WO2021073531A1 - 一种用于制动系统的活塞泵组及其控制方法 - Google Patents

一种用于制动系统的活塞泵组及其控制方法 Download PDF

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Publication number
WO2021073531A1
WO2021073531A1 PCT/CN2020/120884 CN2020120884W WO2021073531A1 WO 2021073531 A1 WO2021073531 A1 WO 2021073531A1 CN 2020120884 W CN2020120884 W CN 2020120884W WO 2021073531 A1 WO2021073531 A1 WO 2021073531A1
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WO
WIPO (PCT)
Prior art keywords
piston
follower
bearing
rotations
inner ring
Prior art date
Application number
PCT/CN2020/120884
Other languages
English (en)
French (fr)
Inventor
姚宇刚
刘国杉
苏东林
刘静
张楠
Original Assignee
比亚迪股份有限公司
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 比亚迪股份有限公司 filed Critical 比亚迪股份有限公司
Priority to JP2022522997A priority Critical patent/JP7420929B2/ja
Priority to EP20876696.4A priority patent/EP4047207A4/en
Priority to US17/769,012 priority patent/US20240101090A1/en
Publication of WO2021073531A1 publication Critical patent/WO2021073531A1/zh

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    • 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
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
    • B60T13/16—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
    • B60T13/20—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs with control of pump driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/14—Adjusting abutments located in the path of reciprocation
    • 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
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • 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
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/745—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive acting on a hydraulic system, e.g. a master cylinder
    • 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
    • B60T17/00—Component parts, details, or accessories of power brake systems not covered by groups B60T8/00, B60T13/00 or B60T15/00, or presenting other characteristic features
    • B60T17/18—Safety devices; Monitoring
    • B60T17/22—Devices for monitoring or checking brake systems; Signal devices
    • B60T17/221—Procedure or apparatus for checking or keeping in a correct functioning condition of brake systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1201—Rotational speed of the axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2087—Arrangements for driving the actuator using planetary gears

Definitions

  • This application belongs to the technical field of hydraulic braking, and in particular relates to a piston pump set used in a braking system and a control method thereof.
  • piston pumps are used for service braking and/or slip adjustment.
  • the piston pump generates brake pressure to deliver the brake fluid from the wheel brakes back to the wheel brakes after the pressure is reduced, so as to increase the wheel brake pressure again, or to transfer the brake fluid in the main brake during slip adjustment. Transport back in the direction of the moving cylinder.
  • the stop position of the piston is difficult to determine. Therefore, when the next braking is required, the braking operation from the current stop position of the piston may not ensure the braking pressure generated by the piston pump. Can achieve the expected effect, thereby affecting driving safety.
  • This application aims to solve at least one of the above technical problems, and provides a piston pump set for a brake system and a control method thereof, which can better achieve the effect of pumping high-pressure fluid and provide stability for the brake system
  • the brake pressure is high, and the working stability is good.
  • a piston pump set for a braking system comprising a piston, a pump body with a working cavity, and a transmission mechanism for driving the piston to move in the working cavity.
  • the transmission mechanism It includes a screw drive assembly, a driven member, and a planetary gear assembly for transmitting power to the screw drive assembly.
  • the driven member is fixedly connected to the piston, and the screw drive assembly is used to drive the
  • the follower moves relative to the working cavity, and a limiting component for restricting the movement of the follower is arranged between the screw drive assembly and the follower.
  • the planetary gear assembly includes a driving wheel, an internal gear ring, a planet cover, and a plurality of planetary gears, and the plurality of planetary gears are respectively meshed and connected with the internal gear ring, and the planetary gears are located on the driving wheel.
  • the inner gear ring, and the driving wheel is respectively meshed and connected with each planetary gear, and the planet cover is matched and connected with the inner gear ring through a positioning structure.
  • the positioning structure includes a groove provided in the circumferential direction of the inner ring of the planetary cover and a protrusion provided in the circumferential direction of the outer ring of the inner gear ring for mating with the groove, or the The positioning structure includes a protrusion provided in the circumferential direction of the inner ring of the planetary cover and a groove provided in the circumferential direction of the outer ring of the inner gear ring for matching with the protrusion.
  • the screw drive assembly includes a bearing outer ring, a bearing inner ring, a bearing retainer and a screw, the bearing outer ring is sleeved outside the bearing inner ring, and the bearing retainer is erected outside the bearing
  • the bearing cage is provided with a plurality of accommodating cavities for accommodating the balls
  • the bearing inner ring is fixedly connected with one end of the screw rod
  • the follower is connected to
  • the screw rod is threadedly connected
  • each of the planetary gears is arranged on the top surface of the inner ring of the bearing through a planetary pin
  • the planet cover is fixedly connected to the outer ring of the bearing.
  • the screw rod and the inner ring of the bearing are integrally formed.
  • the screw rod has a hollow structure, and a through hole is provided along the axial direction of the screw rod.
  • the limiting component is a limiting pin
  • the limiting pin penetrates the inner ring of the bearing to form a collision part
  • the follower is provided with a contact limit for contacting the collision part. Collision structure.
  • the present application also provides a control method for controlling the above-mentioned piston pump set for a brake system.
