WO2022249078A1 - Dispositif de réduction de pulsations - Google Patents

Dispositif de réduction de pulsations Download PDF

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Publication number
WO2022249078A1
WO2022249078A1 PCT/IB2022/054875 IB2022054875W WO2022249078A1 WO 2022249078 A1 WO2022249078 A1 WO 2022249078A1 IB 2022054875 W IB2022054875 W IB 2022054875W WO 2022249078 A1 WO2022249078 A1 WO 2022249078A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
biasing member
brake fluid
brake
fluid pressure
Prior art date
Application number
PCT/IB2022/054875
Other languages
English (en)
Japanese (ja)
Inventor
貴紀 坂本
Original Assignee
ロベルト•ボッシュ•ゲゼルシャフト•ミト•ベシュレンクテル•ハフツング
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ロベルト•ボッシュ•ゲゼルシャフト•ミト•ベシュレンクテル•ハフツング filed Critical ロベルト•ボッシュ•ゲゼルシャフト•ミト•ベシュレンクテル•ハフツング
Priority to CN202280038216.XA priority Critical patent/CN117396381A/zh
Priority to JP2023523699A priority patent/JPWO2022249078A1/ja
Priority to DE112022002833.5T priority patent/DE112022002833T5/de
Publication of WO2022249078A1 publication Critical patent/WO2022249078A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4068—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system the additional fluid circuit comprising means for attenuating pressure pulsations

Definitions

  • the present invention relates to a pulsation reduction device for reducing pulsation of brake hydraulic pressure in a brake hydraulic circuit of a vehicle, and a brake hydraulic pressure control device for a vehicle provided with the pulsation reduction device.
  • a brake fluid pressure control device that controls the brake fluid pressure of the brake system in the vehicle
  • a brake fluid pressure circuit that connects the brake fluid pressure between the master cylinder and the wheel cylinder of the vehicle
  • a pump for increasing the brake fluid pressure in the brake fluid pressure circuit
  • a solenoid valve for connecting and disconnecting the brake fluid pressure in the brake fluid pressure circuit.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 2017-061246
  • the pulsation of the brake fluid pressure generated by driving the pump propagates from the brake system to the engine room of the vehicle, etc., causing the vehicle to malfunction.
  • the brake fluid pressure control device has a volume chamber having a variable volume by having a diaphragm that elastically deforms with changes in the brake fluid pressure, and the pulsation of the brake fluid pressure accompanying the driving of the pump is suppressed. can be reduced.
  • the pulsation of the brake fluid pressure may increase due to the pump being controlled at a higher rotational speed, etc., so it is necessary to further reduce the pulsation of the brake fluid pressure. Desired.
  • the present invention has been made against the background of the above problems, and an object thereof is to provide a brake hydraulic pressure control device capable of reducing pulsation of brake hydraulic pressure in a brake hydraulic circuit of a vehicle. do.
  • a pulsation reducing device includes a brake hydraulic circuit (2) that supplies brake hydraulic pressure to a wheel cylinder (12), a pump that boosts the brake hydraulic pressure (60), A pulsation reduction device (37, 80) provided in a vehicle brake system comprising a brake hydraulic circuit (2) for reducing pulsation of brake hydraulic pressure in the brake hydraulic circuit (2), wherein the brake hydraulic circuit (2 ) to which brake fluid pressure is input, a second chamber (8) to output brake fluid pressure to said brake fluid pressure circuit (2), said first chamber ( ) and said second A connection part (80) connecting the chamber (6) and the connection part (80&) is seated on the valve seat (8513) to connect the first chamber (8) and the Move to a non-connected position where the second chamber (8) is not connected, and a connected position where the valve seat (8513) is separated and the first chamber (8) and the second chamber (6) are connected.
  • biasing member comprises a first biasing member (89) and a second biasing member (90) different from the first biasing member (89)
  • said first biasing member (89) has a hysteresis characteristic in which the restoring force in the loading process and the restoring force in the unloading process have different magnitudes when the displacement is the same in the loading process and the unloading process
  • the second biasing member (90) is the restoring force of the first biasing member (89) when the displacement is the same as that of the first biasing member (89) in the unloading process. It is a configuration that has a characteristic that becomes larger than the restoring force in the unloading process.
  • the first biasing member (89) and the second biasing member (90) absorb fluctuations in the brake fluid pressure inside the pulsation reducing device. , It is possible to reduce the pulsation of the brake hydraulic pressure in the brake hydraulic circuit of the vehicle. Alternatively, it may have a configuration other than the matters specifying the invention described in the claims of the present invention.
  • FIG. 1 is a diagram for explaining the configuration of a brake system according to an embodiment
  • the brake system 1 and the brake fluid pressure control device 50 of the present embodiment are configured to be mounted on a four-wheeled vehicle as a vehicle.
  • a brake system equipped with a pressure control device may be configured to be mounted on vehicles other than four-wheeled vehicles, such as unicycles, two-wheeled vehicles, tricycles, trucks, buses, and construction vehicles.
  • FIG. 1 A brake system 1 according to this embodiment will be described with reference to FIGS. 1 and 2.
  • FIG. The brake system 1 is a system that controls the braking of each wheel of the four-wheeled vehicle that is the vehicle 100 .
  • the brake system 1 includes a master cylinder 11 and a piston (not shown) that reciprocates in conjunction with a brake pedal 16 provided in a vehicle. , a wheel cylinder 12 provided corresponding to each wheel of the four-wheeled vehicle to generate a braking force for each wheel, and a brake fluid pressure supplied to each wheel cylinder 12 according to the brake operation by the driver of the vehicle. and a brake fluid pressure control device 50 that controls independently of the state.
  • a booster 17 is interposed between the brake pedal 16 and the piston of the master cylinder 11, and the driver's power transmitted to the brake pedal 16 The pedaling force is amplified and transmitted to the piston of the master cylinder 11.
