piston 46 is transmitted to the master piston 22 via the compression coil spring 44, the rubber lump pressurizing piston 42, and the rubber lump 40, and the master piston 22 is When the forward movement of the master piston 22 (the advance amount from the return position) reaches a predetermined amount d2, the hole 34 of the master piston 22 is blocked from the port 16 when the input piston 46 moves forward integrally. At this time, since the master piston 22 is almost unable to advance from the position where the hole 34 is blocked with respect to the port 16 by turning on the electromagnetic on-off valve NO, the inside of the stepped cylinder hole 36 of the master piston 22 is the master. The communication hole 38 of the piston 22, the passage formed between the seal member 32 and the annular groove 14 of the housing 10, and the reservoir RS are communicated via the port 16 of the housing 10. It is kept under atmospheric pressure. Accordingly, when the brake operation force applied to the input piston 46 according to the operation of the brake pedal BP becomes equal to or greater than the preload of the compression coil spring 44, the compression coil spring 44 starts to be compressed and the input piston 46 starts to compress the compression coil spring. The compression of the rubber lump 40 is started by the brake operation force transmitted to the rubber lump 40 via 44 and the rubber lump pressurizing piston 42, and the brake pedal BP strokes according to the compression amount of the compression coil spring 44 and the rubber lump 40. To do.

  When the compression of the compression coil spring 44 proceeds and the compression amount reaches a predetermined compression amount d3, the front end of the input piston 46 comes into contact with the rubber mass pressurizing piston 42, and the rubber mass pressurization piston 42 is integrated with the input piston 46. Accordingly, only the rubber mass 40 is compressed, and the brake pedal BP strokes according to the compression amount of the rubber mass 40. Here, the amount of misalignment between the small diameter end 40b of the rubber lump 40 and the front end surface of the rubber lump pressurizing piston is determined by the engagement between the small diameter end 40b of the rubber lump 40 and the recess 42a of the rubber lump pressurizing piston 42. When the lump 40 is compressed by the rubber lump pressurizing piston 42, the rubber lump 40 is restricted to a predetermined amount or less so that the lump 40 is not excessively bent and deformed, so that the rubber lump 40 is excessively bent and deformed. It is compressed without.

  FIG. 4 is a diagram showing the relationship between the operating force applied to the brake pedal BP of the hydraulic brake device and the stroke of the brake pedal BP, and the section OA is due to the compression of the compression coil spring 44 and the rubber mass 40. Yes, section AB is due to compression of the rubber mass 40.

  When an abnormality occurs in the hydraulic pressure control means PC such as the hydraulic pressure source PG, the electromagnetic on-off valve NO is turned off and held in the open position, and as shown in FIG. 3, the port 18 of the master cylinder MC, the wheel cylinder WC, Are in communication. Further, the first proportional solenoid valve SV1 and the second proportional solenoid valve SV2 are also turned off and held in the closed position, and no hydraulic pressure is supplied from the hydraulic pressure source PG to the wheel cylinder WC. When the brake pedal BP is operated in this state, the input piston 46 is advanced in accordance with the operation of the brake pedal BP, and the brake operation force applied to the input piston 46 is compressed by the compression coil spring 44, the rubber lump pressurizing piston 42, and When the master piston 22 moves forward with the input piston 46 through the rubber mass 40 and the master piston 22 advances integrally with the input piston 46, the master piston 22 moves forward (advancing amount from the return position) reaches a predetermined amount d2. Are blocked from the port 16. In this case, since the master piston 22 can be further advanced by turning off the electromagnetic on-off valve NO, the master piston 22 further advances integrally with the input piston 46, and the hydraulic pressure is supplied from the master hydraulic pressure chamber 28 to the wheel cylinder WC. Is done. When the advance amount (advance amount from the return position) of the master piston 22 reaches a predetermined amount d1, the seal member 32 comes into contact with the inner periphery of the housing 10 and the inside of the stepped cylinder hole 36 of the master piston 22 is in the housing 10. Since the input piston 46 is blocked from the port 16 and the input piston 46 is prevented from moving forward with respect to the master piston 22, the input piston 46 and the master piston 22 further move forward together to move from the master hydraulic chamber 28 to the wheel cylinder WC. Brake fluid pressure is supplied.

  The rubber lump 40 may be formed in a substantially truncated cone shape having a small front end and a large rear end, and a recess corresponding to the recess 42 a may be formed on the front end surface of the stepped cylinder hole 36.