  • the control method includes the zero-point calibration of the piston and includes the following steps:
  • control method further includes controlling the piston to automatically stop axial movement at a bottom dead center after step S11, where the bottom dead center is a position at a preset distance from the inner wall of the bottom of the pump body.
  • the step of controlling the piston to automatically stop axial movement at bottom dead center includes:
  • step S21 Determine whether the current number of rotations exceeds the preset number of rotations threshold; if the current number of rotations does not exceed the preset number of rotations threshold, perform step S20, and if the current number of rotations is equal to the preset number of rotations Set the lap threshold, then execute step S22,
  • a piston pump set used in a brake system and a control method thereof provided by the present application have the following beneficial effects:
  • a limit component for restricting the movement of the follower is provided between the screw drive assembly and the follower, so that it can avoid the follower when the follower moves upward (the working volume of the working chamber becomes larger) Collision and interference with other parts.
  • the zero-point calibration of the piston can also be achieved through the limit component. That is, when the follower is blocked by the limit component and stops moving, the working volume of the working chamber is the largest, and the piston is at the zero point position. , To ensure that the liquid discharged from the piston pump set has sufficient pressure to provide a stable brake pressure for the brake system;
  • the inner ring of the bearing and the screw rod adopt an integral structure with high structural strength, and there will be no deformation of the inner ring of the bearing when the inner ring of the bearing and the screw rod are interference press-fitted, so as to ensure the stability of the overall structure of the piston pump set ;
  • the screw rod adopts a hollow structure design, which can avoid negative pressure between the piston and the screw rod when the piston moves away from the limiting part (moving downwards), or it can prevent the piston from moving close to the limiting part (moving upward). Positive pressure is generated between the piston and the screw rod, which causes the resistance to increase when the piston moves, which in turn leads to an increase in energy consumption when driving the piston to move;
  • Fig. 1 is a schematic structural diagram of a piston pump set for a braking system provided by an embodiment of the present application
  • FIG. 2 is an exploded schematic diagram of a transmission mechanism in a piston pump set for a brake system provided by an embodiment of the present application;
  • Fig. 3 is an exploded schematic diagram of a screw drive assembly in a piston pump set for a brake system provided by an embodiment of the present application;
  • Figure 4 is a schematic structural diagram of a screw drive assembly in a piston pump set for a brake system provided by an embodiment of the present application;
  • Fig. 5 is a schematic structural diagram of a follower in a piston pump set for a brake system provided by an embodiment of the present application.
  • an embodiment of the application provides a piston pump set for a braking system, including a piston 2, a transmission mechanism 3, and a pump body 1 with a working cavity.
  • the transmission mechanism 3 is used to drive the piston. 2 Perform reciprocating movement in the working chamber to change the working volume of the working chamber, suck in liquid or discharge liquid with pressure, the transmission mechanism 3 includes a screw drive assembly 32, a follower 33 and a planetary gear assembly 31.
  • the planetary gear assembly 31 is used In order to transmit the power of the driving element to the screw drive assembly 32, the screw drive assembly 32 drives the follower 33 to move relative to the working cavity in the pump body 1, and the follower 33 and the piston 2 are fixedly connected, so that The piston 2 can move with the follower 33 (that is, the piston 2 and the follower 33 are as a whole), by providing a limit member 34 between the screw drive assembly 32 and the follower 33 for restricting the movement of the follower 33 In this way, it is possible to prevent the follower 33 (piston 2) from colliding and interfering with other parts when the follower 33 (piston 2) moves upward (the working volume of the working chamber becomes larger), and at the same time, it can also pass through the limit part 34 To achieve the zero-point calibration of the piston 2, when the follower 33 is blocked by the limiting member 34 and stops moving, the working volume of the working chamber is maximized (that is, the piston 2 is at the zero-point position at this time) to ensure that the liquid discharged by the piston pump set has
  • the driving element drives the planetary gear assembly 31 to rotate, which in turn drives the screw drive assembly 32 to rotate, so that the follower 33 (piston 2) moves closer to the limit member 34 or away from the limit as the screw drive assembly 32 rotates.
  • the movement of the component 34 and the movement of the piston 2 change the working volume of the working chamber.
  • the working chamber of the pump body 1 can be connected with a suction valve port and a discharge valve port.
  • the change in the volume of the working chamber produces a pressure difference, so that the liquid (hydraulic oil) is sucked into the working chamber through the suction valve port, or the liquid (hydraulic oil) ) Discharge from the working chamber through the discharge valve port.
  • the piston pump set for the braking system also includes a driving element for providing power.
  • the driving element is a motor
  • the motor is connected with a motor controller and a revolution sensor.
  • the motor controller is used to control the stop and operation of the motor.
  • the operation of the motor includes clockwise rotation and counterclockwise rotation of the motor, and the revolution sensor is used To get the number of rotations of the output shaft.
  • the follower 33 and the piston 2 can be connected and fixed by a threaded structure, that is, the follower 33 and the piston 2 are fixed by a threaded connection, wherein the threaded structure includes a peripheral outer peripheral provided on the outer side of the follower 33
  • the threaded structure includes a peripheral outer peripheral provided on the outer side of the follower 33
  • the thread 331 and the internal thread provided in the inner circumferential direction of the piston 2 (ie the inner wall of the piston 2), the external thread 331 of the follower 33 and the internal thread of the piston 2 cooperate to realize the connection and fixation of the follower 33 and the piston 2.