  • Wheel cylinder 12 is provided in brake caliper 18 . When the hydraulic pressure of the brake fluid in the wheel cylinder 12 increases, the brake pad 19 of the brake caliper 18 is pressed against the rotor 20 to brake the wheel.
  • the brake fluid pressure control device 50 includes a base body 51 in which a brake fluid hydraulic circuit 2 connecting the brake fluid pressure between the master cylinder 11 and the wheel cylinder 12 is formed. Inside the base body 51, there is a main flow path 13 for communicating the master cylinder 11 and the wheel cylinder 12, a sub flow path 14 for releasing the brake fluid in the main flow path 13, and a brake in the sub flow path 14. A supply channel 15 for supplying fluid and a hydraulic circuit 2 including are formed, and the hydraulic circuit 2 is filled with brake fluid.
  • the brake system 1 includes two systems of hydraulic circuits 2 &, 2 as the hydraulic circuit 2 .
  • the hydraulic circuit 2 & is a hydraulic circuit that communicates the master cylinder 1 1 with the wheel cylinder 1 2 of the F scale by the main flow path 1 3 .
  • the hydraulic circuit 2 is connected to the master cylinder 1 1 and the wheels by the main flow path 1 3 . It is a hydraulic circuit that communicates with the wheel cylinders 1 and 2 of the scale.
  • These hydraulic circuits 2 and 213 have the same configuration except that the wheel cylinder 12 that communicates with them is different.
  • the upstream end of the sub-channel 14 is connected to the middle part 13 of the main channel 13, and the downstream end of the sub-channel 14 is connected to the middle part of the main channel 13. 1 3 1) are connected. Further, the upstream end of the supply channel 15 communicates with the master cylinder 11, and the downstream end of the supply channel 15 is connected to the middle part 14 of the sub-channel 14. .
  • the upstream side of the sub-flow path 14 refers to the upstream side of the brake fluid flow when the pump is driven and the brake fluid is returned from the wheel cylinder to the master cylinder.
  • the downstream side refers to the downstream side in the flow of the brake fluid.
  • an inlet valve (EV) 31 In the area between the middle portion 13b and the middle portion 13& of the main flow passage 13 (the area on the wheel cylinder 12 side with reference to the middle portion 13b) is equipped with an inlet valve (EV) 31.
  • a release valve ( ) 32 is provided in a region between the middle portion 13 and the middle portion 14 of the sub-channel 14 .
  • An accumulator 33 is provided in the area between the release valve 32 and the middle portion 14& of the sub-channel 14.
  • the inlet valve 31 is, for example, an electromagnetic valve that opens in a non-energized state and closes in an energized state.
  • the loosening valve 32 is, for example, an electromagnetic valve that closes in a non-energized state and opens in an energized state.
  • the middle portion 1 4 & and the middle portion 1 3 A pump 60 is provided in the area between The suction side of the pump 60 communicates with the midway portion 14 .
  • the discharge side of the pump 60 communicates with the middle portion 1313 of the sub-channel 14 .
  • the brake system 1 includes a suction flow path 142 and a discharge flow path 140, which are part of the sub flow path 14, and a brake fluid pressure control device 50. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the suction flow path 142 forms a flow path between the middle portion 13 of the sub-flow path 14 and the suction side of the pump 60, and the discharge flow path 140 forms the discharge side of the pump 60. It constitutes a flow path between the sub-flow path 14 and the middle portion 1313.
  • the brake fluid pressure control device 50 is provided with a pulsation reduction section 80 that attenuates the pulsation of the brake fluid discharged from the pump 60 onto the discharge passage 140.
  • the discharge side of the pump 60 is connected to the inflow opening 91b (see FIG. 2) into which the brake fluid of the pulsation reducing section 80 flows, and the brake fluid temporarily stored in the pulsation reducing section 80
  • the outflow opening 910 (see FIG. 2) through which the liquid flows out is connected to the middle part 13 of the sub-channel.
  • the flow path forming between the discharge side of the pump and the inflow opening 9113 will be referred to as the first discharge flow path 140&, the outflow opening 91 and the middle portion 13 of the sub-flow path.
  • a first switching valve 35 is provided in a region of the main flow path 13 on the master cylinder 11 side with respect to the midway portion 13.
  • the supply channel 15 is equipped with a second switching valve (3 ⁇ )
  • the damper unit 37 is provided in the region between the second switching valve 36 and the middle portion 1313 of the supply channel 15 .
  • the first switching valve 35 is, for example, an electromagnetic valve that opens in a non-energized state and closes in an energized state.
  • the second switching valve 36 is, for example, an electromagnetic valve that closes in a non-energized state and opens in an energized state.
  • both the discharge channel 140 and the supply channel 15 are provided with the damper unit 37 and the pulsation reducing unit 80 as pulsation reducing devices.
  • the damper unit 37 may not be provided depending on the required pulsation damping characteristics.
  • Each member (loading valve 31, release valve 32, accumulator 33, pump 60, first switching valve 35, second switching valve 36, damper unit 37 and pulsation reduction section 80) is It may be provided collectively on one base 51, or may be provided separately on a plurality of bases 51.
  • the base body 51, each member provided on the base body 51, the controller 52, and the brake fluid pressure control device 50 are configured.
  • the operations of the charging valve 31, the releasing valve 32, the pump 60, the first switching valve 35, and the second switching valve 36 are controlled by the controller 52.
  • the hydraulic pressure of the brake fluid in the wheel cylinder 12 is controlled. That is, the controller 52 controls the operations of the charging valve 31, the releasing valve 32, the pump 60, the first switching valve 35, and the second switching valve 36. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the controller 52 may be one, or may be divided into a plurality. Also, the controller 52 may be attached to the base 51, or may be attached to another member. In addition, part or all of the controller 52 may be composed of, for example, a microcomputer, a microprocessor unit, or the like, or may be composed of an updatable item such as firmware. It may be a program module or the like that is executed by a command from the ⁇ 11 or the like.