  FIG. 5 is a diagram showing a configuration of a master cylinder TMC provided with a brake device stroke simulator SM2 according to the second embodiment of the present invention. In FIG. 5, the master cylinder TMC is a tandem master cylinder and includes a fixed housing 110. The housing 110 has a stepped cylinder hole 112, ports 116 and 117 for connecting to a reservoir RS (see FIG. 6) for storing brake fluid under atmospheric pressure, and a wheel for applying brake torque to the wheel. Ports 118 and 119 for connecting to cylinders WC2 and WC1 (see FIG. 6) are formed. Further, a port 151 is formed in the housing 110. In FIG. 5, the left side is the front and the right side is the rear.

  Seal members 120, 121, 130, 131, and 132 having a cup-shaped cross section are mounted on the inner periphery of the housing 110. A master piston 122 is incorporated in the front portion of the stepped cylinder hole 112. Further, an input piston 146 that is a component of the brake device stroke simulator SM2 is incorporated in the rear portion of the stepped cylinder hole 112. Further, a stopper 124 is incorporated in the rear end portion of the stepped cylinder 112.

  A fluid pressure chamber 129 constituting the brake device stroke simulator SM2 is formed between the input piston 146 and the master piston 122, in other words, in front of the input piston 146. The hydraulic chamber 129 is a component of the brake device stroke simulator SM2. A master hydraulic chamber 128 is formed between the front end wall of the housing 110 and the master piston 122. A compression coil spring 126 is interposed between the front end wall of the housing 110 and the master piston 122 in the master hydraulic chamber 128. In the hydraulic chamber 129, a headed pin 153 slidably passing through the center of the spring retainer 152 and screwed to the front end of the input piston 146 and fixed to the input piston 146, and the input piston 146 A compression coil spring 154 is interposed between the spring retainer 152 and the spring retainer 152. The preload of the compression coil spring 154 is set to be larger than the preload of the compression coil spring 126. When the master cylinder MC is not in operation, the rear end of the master piston 122 abuts against the spring retainer 151 by the compression coil spring 126. The rear end of the large-diameter portion 146a of the input piston 146 is held in the return position in FIG. The small diameter portion 146b of the input piston 146 is connected to a brake pedal BP (see FIG. 6) that is a brake operation member.

  The master piston 122 is formed with a radial hole 134 for communicating the master hydraulic chamber 128 with the port 116 in the state of FIG. The input piston 146 is also formed with a radial hole 135 for communicating the hydraulic chamber 129 with the port 117 in the state shown in FIG. When the input piston 146 advances from the return position, the master piston 122 also advances integrally with the input piston 146 from the return position. When the advance amounts of the input piston 146 and the master piston 122 reach a predetermined amount d5, the hole 135 of the input piston 146 is closed by the seal member 121, and the hole 134 of the master piston 122 is closed by the seal member 120.

  A groove 114 having an axial length larger than the axial length of the seal member 132 is formed on the outer periphery of the master piston 122. An annular chamber 155 formed by the inner periphery of the housing 110, the outer periphery of the master piston 122, and the two seal members 132 and 131 communicates with a port 151 formed in the housing 110. In FIG. 5, the annular chamber 155 communicates with the hydraulic chamber 129 through the groove 114. However, when the master piston 122 advances from the return position and the advance amount reaches a predetermined amount d4, the seal member 132 causes the annular chamber 155 to Chamber 155 is shut off from hydraulic chamber 129.

  In the fixed housing 156, a stepped cylinder hole 157, a port 158 communicating with the port 151 of the cylinder 110, and a port 160 communicating with the atmosphere are formed. A rubber lump 140 and a rubber lump pressurizing piston 142 adjacent to the front of the rubber lump 140 are disposed in the rear part of the stepped cylinder hole 156. In the front large-diameter portion of the stepped cylinder hole 157, a hydraulically responsive piston 159 that receives the hydraulic pressure from the port 158 and is urged rearward, and the hydraulically responsive piston 159 and the rubber lump pressurizing piston 142 are provided. A compression coil spring 144 interposed therebetween is installed. When the hydraulic pressure responsive piston 159 slides backward, in other words, in the direction in which the compression coil spring 144 is compressed, when the compression amount of the compression coil spring 144 reaches a predetermined compression amount d6, the rear end of the hydraulic pressure response piston 159 becomes rubber. It contacts the front end of the mass pressurizing piston 142. The housing 156, the rubber lump 140, the rubber lump pressurizing piston 142, the compression coil spring 144, and the hydraulic pressure responsive piston 159 are constituent elements of the brake simulator stroke simulator SM2.