  • the follower 33 and the piston 2 of the present application are fixed by a threaded connection, on the one hand, it can ensure that the follower 33, the piston 2 and the working cavity have good coaxiality, and the air tightness of the working cavity can also be ensured.
  • the planetary gear assembly 31 includes a driving gear (not shown in the figure), an internal gear ring 312, a planet cover 311, and a plurality of planetary gears 313 with the same structure.
  • Each planetary gear 313 is separately In mesh connection with the inner gear ring 312, the planetary gears 313 are located between the driving gear and the inner gear ring 312, and each planet gear 313 is also meshed and connected with the driving gear.
  • the driving gear is used as a sun gear and is connected to the motor.
  • the output shaft is connected to transmit the power of the motor to the planetary gear 313, which drives the planetary gear 313 to rotate.
  • the planetary cover 311 is sleeved on the inner gear ring 312, and is connected with the inner gear ring 312 through a positioning structure to perform the operation on the inner gear ring 312. fixed.
  • the planetary gear assembly 31 has the advantages of small size, large carrying capacity, and stable operation.
  • the planetary gears 313, the driving wheel and the inner gear ring 312 can all be helical tooth structures, with Good meshing, stable transmission, low noise, and large overlap of helical gears, which reduces the load of each pair of gears and improves the load-bearing capacity of the gears. It is understandable that the driving gear, the planetary gear 313 and the inner gear ring 312 may also adopt a straight tooth structure.
  • the positioning structure includes a groove 3111 provided in the circumferential direction of the inner ring of the planetary cover 311 and a protrusion 3121 provided in the outer circumference of the inner ring 312 for mating with the groove 3111, or ,
  • the positioning structure includes a protrusion provided in the circumferential direction of the inner ring of the planetary cover 311 and a groove provided in the outer circumference of the inner ring 312 for matching with the protrusion.
  • the protrusion 3121 and the groove 3111 adopt an interference fit, and the positioning connection is performed through the protrusion 3121 and the groove 3111, which facilitates the assembly and connection of the planetary cover 311 and the inner gear ring 312.
  • protrusions 3121 there may be a plurality of protrusions 3121.
  • the protrusions 3121 are distributed on the inner gear ring 312 in a circular array. Viewed along the axial direction of the inner gear ring 312, the cross section of the protrusions 3121 may be rectangular, triangular, or rectangular. Trapezoidal, arc-shaped and other structures, the number and cross-section of the grooves 3111 correspond to the protrusions 3121.
  • the screw drive assembly 32 includes a bearing outer ring 321, a bearing inner ring 322, a bearing retainer 323 and a screw 324, and the bearing outer ring 321 is sleeved outside the bearing inner ring 322
  • the bearing cage 323 is arranged between the bearing outer ring 321 and the bearing inner ring 322.
  • the bearing cage 323 is provided with a plurality of accommodating cavities 3231 for accommodating the balls 325, and the bearing inner ring 322 is connected to the bearing outer ring through the balls 325 321 rolling connection, the bearing inner ring 322 is fixedly connected with one end of the screw rod 324, each planetary gear 313 is respectively arranged on the top surface of the bearing inner ring 322 through a planetary pin 3131, and the planetary gear 313 can be opposed to the bearing inner ring around the planetary pin 3131
  • the ring 322 rotates, while the planetary gear 313 can also rotate relative to the inner gear ring 312, which in turn drives the bearing inner ring 322 (screw 324) to rotate.
  • the follower 33 and the screw 324 are connected in a threaded manner, so that the follower 33 can As the screw 324 rotates and moves axially relative to the screw 324 (close to or away from the limiting member 34), the planetary cover 311 and the bearing outer ring 321 are connected and fixed by welding, and the inner gear ring 312 is clamped by the bearing outer ring 321 Inside the planetary cover 311. It is understandable that the planet cover 311 can also be connected and fixed to the bearing outer ring 321 by screws.
  • the screw rod 324 and the bearing inner ring 322 are integrally formed, and the cross section of the screw rod 324 and the bearing inner ring 322 may be T-shaped, and the center of the bearing inner ring 322 and the wire
  • the central axis of the rod 324 coincides and adopts an integrated structure design with high structural strength. It can also prevent the bearing inner ring 322 from being easily deformed when the screw 324 and the bearing inner ring 322 are press-fitted, so that the bearing inner ring 322 can roll smoothly. , To ensure the reliability of the overall operation of the piston pump set.
  • the screw rod 324 has a hollow structure, and a through hole 3241 is provided along the axial direction of the screw rod 324.
  • the through hole 3241 is coaxially arranged with the screw rod 324, that is, the central axis of the through hole 3241 coincides with the central axis of the screw rod 324, which ensures that the center of mass of the screw rod 324 is on the central axis during rotation.