  • the controller 52 for example, implements the following hydraulic pressure control actions in addition to well-known hydraulic pressure control actions (eight 83 control actions, 1/2 control actions, etc.).
  • the controller 5 2 keeps the inlet valve 3 1 open so that the flow from the middle portion 1 3 13 of the main flow path 1 3 to the wheel cylinder 1 2 Allows flow of brake fluid.
  • the controller 52 also limits the flow of brake fluid from the wheel cylinder 12 to the accumulator 33 by keeping the release valve 32 closed.
  • the controller 52 closes the first switching valve 35 so that the brake fluid in the flow path from the master cylinder 11 to the middle portion 1313 of the main flow path 13 without passing through the pump 60. restrict the flow of
  • the controller 52 opens the second switching valve 36 to reduce the flow of brake fluid in the flow path from the master cylinder 11 to the middle portion 1313 of the main flow path 13 via the pump 60. allow flow.
  • the controller 52 drives the pump 60 to raise (increase) the hydraulic pressure of the brake fluid in the wheel cylinder 12.
  • the controller 52 opens the first switching valve 35 and closes the second switching valve 36. And, by stopping the driving of the pump 60, the active pressure increase control operation is terminated.
  • the pulsation generated in the brake fluid may be transmitted to the wheel cylinder 12 through the secondary flow path 14 and the main flow path 13. There is This pulsation is also transmitted to the engine room housing the brake fluid pressure control device 50 of the brake system 1. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the brake fluid pressure control device 50 of the brake system 1 of this embodiment can reduce the pulsation that occurs when the pump 60 is driven.
  • the brake fluid pressure control device 50 of the present embodiment include the damper unit 37 as shown in FIG.
  • the damper unit 37 can reduce the pulsation of the brake fluid propagating from the pump 60 to the brake pedal 16.
  • damper unit 37 when damper unit 37 is provided in brake system 1 in which booster 17 is omitted, damper unit 37 is provided at the upstream end of supply channel 15. It may be provided in a region between the part and the second switching valve 36. By providing the damper unit 37 at such a position, when the user depresses and operates the brake pedal 16, the brake fluid can flow into the damper unit 37, and the hydraulic pressure transmitted to the brake pedal 16 is increased. The reaction force of the brake fluid in circuit 2 is reduced. Therefore, when the user operates the brake pedal, an operation amount of the brake pedal 16 similar to that of the brake system 1 having the booster 17 can be obtained. Therefore, the user can obtain the same feeling of use of the brake system 1 without the booster 17 as with the brake system 1 provided with the booster 17 .
  • FIG. Fig. 2 shows the pump 60 and the pulsation reduction unit 80 mounted on the base body 51 of the brake fluid pressure control device 50, and the drive shaft 57 for driving the piston 62 of the pump 60 removed.
  • FIG. 4 is a partial cross-sectional view of the substrate 51 in a state; The two-dot chain line in FIG. 2 indicates the drive shaft 57 and the eccentric portion 57 formed on the drive shaft 57. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the base body 51 is formed with a housing chamber 59 in which a drive shaft 57 for driving the piston 62 of the pump 60 is provided.
  • the accommodation chamber 59 is a bottomed hole formed in the outer wall of the base 51.
  • the base body 51 is formed with a housing chamber 53 for housing the pump 60 .
  • These storage chambers 53 are stepped through holes penetrating from the outer wall of the base body 51 to the storage chamber 59 .
  • the pump 60 housed in the housing chamber 53 includes a cylinder 61, a piston 62 and the like.
  • Cylinder 61 is formed in a bottomed cylindrical shape having bottom 6113 .
  • One end side of the piston 62 is accommodated in the cylinder 61.
  • a space surrounded by the inner peripheral surface of the cylinder 61 and the one end of the piston 62 serves as the pump chamber 63 .
  • This piston 62 can freely reciprocate in the axial direction of the cylinder 61 .
  • An end portion 62, which is the other end portion of the piston 62, protrudes into the housing chamber 59.
  • an annular seal member 66 is attached to the portion of the piston 62 that is housed in the cylinder 61. This seal member 66 prevents brake fluid from leaking between the outer peripheral surface of the piston 62 and the inner peripheral surface of the cylinder 61 .
  • a spring 67 is housed between the bottom 6113 and the piston 62, that is, in the pump chamber 63.
  • This spring 67 always urges the piston 62 toward the storage chamber 59 side.
  • the end portion 62 & of the piston 62 is in contact with the eccentric portion 57 & formed on the drive shaft 57 within the accommodation chamber 59 .
  • the eccentric portion 57 is eccentric with respect to the center of rotation of the drive shaft 57. Therefore, when the drive shaft 57 is rotated by a drive source (not shown), the eccentric portion 57 & rotates eccentrically with respect to the center of rotation of the drive shaft 57 . That is, the eccentric rotational motion of the eccentric portion 57 & causes the piston 62, whose end portion 62 & is in contact with the eccentric portion 57 &, to reciprocate in the axial direction of the cylinder 61. Become.
  • a portion of the piston 62 protruding from the cylinder 61 is slidably guided by a guide member 68 provided on the inner peripheral surface of the housing chamber 53.
  • An annular seal member 69 is attached adjacent to the guide member 68 in the storage chamber 53 . This sealing member 69 seals the outflow from the outer peripheral surface of the piston 62 in a liquid-tight manner.
  • the piston 62 is axially formed with a bottomed hole 62 that opens toward the pump chamber 63 side of the cylinder 61 .
  • the piston 62 is also formed with an intake port 620, which is a through hole that communicates between the outer peripheral surface of the piston and the bottomed hole 62.