  The rubber mass 140 is formed in a substantially truncated cone shape having a large-diameter rear end and a small-diameter front end, and is press-fitted into the stepped cylinder hole 157 at the rear end. At the rear end of the rubber lump pressurizing piston 142, the rubber lump 140 compresses the amount of misalignment between the rear end surface of the rubber lump pressurizing piston 142 and the small diameter front end of the rubber lump 140 by engaging with the front end of the rubber lump 140. A recess 142a is formed to restrict the rubber lump 140 to a predetermined amount or less so that the rubber lump 140 is not excessively bent and deformed.

  The rear end surface of the rubber mass pressurizing piston 142 and the rear end surface of the stepped cylinder hole 157 correspond to the pair of rubber mass pressurization surfaces in claim 1.

  The master cylinder TMC shown in FIG. 5 is connected as shown in FIG. 6 to constitute a vehicle hydraulic brake device. In FIG. 6, a normally open electromagnetic on / off valve NO1 is interposed in the hydraulic system H1 (connected to the port 119 shown in FIG. 5), and a system of wheel cylinders (typically WC1) is connected via the electromagnetic on / off valve NO1. And a hydraulic pressure source PG that generates and outputs a predetermined hydraulic pressure regardless of the driver's brake operation. Similarly, a normally open electromagnetic on / off valve NO2 is interposed in the hydraulic system H2 (connected to the port 118 shown in FIG. 5), and other system wheel cylinders (typically WC2) are provided via the electromagnetic on / off valve NO2. The hydraulic pressure source PG is connected.

  The hydraulic pressure source PG includes an electric motor M controlled by the electronic control unit ECU, and a hydraulic pump HP driven by the electric motor M. The input side thereof is connected to the reservoir RS, and the output side is connected to the accumulator AC. Has been. A pressure sensor Sps is connected to the output side, and the detected pressure of the pressure sensor Sps is monitored by the electronic control unit ECU. Based on this monitoring result, the electric motor M is controlled by the electronic control unit ECU so that the hydraulic pressure of the accumulator AC is maintained at a pressure between a predetermined upper limit value and a lower limit value.

  An accumulator AC is connected between the electromagnetic on-off valve NO1 of the hydraulic system H1 and the wheel cylinder WC1 via a normally closed first proportional electromagnetic valve SV1, and the output hydraulic pressure of the hydraulic pressure source PG is The pressure is adjusted and supplied to the wheel cylinder WC1. Further, the electromagnetic on-off valve NO1 and the wheel cylinder WC1 are connected to the reservoir RS via a normally closed second proportional electromagnetic valve SV2, so that the hydraulic pressure of the wheel cylinder WC1 is reduced and regulated. It is configured. Similarly, an accumulator AC is connected between the electromagnetic on-off valve NO2 of the hydraulic system H2 and the wheel cylinder WC2 via a normally-closed first proportional solenoid valve SV3, and the output hydraulic pressure of the hydraulic pressure source PG. Is regulated and supplied to the wheel cylinder WC2. Further, the electromagnetic on-off valve NO2 and the wheel cylinder WC2 are connected to the reservoir RS via a normally closed second proportional electromagnetic valve SV4 so that the hydraulic pressure of the wheel cylinder WC2 is reduced and regulated. It is configured. Thus, the hydraulic pressure control means PC is constituted by the hydraulic pressure source PG, the first proportional solenoid valves SV1 and SV3, the second proportional solenoid valves SV2 and SV4, the electronic control unit, the following sensors, and the like.

  In FIG. 6, the pressure sensor Smc is connected to the upstream side of the electromagnetic on-off valve NO2 in the hydraulic system H2, and the pressure sensor Swc is connected to the downstream side and the downstream side of the electromagnetic on-off valve NO1 in the hydraulic system H1. Yes. The brake pedal BP is provided with a stroke sensor BS for detecting the stroke, and detection signals from these sensors are input to the electronic control unit ECU. These sensors monitor the output hydraulic pressure of the master hydraulic chamber 128, the brake hydraulic pressure of the wheel cylinders WC2 and WC1, and the stroke of the brake pedal BP (note that the pressure sensor Smc is provided on the hydraulic system H1 side). Or may be provided in both hydraulic systems). Further, sensors (typically represented by SN) such as wheel speed sensors and acceleration sensors used for various controls such as anti-lock control are provided, and these detection signals are also input to the electronic control unit ECU. Configured.