  • the through hole 3241 allows the cavity formed between the piston 2 and the screw rod 324 to communicate with the outside world, so that when the piston 2 moves downward (the axial distance between the piston 2 and the screw rod 324 increases), the void can be avoided
  • the larger cavity volume produces negative pressure, or when the piston 2 moves upwards (the axial distance between the piston 2 and the screw rod 324 becomes smaller), the smaller cavity volume is compressed and the positive pressure is generated to ensure the piston 2
  • the movement will not be affected by the change of the cavity volume, avoiding the movement of the piston 2 from being affected by positive pressure or negative pressure, and effectively reducing the energy consumption required to drive the piston 2 to move;
  • the weight reduction of the screw rod 324 reduces the inertia, which can improve the response speed of the screw rod transmission assembly 32 during transmission.
  • the hole diameter of the through hole 3241 is 1/5 to 1/2 of the diameter of the screw rod 324.
  • the outer bearing ring 321 is connected to the pump body 1 through a connecting piece 35, and the planetary gear assembly 31 and the screw drive assembly 32 are installed and fixed to the pump body 1.
  • the bearing outer ring 321 is integrally press-fitted with the pump body 1 through the connecting piece 35.
  • the planet cover 311, the inner gear ring 312, and the bearing outer ring 321 are all fixed and immobile.
  • the limiting member 34 is a limiting pin, which penetrates through the bearing inner ring 322 and forms a collision portion 342 on the side facing the follower 33, and the follower 33 is provided There is a collision structure for contacting and limiting the collision portion 342.
  • the follower 33 moves toward the bearing inner ring 322 (the direction of the planetary gear assembly 31)
  • the collision structure provided on the follower 33 and the collision portion 342 on the bearing inner ring 322 gradually approach, and finally contact to generate a collision signal
  • the motor After receiving the collision signal, it immediately stops rotating, and at the same time the screw 324 stops rotating, the piston 2 then stops moving and stops at the current position.
  • the movement of the follower 33 is restricted by setting the limit member 34 to avoid the follower when the piston 2 returns.
  • the piece 33 collides and interferes with the inner ring 322 of the bearing.
  • the zero-point calibration of the piston 2 can also be performed by the limit component 34 to ensure that the piston 2 is at the zero-point position every time it works (definition: the zero-point position refers to the position where the piston 2 is when the working chamber is at the maximum working volume. position).
  • the limiting member 34 is threadedly connected to the bearing inner ring 322, and the length of the collision portion 342 can be controlled by adjusting the length of the limiting member 34 passing through the bearing inner ring 322 to limit the movement stroke of the piston 2 to the limiting member 34.
  • the maximum volume of the working chamber is adjusted, and it is also easy to replace when the limiting component 34 is worn out due to collision.
  • the follower 33 may be a nut
  • the external thread 331 is provided at the lower end of the outer circumference of the nut
  • the collision structure may be a boss 341 integrally formed on the top of the nut.
  • the boss 341 and the collision After the portion 342 contacts, the nut (piston 2) immediately stops moving, and the position of the piston 2 at this time is the zero position.
  • the total length of the nut is 40.3 mm (including the boss 341 of 3 mm), and the length of the external thread 331 is 14 mm.
  • the collision structure is mainly used for positioning the collision portion 342, so the collision structure may also be a countersink provided on the top surface of the nut.
  • This application also provides a control method for controlling the above-mentioned piston pump set for the brake system.
  • the control method includes the zero point calibration of the piston 2, that is, the piston 2 needs to be moved to the zero point position before work to ensure that the piston
  • the initial discharge pressure of the pump set is the expected value, and the braking effect is stable.
  • control method further includes controlling the piston 2 to automatically stop axial movement at the bottom dead center after step S11, and the bottom dead center is a position at a preset distance from the inner wall of the bottom of the pump body 1, specifically referring to when the piston 2 and the bottom of the pump body 1 The distance between the inner walls (the bottom of the working chamber) is equal to the position of the piston 2 at the preset distance.
  • the step of controlling the piston 2 to automatically stop axial movement at the bottom dead center includes:
  • the motor is controlled to rotate in the second direction, driving the planetary gear assembly 31 to rotate in the second direction, and then driving the screw drive assembly 32 to rotate in the second direction, and the follower 33 follows the screw
  • the rotation of the transmission assembly 32 moves away from the limiting member 34, the working volume of the working chamber gradually decreases with the movement of the piston 2, and the working chamber is compressed to generate pressure to discharge the liquid in the working chamber from the discharge valve port, and the discharged
  • the liquid has a certain pressure, and the current number of rotations of the motor can be obtained in real time (the number of rotations of the motor output shaft can be obtained by the motor controller through the rotation number sensor) or the current number of rotations of the screw drive assembly 32 (that is, the screw 324
  • the number of rotations of the screw rod 324 can be obtained indirectly by obtaining the number of rotations of the motor);
  • step S21 Judge whether the current number of rotations exceeds the preset number of revolutions threshold to determine whether the piston 2 moves to the bottom dead center, where the preset number of revolutions threshold refers to the motor output shaft when the piston 2 moves from the zero position to the bottom dead center
  • step S20 if the current number of rotations of the motor or the current number of rotations of the screw drive assembly 32 does not exceed the preset number of rotations threshold, step S20 is executed; if the current number of rotations of the motor Or the current number of rotations of the screw drive assembly 32 is equal to the preset number of rotations threshold, then step S22 is executed.