  • the piston 62 is provided with a suction valve (not shown) for freely opening and closing the opening of the bottomed hole 62b. This suction valve opens the bottomed hole 6 2 13. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • a cylindrical filter 70 is attached to the end of the cylinder 61 on the side of the piston 62 so as to cover the opening of the intake port 62 of the piston 62 .
  • the bottom 6113 of the cylinder 61 is formed with a through hole 610 that communicates the pump chamber 63 with the outside of the cylinder 61.
  • a discharge valve 64 is provided on the opening side opposite to the pump chamber 63 in the through hole 610.
  • the discharge valve 64 includes a ball valve 64, a valve seat 6413 formed around the opening edge of the through hole 610 and on which the ball valve 64 & can be attached and detached, and a valve seat for the ball valve 64. It is provided with a spring 640 that biases it in a direction to seat it on 64.
  • This discharge valve 6 4 is arranged between the cylinder 6 1 and the cover 6 5 .
  • the cover 65 is attached to the bottom 61 of the cylinder 61, for example, by press fitting.
  • the cover 65 is formed with a bottomed hole 65 & having an opening at a position facing the through hole 610 of the bottom 6113 .
  • the spring 64 of the discharge valve 64. is housed in the bottomed pit 6 5 &.
  • the inner diameter of the bottomed hole 65 & is larger than the outer diameter of the ball valve 64 . Therefore, when the ball valve 64 is separated from the valve seat 64I), the ball valve 64 moves into the bottomed hole 65 & .
  • the hydraulic pressure of the brake fluid in the pump chamber 63 of the cylinder 61 increased, and the force of the brake fluid pushing the ball valve 64& became larger than the biasing force of the spring 640.
  • the ball valve 64& is separated from the valve seat 643 ⁇ 4>, and the pump chamber 63 and the bottomed hole 65 of the cover 65 communicate with each other through the through hole 610.
  • the brake fluid in the pump chamber 63 flows into the bottomed hole 65.
  • the cover 65 is formed with a groove as a discharge port 65 that communicates the outside of the cover 65 with the bottomed hole 65 &.
  • the brake fluid that has flowed into the bottomed hole 65 of the cover 65 flows from the discharge port 6513 to the outside of the cover 65, that is, the outside of the pump 60 (for example, a flow path leading to the pulsation reduction section 80). Dispensed.
  • the pump 60 configured in this manner is accommodated in the accommodation chamber 53 formed in the base 51 as described above. Specifically, in a state in which the annular protrusion 61 formed on the outer peripheral portion of the cylinder 61 is in contact with the stepped portion 53 & of the storage chamber 53, the periphery of the opening of the storage chamber 53 The pump 60 is fixed in the housing chamber 53 of the base 51 by caulking.
  • the discharge port 6 of the pump 60 is positioned between the outer peripheral surface of the pump 60 and the inner peripheral surface of the accommodation chamber 53.
  • a discharge chamber 54 which is a space communicating with 5, is formed. That is, the discharge chamber 54 is an annular space formed on the outer peripheral side of the pump 60 so as to communicate with the discharge port 65 of the pump 60 .
  • the discharge chamber 54 constitutes a part of the first discharge channel 140 & as described later. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the space between the annular protrusion 61 & of the cylinder 61 and the cover 65 is partitioned into two spaces by the partition 71.
  • a space on the cover 65 side of the partition portion 71 serves as the discharge chamber 54 .
  • a space on the projecting portion 6 1 & side of the partitioning portion 7 1 forms an annular flow path 5 5 .
  • the partition portion 71 is composed of a projecting portion annularly projecting from the outer peripheral surface of the cylinder 61 and a ring provided on the projecting portion. ing.
  • the configuration of the partition 71 is arbitrary.
  • the partitioning portion 71 may be configured only by a projecting portion annularly projecting from the outer peripheral surface of the cylinder 61 .
  • the partition portion 71 may be configured only by the O-ring provided on the outer peripheral surface of the cylinder 61.
  • annular channel 56 which is a space that communicates with the suction port 620 of 60, is formed. That is, the annular channel 56 is a space formed annularly on the outer peripheral side of the pump 60 so as to communicate with the suction port 62 of the pump 60 .
  • the annular channel 56 is formed between the annular protrusion 61 & of the cylinder 61 and the seal member 69 .
  • the annular flow path 56 is formed on the outer peripheral side of the filter 70 provided so as to cover the opening of the suction port 620.
  • the annular channel 56 communicates with the middle portion 14 & of the subchannel 14 in FIG. 1 by an internal channel (not shown) formed in the base 51.
  • the annular channel 56 constitutes a part of the secondary channel 14.
  • the suction port 62 of the pump 60 when the pump 60 is housed in the housing chamber 53. and 1 4 & in the middle must be in communication.
  • having the annular flow path 56 when housing the pump 60 in the housing chamber 53, it is not necessary to align the suction port 620 of the pump 60 with the middle portion 14& for communication. becomes. Therefore, having the annular flow path 56 facilitates assembly of the brake hydraulic pressure control device 50 .
  • the annular flow path 56 when processing the storage chamber 53 into the base body 51, a part of the sub-flow path 14 is also processed. Therefore, the processing cost of the base body 51, that is, the manufacturing cost of the brake fluid pressure control device 50 can be reduced. In addition, by having the annular flow path 56, the space on the outer peripheral side of the pump 60 can be effectively used as the sub-flow path 14, so the base body 51, that is, the brake fluid pressure control device 50 can be made smaller. .
  • the discharge chamber 54 formed on the outer peripheral surface side of the pump 60 is connected to the first discharge flow path 140& which constitutes part of the discharge flow path 140. It is connected.