  The operation of the vehicle hydraulic brake device according to the above configuration will be described. First, when the operation of the brake pedal BP is started when the hydraulic pressure control means PC is normal, the start of the brake pedal operation is detected by the stroke sensor BS, and the electromagnetic on-off valves NO1 and NO2 in FIG. The communication between the cylinder TMC and the wheel cylinders WC1 and WC2 is cut off, and the hydraulic pressure corresponding to the brake operation amount is supplied from the hydraulic pressure source PG to the wheel cylinders WC1 and WC2 based on the detection values of the stroke sensor BS and the pressure sensor Smc. . That is, the drive currents to the first proportional solenoid valves SV1 and SV3 and the second proportional solenoid valves SV2 and SV4 are set so that the brake fluid pressure in the wheel cylinder detected by the pressure sensor Swc becomes the target brake fluid pressure. It is controlled appropriately. Thus, the hydraulic pressure corresponding to the operation of the brake pedal BP is supplied to the wheel cylinders WC1 and WC2 by the hydraulic pressure control means PC.

  In this case, the input piston 146 and the master piston 122 are advanced from the return position, and when the advance amount from the return position reaches a predetermined amount d5, the hole 135 of the input piston 146 and the hole 134 of the master piston 122 are sealed. And 120 are blocked from ports 117 and 116, respectively. As a result, the master piston 122 can no longer move forward, and only the input piston 146 moves forward. At this time, the annular chamber 155 that is always in communication with the port 158 of the brake simulator stroke simulator is in communication with the hydraulic pressure chamber 129 via the groove 114, so that the hydraulic pressure chamber 129 and the cylinder 156 are operated according to the operation of the brake pedal BP. The hydraulic pressure responsive piston 159 slides backward while compressing the compression coil spring 144, and the rubber mass pressurizing piston 142 slides backward while compressing the rubber mass 140. While moving, the input piston 146 also advances. When the compression amount of the compression coil spring 144 reaches the predetermined compression amount d6, the hydraulic pressure responsive piston 159 comes into contact with the rubber mass pressurizing piston 142, so that further compression of the compression coil spring 144 does not occur, and only the rubber mass 140 is liquid. The pressure piston 159 is compressed by the backward sliding movement, and the input piston 146 moves forward. Accordingly, the brake pedal BP is given a stroke according to the operating force.

When the rubber lump 140 is compressed as described above, the amount of misalignment between the small diameter end of the rubber lump 140 and the rear end surface of the rubber lump pressurizing piston 142 is such that the small diameter end of the rubber lump 140 and the rubber lump pressurizing piston 142 are Since the rubber lump 140 is restricted to a predetermined amount or less so that the rubber lump 140 is not excessively bent and deformed when the rubber lump 140 is compressed by the rubber lump pressurizing piston 142 by the engagement with the recess 142a of the rubber. The lump 140 is compressed without being excessively bent and deformed.

  When an abnormality occurs in the hydraulic pressure control means PC such as the hydraulic pressure source PG, the electromagnetic on-off valves NO1 and NO2 are turned off to the open position, and the master cylinder TMC and the wheel cylinders WC1 and WC2 are opened as shown in FIG. It becomes a communication state. Further, the first proportional solenoid valves SV1 and SV2 and the second proportional solenoid valves SV2 and SV4 are also turned off to the closed position, and no hydraulic pressure is supplied from the hydraulic pressure source PG to the wheel cylinders WC1 and WC2. It becomes. When the brake pedal BP is operated in this state and the input piston 146 and the master piston 122 are advanced from the return position and the advance amount reaches a predetermined amount d5, the holes 135 and 134 are opened to the ports 117 and 116 by the seal members 121 and 120, respectively. Each is blocked. As a result, the brake fluid pressure is supplied from the master fluid pressure chamber 128 to the wheel cylinder WC2. Further, when the amount of advance from the return position of the master piston 122 reaches a predetermined amount d4, the groove 114 formed in the master piston 122 is blocked from the hydraulic chamber 129 by the seal member 132. The brake hydraulic pressure is not supplied to the port 158, and the brake hydraulic pressure is supplied from the hydraulic chamber 129 to the wheel cylinder WC1. Thus, the hydraulic pressure is output to the hydraulic pressure systems H1 and H2 in accordance with the operation of the brake pedal BP.