  • the current number of rotations of the motor or the current number of rotations of the screw drive assembly 32 is equal to the preset number of rotations threshold, the motor controller will generate a stop operation instruction, and execute the stop operation instruction, the motor stops rotating in the second direction, The planetary gear assembly 31 and the screw drive assembly 32 stop rotating in the second direction, thereby controlling the follower 33 (piston 2) to stop moving, and the piston 2 stops at the bottom dead center, that is, once the piston 2 reaches the bottom dead center, it automatically stops moving. Avoid collision between the piston 2 and the bottom surface of the working chamber.
  • the motor controller If the current number of rotations of the motor or the current number of rotations of the screw drive assembly 32 does not exceed the preset number of rotations threshold, the motor controller generates a continuous operation instruction and executes the continuous operation instruction to control the motor to continue to rotate in the second direction , Until the current number of rotations of the motor or the current number of rotations of the screw drive assembly 32 is equal to the preset number of turns threshold (the piston 2 moves to the bottom dead center), the motor is controlled to stop rotating in the second direction.
  • the first direction and the second direction are determined according to the thread rotation direction of the screw rod 324.
  • the first direction is counterclockwise, and the follower 33 is opposite to the screw thread.
  • the rod 324 moves upward, the second direction is clockwise, and the follower 33 moves downward relative to the screw rod 324; if the thread of the screw 324 is left-handed, the first direction is clockwise, and the follower 33 is relative to the screw rod. 324 moves upward, the second direction is counterclockwise, and the follower 33 moves downward relative to the screw rod 324.
  • the operation process of the piston pump set used in the brake system of the present application is as follows: firstly calibrate the piston 2 at zero point, and then control the piston 2 to move down from the zero point position to the bottom dead center, and discharge the liquid in the working chamber for braking. Finally, control the return stroke of the piston 2 and move upward from the bottom dead center to suck liquid into the working chamber.
  • the work of the piston pump set can be a continuous process, that is, after the piston 2 is calibrated at its zero point, the piston 2 performs continuous reciprocating motion between the zero point and the bottom dead center.
  • the piston pump set used in the brake system and the control method thereof provided by the embodiments of the present application have the following beneficial effects:
  • a limit component 34 for restricting the movement of the follower 33 is provided between the screw drive assembly 32 and the follower 33, so that the follower 33 can be prevented from moving upwards (the working volume of the working chamber becomes larger) )
  • the zero point calibration of the piston 2 can also be achieved through the limit component 34, that is, when the follower 33 is blocked by the limit component 34 and stops moving, the working cavity
  • the working volume is the largest, and the piston 2 is at the zero position at this time to ensure that the liquid discharged from the piston pump set has sufficient pressure to provide a stable braking pressure for the braking system;
  • the follower 33 and the piston 2 are fixed by threaded connection, which can avoid the expansion and deformation of the piston 2 due to interference press fitting, and ensure that the piston 2 and the working chamber have good coaxiality.
  • the working cavity is closely matched, and the air tightness of the changing process of the working cavity volume is good;
  • the follower 33 and the piston 2 are connected in a threaded manner.
  • the piston 2 and the follower 33 are in surface contact, which increases the force area, which can avoid stress concentration and improve the service life of the piston 2;
  • the bearing inner ring 322 and the screw rod 324 adopt an integral structure with high structural strength, and there will be no deformation of the bearing inner ring 322 during the interference press fitting of the bearing inner ring 322 and the screw rod 324, thereby ensuring the piston pump set The stability of the overall structure.
  • the screw rod 324 adopts a hollow structure design, which can avoid negative pressure between the piston 2 and the screw rod 324 when the piston 2 moves away from the limiting component 34 (moving downwards), or it can prevent the piston 2 from approaching the limiting component 34 During movement (upward movement), a positive pressure is generated between the piston 2 and the screw rod 324, which increases the resistance when the piston 2 moves, which in turn leads to an increase in energy consumption when driving the piston 2 to move;
  • first and second are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the features defined with “first” and “second” may explicitly or implicitly include one or more of these features. In the description of the present application, “multiple” means two or more, unless it is specifically defined otherwise.
  • the terms “installed”, “connected”, “connected”, “fixed” and other terms should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection , Or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two components or the interaction relationship between two components.
  • installed can be a fixed connection or a detachable connection , Or integrated; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication of two components or the interaction relationship between two components.
  • the first feature “on” or “under” the second feature may be in direct contact with the first and second features, or the first and second features may be indirectly through an intermediary. contact.
  • the "above”, “above” and “above” of the first feature on the second feature may mean that the first feature is directly above or obliquely above the second feature, or it simply means that the level of the first feature is higher than the second feature.