  • the containment chamber 58 contains the pulsation reduction section 80. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the discharge chamber 54 is connected to the inflow opening 91 of the pulsation reducing section 80 via the first discharge channel 140&. In the figure, it is constructed such that the brake fluid flows in from the lateral direction with respect to the axis of the housing chamber 58 of the pulsation reducing section 80 . and an outflow opening 91 located at the bottom of the containment chamber 58. is connected to the second discharge channel 14013.
  • the second discharge channel 14013 communicates with the middle portion 13 of the main channel 13 in FIG.
  • the pulsation reduction device according to this embodiment will be described with reference to FIGS. 3 to 6.
  • FIG. The configuration of the pulsation reduction device described later will be described using an example of application to the pulsation reduction section 80, but the configuration may be applied to both the damper unit 37 and the pulsation reduction section 80. However, it may be applied to only one of the damper unit 37 and the pulsation reduction section 80.
  • the brake hydraulic circuit 2 is configured to include the damper unit 37 and the pulsation reduction section 80 as a pulsation reduction device, but the brake hydraulic circuit 2 is a pulsation reduction device.
  • a configuration including only the pulsation reducing section 80 is also possible.
  • the damper unit 37 and the pulsation reduction section 80 may be collectively referred to as a pulsation reduction device.
  • the base body 51 of the brake fluid pressure control device 50 has a pulsation reducing portion 80 formed by a cylindrical bore drilled along the axis 8XI.
  • the accommodation chamber 58 is composed of a large diameter portion 58 formed on the outer peripheral side of the base 51, and a smaller diameter than the large diameter portion 58 & and an inner side of the base 51 from the large diameter portion 58 &. a formed intermediate diameter portion 58I), a small diameter portion 58 ⁇ 3 having a smaller diameter than the intermediate diameter portion 5813 and formed on the inner side of the base body 51 from the intermediate diameter portion 5813, including.
  • These large-diameter portion 58, medium-diameter portion 581), and small-diameter portion 58 ⁇ 3 are drilled with the axis 81 as a common central axis.
  • the pump An inlet opening 9113 is provided through which the brake fluid 1 to be dispensed flows.
  • an outflow opening 91 that communicates with the main flow path 13 and allows the brake fluid 2 to flow out from the pulsation reducing section 80 to the main flow path 13 is provided in the bottom surface 58 1 of the small diameter portion 58 . It is In addition, the opening 586 of the housing chamber 58 leading to the outer peripheral surface of the base 51 is closed by the closing member 81.
  • a disk-shaped partition member 85 having an outer diameter approximately equal to the inner diameter of the medium-diameter portion 58 has a smaller diameter than the inflow opening 9113. It is fitted along the inner peripheral surface of the medium-diameter portion 58 on the ⁇ side of the portion 58 .
  • the inner peripheral surface of the intermediate diameter portion 5813, the stepped surface connecting the large diameter portion 58 with the intermediate diameter portion 5813, the inner peripheral surface of the large diameter portion 58 & , and the closing member A first chamber defined by one end surface of the partition member 81 and one end surface of the partition member 85 is formed.
  • the inner peripheral surface of the first chamber is provided with an inflow opening 9113 communicating with the discharge port 65 of the pump 60, and the brake fluid pressure boosted by the pump 60 is input to the first chamber. It is designed to be Also, the second chamber 8 is defined by the inner peripheral surface and bottom surface of the small diameter portion 58° and the one end surface of the partition member 85 . The inner peripheral surface of the second chamber 8 is provided with an outflow opening 910 that communicates with the main flow path 13 of the brake hydraulic circuit 2 .
  • a first moving body 83 is formed in a disc shape with an outer diameter approximately equal to the inner diameter of the large-diameter portion 58 & , and moves in the direction of the axis X1; 1
  • a seal member 84 for sealing between the outer peripheral surface of the moving body 83 and the inner peripheral surface of the large diameter portion 58, and a first moving body 83 for biasing the first moving body 83 toward the intermediate diameter portion 58 Biasing members 8 2 and are arranged.
  • a sealing member 84 is arranged on the outer peripheral surface of the first moving body 83, and the axial line 8X1 extends along the inner peripheral surface of the large diameter portion 58a with the sealing member 84 interposed. It is designed to slide in one direction.
  • steel can be used in order to make the sliding smooth.
  • the first chamber 8 Divided into two regions by the moving body 83, the first region 8 is divided by the inner peripheral surface of the intermediate diameter portion, one end surface of the partition member 85, and one end surface of the first moving body 83. 1 is formed, and a second region 2 defined by the inner peripheral surface of the large diameter portion 58&, one end surface of the first moving body 83, and one end surface of the closing member 81 is formed.
  • the volume of the first region 81 is expanded and the volume of the second region 2 is reduced, while the first moving body 83 is , the volume of the first region 81 is reduced and the volume of the second region 2 is expanded by moving to the partition member 85 side (see FIG. 4).
  • the first moving body 83 is moved against the biasing force of the first biasing member 82 by the brake fluid pressure input from the inflow opening 91. Since part of the energy of the brake fluid pressure is consumed by the first urging member 82, the change speed and variation width of the brake fluid pressure in the first chamber are determined by the brake fluid pressure input to the first chamber. It is possible to reduce the pulsation of the brake hydraulic pressure output from the pulsation reduction device.
  • the partition member 85 is formed with, for example, two communication holes 85 for communicating between the medium diameter portion 5813 side and the small diameter portion 58 side. .
  • a first valve seat 85 to be seated on a first valve body 86 corresponding to each communicating hole 85 & is formed on the small diameter portion 580 side of each communicating hole 85.
  • the members (the second biasing member 89 and the third biasing member 90) form a connecting portion 80 & which connects the first chamber 8 and the second chamber 6.
  • the pulsation reducing section 80 of this embodiment includes two first valve seats 8513 in the partition member 85, and two first valve seats 85 corresponding to the first valve seats 85.