  The rubber lump 140 may be formed in a substantially truncated cone shape having a small rear end and a large front end, and a recess corresponding to the recess 142a may be formed on the rear end surface of the stepped cylinder hole 157.

  The end surfaces of the small-diameter ends of the rubber lumps 40 and 140 described above are flat, and the concave portions of the end surfaces of the rubber lumps pressure pistons 42 and 142 are formed in a dish shape with a flat bottom. It is not limited. Instead of the first embodiment shown in FIG. 2, it may be configured as in the third embodiment shown in FIG. In the third embodiment shown in FIG. 7, the end surface of the small diameter end 240b of the rubber lump 240 has a hemispherical shape, and the recess 242a of the rubber lump pressurizing piston 242 has a conical shape. In FIG. 7, reference numeral 240 a indicates the large diameter end of the rubber mass 240, and reference numeral 222 indicates the master piston. Also in the third embodiment, the amount of misalignment between the small-diameter end surface of the rubber mass 240 and the rubber mass-side end surface of the rubber mass pressurizing piston 242 is restricted to a predetermined amount or less, and the rubber mass 240 is excessively compressed when the rubber mass 240 is compressed. Bending deformation does not occur. Alternatively, the recess of the rubber mass pressurizing piston may be formed into a simple hole shape, and the small diameter end portion of the rubber mass may be press-fitted into the recess of the rubber mass pressurizing piston.

It is a figure which shows the structure of the master cylinder provided with the stroke simulator for brake devices which concerns on 1st Embodiment of this invention. It is a principal part enlarged view of FIG. It is a figure which shows the structure of the hydraulic brake device for vehicles provided with the master cylinder shown in FIG. FIG. 4 is a diagram showing a correlation between a brake operation force and a brake operation stroke in the vehicle hydraulic brake device shown in FIG. 3. It is a figure which shows the structure of the master cylinder provided with the stroke simulator for brake devices which concerns on 2nd Embodiment of this invention. It is a figure which shows the structure of the hydraulic brake device for vehicles provided with the master cylinder shown in FIG. It is a figure which shows the principal part of the stroke simulator for brake devices which concerns on 3rd Embodiment of this invention.

Explanation of symbols

MC, TMC ... Master cylinder SM1, SM2 ... Stroke simulator for brake device 10, 110 ... Housing 22, 122, 222 ... Master piston 36, 157 ... Cylinder bore 40, 140, 240 ... rubber block 40a, 240a ... large diameter end 40b, 240b ... small diameter end 42, 142, 242 ... rubber block pressurizing piston 42a, 142a, 242a ... recess 44, 144 ...・ Compression coil spring 46, 146 ... Input piston 129 ... Hydraulic chamber

Claims (4)

An input piston coupled to the brake operation member, and at least one that is compressed by a brake operation force transmitted from the brake operation member via the input piston and applies a stroke corresponding to the brake operation force to the brake operation member A pair of elastic members for compressing the rubber mass in a stroke simulator for a brake device, wherein the elastic member is constituted by a roughly truncated cone-shaped rubber mass having a large-diameter end and a small-diameter end. The rubber lump pressurizing surface of the rubber lump is opposed to the end surface of the small-diameter end of the rubber lump, and the end surface of the small-diameter end of the rubber lump is engaged with the small-diameter end of the rubber lump. a recess is formed to be limited to less than a predetermined amount of misalignment amount between the rubber lumps pressing surface Rutotomoni, large diameter of the rubber mass, a hole is incorporated with the rubber mass Stroke simulator braking device, characterized in that it is entering. The brake simulator for a brake device according to claim 1,
Wherein said rubber lump pressure piston on the small diameter end side is positioned adjacent the rubber lump, the said rubber lump pressure piston rubber lumps pressing surface is provided, wherein the recess is formed on the rubber lump pressing surface A stroke simulator for a brake device. The brake simulator for a brake device according to claim 2, wherein the rubber mass and the rubber mass pressurizing piston are arranged coaxially with respect to the input piston in front of the input piston. Stroke simulator for equipment. A stroke simulator brake device according to claim 2,
A hydraulic pressure chamber that generates a hydraulic pressure corresponding to an operating force applied to the brake operating member is formed in front of the input piston, and the rubber lump pressurizing piston is driven by the hydraulic pressure of the hydraulic pressure chamber. A stroke simulator for a brake device.