  • the “below”, “below” and “below” of the second feature of the first feature may be that the first feature is directly below or obliquely below the second feature, or it simply means that the level of the first feature is smaller than the second feature.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Transmission Devices (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

一种用于制动系统的活塞泵组及其控制方法，活塞泵组包括活塞(2)、具有工作腔的泵体(1)和用于带动活塞(2)在工作腔内运动的传动机构(3)，传动机构(3)包括丝杆传动组件(32)、从动件(33)和用于将动力传递给丝杆传动组件(32)的行星齿轮组件(31)，从动件(33)与活塞(2)固定连接，丝杆传动组件(32)用于带动从动件(33)相对工作腔进行运动，丝杆传动组件(32)与从动件(33)之间设置有用于限制从动件(33)运动的限位部件(34)。上述活塞泵组通过限位部件(34)实现活塞的零点校准。

Description

一种用于制动系统的活塞泵组及其控制方法
相关申请的交叉引用
本申请要求比亚迪股份有限公司于2019年10月16日提交的、申请名称为“一种用于制动系统的活塞泵组及其控制方法”的、中国专利申请号“201910980645.9”的优先权。
技术领域
本申请属于液压制动技术领域，尤其涉及一种用于制动系统的活塞泵组及其控制方法。
背景技术
在液压车辆制动系统中，活塞泵用于行车制动，和/或滑动调节。活塞泵产生制动压力用于将出自车轮制动器的输送制动液在压力降低之后输送回所述车轮制动器，以便再次提高车轮制动压力，或者用于在滑动调节期间将制动液在主制动缸的方向上输送回。然而，当活塞泵的上一次运动完成后，活塞停止的位置难以确定，因此，当需要进行下一次制动时，从活塞当前停止位置进行制动操作，可能无法确保活塞泵产生的制动压力能达到预期的效果，从而影响行车安全。
发明内容
本申请旨在至少解决上述技术问题之一，提供了一种用于制动系统的活塞泵组及其控制方法，其可更好的实现的泵出高压液的效果，为制动系统提供稳定的制动压力，工作稳定性好。
本申请的技术方案是：一种用于制动系统的活塞泵组，包括活塞、具有工作腔的泵体和用于带动所述活塞在所述工作腔内运动的传动机构，所述传动机构包括丝杆传动组件、从动件和用于将动力传递给所述丝杆传动组件的行星齿轮组件，所述从动件与所述活塞固定连接，所述丝杆传动组件用于带动所述从动件相对所述工作腔运动，所述丝杆传动组件与所述从动件之间设置有用于限制所述从动件运动的限位部件。
可选地，所述行星齿轮组件包括主动轮、内齿环、行星盖和多个行星齿轮，多个所述行星齿轮分别与所述内齿环啮合连接，所述行星齿轮位于所述主动轮与所述内齿环之间，且所述主动轮分别与每一个行星齿轮啮合连接，所述行星盖通过定位结构与所述内齿环配合连接。
可选地，所述定位结构包括设于所述行星盖内圈周向的凹槽和设于所述内齿环外圈周向用于与所述凹槽配合的凸起，或者，所述定位结构包括设于所述行星盖内圈周向的凸起和 设于所述内齿环外圈周向用于与所述凸起配合的凹槽。
可选地，所述丝杆传动组件包括轴承外圈、轴承内圈、轴承保持架和丝杆，所述轴承外圈套设于所述轴承内圈外，所述轴承保持架设于所述轴承外圈与所述轴承内圈之间，所述轴承保持架设置有多个用于容置滚珠的容置腔，所述轴承内圈与所述丝杆的一端固定连接，所述从动件与所述丝杆螺纹连接，每一个所述行星齿轮通过行星销设于所述轴承内圈的顶面上，且所述行星盖与所述轴承外圈固定连接。
可选地，所述丝杆与所述轴承内圈为一体成型结构。
可选地，所述丝杆为中空结构，沿所述丝杆的轴向方向设置有一通孔。
可选地，所述限位部件为限位销，所述限位销贯穿于所述轴承内圈形成有一碰撞部，所述从动件上设置有用于与所述碰撞部进行接触限位的碰撞结构。
本申请还提供了一种控制方法，用于控制上述的用于制动系统的活塞泵组,所述控制方法包括活塞的零点校准，具有包括以下步骤：
S10、控制电机沿第一方向旋转，带动行星齿轮组件沿第一方向旋转，进而带动丝杆传动组件沿第一方向旋转，从动件随所述丝杆传动组件的旋转靠近限位部件运动；
S11、当所述从动件的碰撞结构接触到所述限位部件时，控制所述电机停止运转，以致所述行星齿轮组件和所述丝杆传动组件停止旋转，从而使所述从动件和所述活塞停止轴向运动，此时活塞所处位置为零点位置。
可选地，所述控制方法还包括在步骤S11后控制所述活塞在下止点自动停止轴向运动，所述下止点为距离泵体底部内壁预设距离的位置。
可选地，控制所述活塞在下止点自动停止轴向运动的步骤，包括：