  • the configuration includes one valve disc 86
  • the pulsation reduction section may have a configuration including one first valve seat and one first valve disc, or may have three or more first valve seats and three or more first valve discs. may be provided.
  • Small diameter portion 58 (Inside the shell, the first valve body 86 and the small diameter portion 58 are formed in a disk shape with an outer diameter smaller than the inner diameter of the axis 8X a second moving body 87 that moves in one direction; a second biasing member 89 that biases the second moving body 87 toward the partition member 85; A second valve body 88 seated on the second valve seat 876 and a third biasing member 90 for biasing the second valve body 88 toward the second valve seat 876 are arranged. ing.
  • the second moving body 87 includes a disk-shaped main body 87 & and is formed on one end surface side of the main body 87 & to position the first valve body 86.
  • a second valve seat 876 is formed.
  • the first valve body 86 is arranged in the groove part 87 of the second moving body 87, so that the first valve body 86 and the second moving body 87 are aligned. A relationship is determined so that the first valve body 86 can be seated on the first valve seat 866 .
  • the second biasing member 89 is formed in a ring shape, and the inner peripheral surface of the second biasing member 89 is aligned with the protrusion 870 of the second moving body 87.
  • the positional relationship between the second biasing member 89 and the second moving body 87 is determined by being arranged to contact the outer peripheral surface of the second biasing member 89, and the second biasing member 89 presses the second moving body 87.
  • the moving body 87 is biased toward the partition member 85, and the second biasing member 89 pushes the first valve body 86 toward the first valve seat 8513 via the second moving body 87. It is designed to be urged to.
  • the second valve body 88 is biased by the third biasing member 90 and is seated on the second valve seat 876.
  • the third biasing member 90 By urging the second valve body 88 toward the second valve seat 876 by the third urging member 90, ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the first valve body 86 is biased toward the first valve seat 85 by the third biasing member 90.
  • the first valve body 86 and the second moving body 87 are biased toward the first valve seat 85 by the second biasing member 89 and the third biasing member 90 .
  • the second biasing member 89 is made of a resin material such as elastomer rubber, as will be described later.
  • the third region 1 is formed by the bottom surface of the small diameter portion 580, the inner peripheral surface of the second biasing member 89, the outer peripheral surface of the second moving body 87, and the second valve body.
  • a fourth region 82 defined by the outer peripheral surface of 88 is formed.
  • the volume of the third region 1 is expanded and the volume of the fourth region 62 is reduced, while the second moving body By moving 87 toward the partition member 85 side, the volume of the third region 81 is reduced and the volume of the fourth region 62 is increased (see FIG. 4).
  • the first biasing member 82 and the second biasing member 89 are, as shown in FIG. When the displacement is the same (3) in the process of changing from 1 to 0), the restoring force in the loading process and the restoring force in the unloading process have different magnitudes. It consists of a body and is formed as a ring-shaped member. As a material for the first biasing member 82 and the second biasing member 89, for example, an elastomer spring made of a material such as ethylene-propylene-diene rubber or silicone can be used. Also, the first biasing member 82 and the second biasing member 89 may be made of one material, or may be made of a plurality of materials. For example, it may be configured such that a wire having a relatively low rebound resilience is sandwiched between silicon having a relatively high rebound resilience. of material ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the third biasing member 90 is the same displacement of 3 in the unloading process (the process in which the displacement changes from 1 to 0) or the loading process (the process in which the displacement changes from 0 to 31) of the second biasing member 89. It is composed of an elastic body having a characteristic scale 2 larger than the restoring force.
  • a metal spring can be used as the third biasing member 90 .
  • the third biasing member 90 may be made of one material, or may be made of a plurality of materials. Depending on the combination and shape of the materials, it is possible to adjust the rebound resilience of the urging member according to the characteristic pulsation frequency caused by the performance of the brake fluid pressure pump 60.
  • the brake fluid pressure on the discharge side of the pump 60 rises to a predetermined first pressure value 1 immediately after the pump 60 starts to be driven.
  • the brake fluid pressure acts on the first moving body 83, and the first moving body 83 acts on the first urging member 8 2 is moved against the biasing force.
  • the first moving body 83 is moved against the biasing force of the first biasing member 82, part of the energy of the brake hydraulic pressure is consumed.
  • the first valve body 86 By moving against the biasing force of the biasing member 90, the first valve body 86 is separated from the first valve seat 8513, and the first and second chambers are connected. At this time, since the first valve body 86 and the second moving body 87 are moved against the biasing forces of the second biasing member 89 and the third biasing member 90, these biasing members A part of the energy of the brake fluid pressure is consumed by the second chamber, and the fluctuation of the brake fluid pressure in the third area 61 of the second chamber 6 is changed to the brake fluid in the first area 81 of the first chamber 8. reduced compared to pressure fluctuations.
  • the brake fluid pressure fluctuations in the fourth region 2 of the second chamber are reduced compared to the brake fluid pressure fluctuations in the third region 81 of the second chamber 6. Therefore, in the pulsation reduction device, the brake hydraulic pressure fluctuates due to the biasing forces of the first biasing member 82, the second biasing member 89, and the third biasing member 90 and the sliding resistance of the seal member 84. Due to the reduction, the pulsation of the brake fluid pressure output from the pulsation reduction device to the brake fluid pressure circuit 2 is reduced compared to the pulsation of the brake fluid pressure on the discharge side of the pump 60 .
  • the brake fluid pressure in 18 can exceed the second pressure value 2. As a result, the drop width of the brake fluid pressure in the fourth region 82 can be reduced.
  • the pulsation reducing device of the present embodiment includes the first valve body 86 and the first valve seat 85.
  • the first valve body 86 is separated from the first valve seat 8513;
  • the second valve body 88 is seated on the second valve seat 876;
  • the state in which the valve body 88 is separated from the second valve seat 876 is sequentially changed according to the fluctuation of the brake fluid pressure accompanying the driving of the pump 60, and
  • the pulsation of the brake fluid pressure can be reduced.
  • a vehicle brake system 1 includes a brake hydraulic circuit 2 that supplies brake hydraulic pressure from a master cylinder 11 to a wheel cylinder 12, and the brake hydraulic circuit A pump 60 for increasing the brake fluid pressure in 2 and a brake fluid pressure control device 50 for controlling the brake fluid pressure are provided.
  • pulsation may occur in the brake fluid pressure as the pump 60 is driven. or transmitted to the engine room of a vehicle equipped with a brake system 1 equipped with a pump 60, causing discomfort or discomfort to the vehicle driver (for example, the vehicle driver, fellow passengers, people outside the vehicle, etc.). Possible noise may occur.
  • the brake hydraulic pressure control device 50 of the brake system 1 of this embodiment includes a pulsation reduction device that reduces the pulsation of the brake hydraulic pressure in the brake hydraulic circuit 2.
  • the pulsation reduction device includes a first chamber 8 to which brake fluid pressure is input from the brake fluid pressure circuit 2, a second chamber 8 to output the brake fluid pressure to the brake fluid pressure circuit 2, a first chamber 8 and a second chamber.
  • valve seat 85I is separated from the connection position where the first chamber 8 and the second chamber 13 are connected, the first valve body 86 moves to the first valve body 86, and the first valve body 86 moves to the first a biasing member that biases toward the valve seat 8513, the biasing member comprising a second biasing member 89 and a third biasing member 9 different from the second biasing member 89
  • the second biasing member 89 has the same displacement 3 in the loading process (the process in which the displacement changes from 0 to 31) and the unloading process (the process in which the displacement changes from 31 to 0) Furthermore, it has a hysteresis characteristic in which the restoring force in the loading process and the restoring force in the unloading process have different magnitudes
  • the third biasing member 90 has the same displacement as the second
  • Restoring force in a certain unloading process (process where the displacement changes from 8 2 to ⁇ )? is larger than the restoring force in the unloading process of the second biasing member 89 (the process in which the displacement is 81 to 0) when the displacement is the same 3. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the connecting portion 80 between the first chamber 8 and the second chamber 8 connects the first valve body 86 and the first valve body 86 to the first valve seat 8. Equipped with a second biasing member 89 and a third biasing member 90 for biasing to the 5th side, and when the second biasing member 89 has the same displacement in the loading process and the unloading process, the load When there is a hysteresis characteristic in which the restoring force in the process and the restoring force in the unloading process have different magnitudes, and the third biasing member 90 has the same displacement 3 as the second biasing member 89
  • the restoring force O in the unloading process of the second urging member 89 has a characteristic of being larger than the restoring force in the unloading process of the second biasing member 89 when the same displacement is 3 .
  • the first valve body 86 When the input brake fluid pressure input from the pressure circuit 2 exceeds the predetermined first pressure value 1 and the brake fluid pressure on the first chamber side is higher than the brake fluid pressure on the second chamber side , the first valve body 86 is biased by the second biasing member 89 and the third biasing member 90 . As a result, the first valve body 86 is operated by the second urging member 89 and the third urging member 89 in the process in which the brake fluid pressure input to the first chamber is increased as the pump 60 is driven. It will move against the two biasing forces of member 90 . That is, in this process, part of the energy of the brake fluid pressure input to the first chamber 8 is consumed by the two urging members and output to the second chamber. The change speed of the brake fluid pressure that rises in the first chamber can be made lower than the change speed of the brake fluid pressure that is input on the first chamber side.
  • the second biasing member 89 has the hysteresis characteristic of the restoring force and the restoring force in the unloading process of the third biasing member 90 is the same displacement 8 , the second biasing member 89 Since the restoring force of the force member 89 is larger than the restoring force of the force member 89, the speed at which the second force force member 89 returns to the unloaded state in the unloading process is equal to the unloaded state of the third force member 90.
  • the input brake fluid pressure input from the brake fluid pressure circuit 2 to the first chamber 8 exceeds the second pressure value 2, and the first After the brake fluid pressure on the chamber side becomes lower than the brake fluid pressure on the second chamber side, the first valve body 86 is biased only by the third biasing member 90 for a predetermined period of time. As a result, the first valve body 86 is urged by the third urging member to move toward the first valve seat 8513 in the course of the brake fluid pressure in the first chamber 8 decreasing. As a result, the brake fluid pressure in the first chamber drops to a predetermined second pressure value 2 lower than the first pressure value 1, whereby the first valve body 86 is seated on the first valve seat 85.
  • the first valve body 86 will apply only the biasing force of the third biasing member 90.
  • part of the energy of the brake fluid pressure input to the first chamber is not consumed by the second biasing member 89, and the corresponding energy is used to increase the brake fluid pressure in the second chamber. used. That is, in this case, the drop width of the brake fluid pressure on the second chamber 8 side can be reduced. Therefore, by the pulsation reduction device configured as described above, the brake pressure in the second chamber that is output to the brake hydraulic circuit 2 is reduced. ⁇ 0 2022/249078 ⁇ (:17132022/054875
  • the second biasing member 89 is an elastomer spring made of, for example, chetylene-propylene-diene rubber. , formed of a material such as silicon. According to such a configuration, when the second biasing member 89 has the same displacement in the loading process and the unloading overload, the restoring force in the loading process and the restoring force in the unloading process are equal to each other. It can have hysteresis characteristics of different magnitudes and the pulsation reducing device can reduce the pulsation of the brake hydraulic pressure in the brake hydraulic circuit 2 of the vehicle.