S20、控制所述电机沿第二方向旋转，带动所述行星齿轮组件沿第二方向旋转，从而带动所述丝杆传动组件沿第二方向旋转，所述从动件随所述丝杆传动组件的旋转远离所述限位部件运动，并实时获取所述电机的当前旋转圈数或所述丝杆传动组件的当前旋转圈数；
S21、判断所述当前旋转圈数是否超过预设圈数阈值；若所述当前旋转圈数未超过所述预设圈数阈值，则执行步骤S20，若所述当前旋转圈数等于所述预设圈数阈值，则执行步骤S22，
S22、控制所述电机停止沿第二方向旋转，以致所述行星齿轮组件和所述丝杆传动组件停止沿第二方向旋转，从而使所述从动件和所述活塞停止轴向运动，此时所述活塞所处位置为所述下止点。
本申请所提供的一种用于制动系统的活塞泵组及其控制方法，与现有技术相比，具有以下有益效果：
1、通过在丝杆传动组件与从动件之间设置有用于限制从动件运动的限位部件，这样， 可以避免从动件在向上运动(工作腔的工作容积变大)时从动件与别的部件发生碰撞干涉，同时，还可以通过限位部件来实现活塞的零点校准，即当从动件被限位部件阻挡停止运动后，工作腔的工作容积最大，此时活塞处于零点位置，以保证活塞泵组排出的液体具有足够的压力，来为制动系统提供稳定的制动压力；
2、轴承内圈与丝杆采用一体成型的结构，结构强度高，不会出现轴承内圈与丝杆过盈压装时轴承内圈发生变形的现象，从而保证活塞泵组整体结构的稳定性；
3、丝杆采用中空结构设计，可避免活塞远离限位部件运动(向下运动)时，活塞与丝杆之间产生负压，或者，可避免活塞靠近限位部件运动(向上运动)时，活塞与丝杆之间产生正压，从而致使活塞运动时阻力增加，进而导致驱动活塞运动时所需能耗增加；
4、通过判断当前旋转圈数与预设圈数阈值的关系，来确认活塞与工作腔底面之间的距离，即控制活塞在下止点处自动停止运动，以避免活塞远离限位部件运动(向下运动)时，活塞与工作腔的底面发生碰撞，从而进一步延长了活塞的使用寿命。
本申请的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本申请的实践了解到。
附图说明
本申请的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是本申请实施例提供的用于制动系统的活塞泵组的结构示意图；
图2是本申请实施例提供的用于制动系统的活塞泵组中传动机构的爆炸示意图；
图3是本申请实施例提供的用于制动系统的活塞泵组中丝杆传动组件的爆炸示意图；
图4是本申请实施例提供的用于制动系统的活塞泵组中丝杆传动组件的结构示意图；
图5是本申请实施例提供的用于制动系统的活塞泵组中从动件的结构示意图。
具体实施方式
下面详细描述本申请的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，旨在用于解释本申请，而不能理解为对本申请的限制。
如图1至图5所示，本申请实施例提供的一种用于制动系统的活塞泵组，包括活塞2、传动机构3和具有工作腔的泵体1，传动机构3用于带动活塞2在工作腔内进行往复运动来改变工作腔的工作容积，吸入液体或排出具有压力的液体，传动机构3包括丝杆传动组件32、从动件33和行星齿轮组件31，行星齿轮组件31用于将驱动元件的动力传递给丝杆传 动组件32，使得丝杆传动组件32带动从动件33在泵体1内相对工作腔内运动，从动件33与活塞2采用固定连接的方式，使得活塞2能随从动件33运动(即活塞2与从动件33作为一个整体)，通过在丝杆传动组件32与从动件33之间设置有用于限制从动件33运动的限位部件34，这样，可以避免从动件33(活塞2)在向上运动(工作腔的工作容积变大)时从动件33(活塞2)与其他部件发生碰撞干涉，同时，还可以通过限位部件34来实现活塞2的零点校准，当从动件33被限位部件34阻挡停止运动后，工作腔的工作容积最大(即此时活塞2处于零点位置)，保证活塞泵组排出的液体具有足够的压力，为制动系统系统提供稳定的制动压力。工作时，驱动元件运转带动行星齿轮组件31旋转，进而带动丝杆传动组件32旋转，以致从动件33(活塞2)随着丝杆传动组件32的旋转做靠近限位部件34或远离限位部件34的运动，活塞2的运动改变工作腔的工作容积。
具体地，泵体1的工作腔可连接有吸入阀口和排出阀口，工作腔容积的变化产生压力差，使得液体(液压油)通过吸入阀口吸入工作腔内，或者，液体(液压油)通过排出阀口从工作腔内排出。
具体地，该用于制动系统的活塞泵组还包括用于提供动力的驱动元件。本实施例中，驱动元件为电机，电机连接有电机控制器和转数传感器，电机控制器用来控制电机的停止和运转，电机的运转包括电机的顺时针旋转和逆时针旋转，转数传感器用来获取输出轴的旋转圈数。
可选地，从动件33与活塞2可通过螺纹结构连接固定，即从动件33与活塞2采用螺纹连接的方式进行固定，其中，螺纹结构包括设于从动件33外侧周向的外螺纹331和设于活塞2内侧周向(即活塞2的内壁)的内螺纹，从动件33的外螺纹331与活塞2的内螺纹配合，来实现从动件33与活塞2的连接固定。