  • the third biasing member 90 is a metal spring. According to such a configuration, the third biasing member 90 has the same restoring force of 8 as the displacement 8 of the second biasing member 89 in the unloading process. is larger than the restoring force in the unloading process of the second biasing member 89 when the displacement is the same 3, and the pulsation reducing device reduces the vehicle brake hydraulic circuit 2 It is possible to reduce the pulsation of the brake fluid pressure inside.
  • the pulsation reducing device of the present embodiment includes a first moving body 83 that moves in the direction of the axis X1 in the first chamber 8 on the upstream side of the connecting portion 80&; 1.
  • a first urging member 82 for urging a moving body 83 is provided, and the first moving body 83 partitions the first chamber 8 into two areas to move the first moving body 83.
  • the volume of the first region 81 to which the brake fluid pressure is input from the brake fluid pressure circuit 2 fluctuates.
  • the pulsation reducing device of the present embodiment includes, in the first chamber 8 upstream of the connection portion 80, a first moving body 83 that moves in the direction of the axis X1;
  • a first biasing member 82 for biasing the moving body 83 is provided, and the first biasing member 82 is an elastomer spring made of, for example, ethylene-propylene-diene rubber. , and are made of a material such as silicon.
  • the restoring force in the overloading process and the restoring force in the unloading process are equal to each other. can have hysteresis characteristics with different magnitudes, and the pulsation reduction device can reduce the pulsation of the brake hydraulic pressure in the brake hydraulic circuit 2 of the vehicle.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne un dispositif de réduction de pulsations prévu dans un système de frein hydraulique d'un véhicule. Le dispositif de réduction de pulsations comprend une première chambre (A) dans laquelle une pression hydraulique de frein est entrée à partir d'un circuit hydraulique de frein (2), une seconde chambre (B) qui délivre la pression hydraulique de frein au circuit hydraulique de frein (2), et une partie de raccordement (80a) qui raccorde la première chambre (A) et la seconde chambre (B). La partie de raccordement (80a) comprend un premier corps de vanne (86) qui se déplace vers une position de non raccordement dans laquelle le premier corps de vanne repose sur un premier siège de vanne (85b) et ne raccorde pas la première chambre (A) et la seconde chambre (B) et une position de raccordement dans laquelle le premier corps de vanne est séparé du premier siège de vanne (85b) et raccorde la première chambre (A) et la seconde chambre (B) et un élément de poussée qui pousse le premier corps de vanne (86) vers le premier siège de vanne (85b). L'élément de poussée comprend un deuxième élément de poussée (89) et un troisième élément de poussée (90) différent du deuxième élément de poussée (89). Le deuxième élément de poussée (89) a une caractéristique d'hystérésis dans laquelle une force de rappel (p) dans un processus de chargement et une force de rappel (p) dans un processus de déchargement ont différentes grandeurs au même déplacement (s) dans le processus de chargement et le processus de déchargement, et le troisième élément de poussée (90) a une caractéristique dans laquelle une force de rappel (p) dans un processus de déchargement au même déplacement (s) que le deuxième élément de poussée (89) est supérieure à une force de rappel dans le processus de déchargement du deuxième élément de poussée (89) au même déplacement (s).
PCT/IB2022/054875 2021-05-28 2022-05-25 Dispositif de réduction de pulsations WO2022249078A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN202280038216.XA CN117396381A (zh) 2021-05-28 2022-05-25 脉动降低装置
JP2023523699A JPWO2022249078A1 (fr) 2021-05-28 2022-05-25
DE112022002833.5T DE112022002833T5 (de) 2021-05-28 2022-05-25 Pulsationsreduzierungsvorrichtung

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JP2021-090183 2021-05-28
JP2021090183 2021-05-28

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WO2022249078A1 true WO2022249078A1 (fr) 2022-12-01

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CN (1) CN117396381A (fr)
DE (1) DE112022002833T5 (fr)
WO (1) WO2022249078A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5551767A (en) * 1993-12-07 1996-09-03 Kelsey Hayes Combination high pressure pump/attenuator for vehicle control systems
US5673978A (en) * 1993-12-07 1997-10-07 Kelsey-Hayes Company Pressure attenuators and networks for anti-lock braking systems
DE102009006980A1 (de) * 2008-02-08 2009-08-13 Continental Teves Ag & Co. Ohg Hydraulikaggregat mit verbesserter Pulsationsdämpfung
DE102011007178A1 (de) * 2011-04-12 2012-10-18 Continental Teves Ag & Co. Ohg Ventilbaugruppe
DE102011078250A1 (de) * 2011-06-29 2013-01-03 Continental Teves Ag & Co. Ohg Ventilbaugruppe
DE102012207334A1 (de) * 2012-05-03 2013-11-07 Continental Teves Ag & Co. Ohg Ventilbaugruppe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017061246A (ja) 2015-09-25 2017-03-30 株式会社アドヴィックス パルセーションダンパ及び液圧制動装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5551767A (en) * 1993-12-07 1996-09-03 Kelsey Hayes Combination high pressure pump/attenuator for vehicle control systems
US5673978A (en) * 1993-12-07 1997-10-07 Kelsey-Hayes Company Pressure attenuators and networks for anti-lock braking systems
DE102009006980A1 (de) * 2008-02-08 2009-08-13 Continental Teves Ag & Co. Ohg Hydraulikaggregat mit verbesserter Pulsationsdämpfung
DE102011007178A1 (de) * 2011-04-12 2012-10-18 Continental Teves Ag & Co. Ohg Ventilbaugruppe
DE102011078250A1 (de) * 2011-06-29 2013-01-03 Continental Teves Ag & Co. Ohg Ventilbaugruppe
DE102012207334A1 (de) * 2012-05-03 2013-11-07 Continental Teves Ag & Co. Ohg Ventilbaugruppe

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DE112022002833T5 (de) 2024-03-21
CN117396381A (zh) 2024-01-12

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