当活塞泵组应用于车辆制动领域时，必须保证每次制动的效果是可预期的，如果活塞发生变形，首先，会导致活塞在泵体工作腔内的运动不顺畅，可能会使活塞泵组的制动不能及时跟上驾驶员的动作，即制动出现迟缓现象；其次，活塞的变形与工作腔存在同轴度差的问题，导致工作时活塞与工作腔壁容易摩擦受损，从而影响活塞的使用寿命；最后，活塞变形会导致活塞与工作腔壁之间具有一定的缝隙，使工作腔内的气密性差，工作腔容积变化时不能保证将液体吸入工作腔或将液体排出工作腔的效果，从而影响制动的可靠性。这些问题都会成为影响行车过程中的制动可靠性，危及驾驶安全。
而本申请的从动件33与活塞2通过采用螺纹连接的固定方式，一方面可以保证从动件33、活塞2与工作腔具有良好的同轴度，还可以保证工作腔的气密性，为制动系统系统提供稳定的制动压力，保证行车安全；另一方面，从动件33与活塞2采用螺纹连接的方式，增大两者受力面积，从而可以很好的避免应力集中的问题，从而提高活塞泵组的使用寿命。
可选地，如图2所示，行星齿轮组件31包括一个主动轮(图中未示出)、内齿环312、行星盖311和多个结构相同的行星齿轮313，每一个行星齿轮313分别与内齿环312啮合连接，行星齿轮313位于主动轮与内齿环312之间，且每一个行星齿轮313还分别与主动轮啮合连接，本实施例中，主动轮作为太阳轮，与电机的输出轴连接，来将电机的动力传递给行星齿轮313，驱动行星齿轮313旋转，行星盖311套在内齿环312上，并通过定位结构与内齿环312配合连接，对内齿环312进行固定。其中，行星齿轮组件31具有体积小、承载能力大、工作平稳的优点。
本实施例中，如图2所示，行星齿轮313具有三个，关于主动轮的中心以圆周阵列形式分布，其中，行星齿轮313、主动轮和内齿环312均可为斜齿结构，具有啮合性好，传动平稳，噪声小的特点，且斜齿轮的重合度大，降低了每对齿轮的载荷，提高了齿轮的承载能力。可以理解地，主动轮、行星齿轮313和内齿环312也可以采用直齿结构。
可选地，如图2所示，定位结构包括设于行星盖311内圈周向的凹槽3111和设于内齿环312外圈周向用于与凹槽3111配合的凸起3121，或者，定位结构包括设于行星盖311内圈周向的凸起和设于内齿环312外圈周向用于与凸起配合的凹槽。其中，凸起3121和凹槽3111采用过盈配合，通过凸起3121和凹槽3111进行定位连接，易于实现行星盖311和内齿环312的装配连接。
具体地，凸起3121可设置有多个，凸起3121以圆周阵列的形式分布于内齿环312上，沿内齿环312的轴向方向看，凸起3121的截面可呈矩形、三角形、梯形、弧形等结构，凹槽3111的数量和截面与凸起3121相对应。
可选地，如图3和图4所示，丝杆传动组件32包括轴承外圈321、轴承内圈322、轴承保持架323和丝杆324，轴承外圈321套设于轴承内圈322外，轴承保持架323设于轴承外圈321与轴承内圈322之间，轴承保持架323设置有多个用于容置滚珠325的容置腔3231，轴承内圈322通过滚珠325与轴承外圈321滚动连接，轴承内圈322与丝杆324的一端固定连接，每一个行星齿轮313分别通过行星销3131设于轴承内圈322的顶面上，行星齿轮313可绕行星销3131相对轴承内圈322旋转，同时行星齿轮313还可相对内齿环312转动，进而带动轴承内圈322(丝杆324)旋转，从动件33与丝杆324采用螺纹连接的方式，使得从动件33能随着丝杆324的旋转相对丝杆324轴向运动(靠近或远离限位部件34)，行星盖311与轴承外圈321通过焊接的方式连接固定，内齿环312被轴承外圈321卡于行星盖311内。可以理解地，行星盖311也可以通过螺钉与轴承外圈321进行连接固定。
可选地，如图3和图4所示，丝杆324与轴承内圈322为一体成型结构，丝杆324和轴承内圈322的截面可呈T字型，轴承内圈322的圆心与丝杆324的中轴线重合，采用一体成型结构的设计，结构强度高，还可避免丝杆324与轴承内圈322过盈压装时轴承内圈322 易于出现变形现象，使轴承内圈322滚动顺畅，保证活塞泵组的整体运转的可靠性。
可选地，如图4所示，丝杆324为中空结构，沿丝杆324的轴向方向设置有一通孔3241。其中，通孔3241与丝杆324同轴设置，即通孔3241的中心轴与丝杆324的中心轴重合，保证转动时丝杆324质心在中轴线上。将丝杆324设计成中空结构：
1、通孔3241使活塞2与丝杆324之间形成的空腔连通外界，这样，当活塞2向下运动时(活塞2与丝杆324之间的轴向距离增大)，可避免空腔体积变大产生负压，或者，当活塞2向上运动时(活塞2与丝杆324之间的轴向距离变小)，可避免空腔体积变小被压缩产生正压，来确保活塞2运动时不会受到空腔体积变化的影响，避免活塞2的运动受正压或负压影响，有效降低驱动活塞2运动时所需的能耗；
2、可以有效降低了丝杆324的材料成本；
3、丝杆324的质量减轻使惯性减小，传动时，能提高丝杆传动组件32的响应速度。
具体地，通孔3241的孔径为丝杆324直径的1/5至1/2。
可选地，如图1所示，轴承外圈321通过连接件35与泵体1连接，将行星齿轮组件31和丝杆传动组件32安装固定到泵体1上。本实施例中，轴承外圈321通过连接件35与泵体1过盈压装为一体，活塞泵组工作时，行星盖311、内齿环312、轴承外圈321均固定不动，对行星齿轮313、轴承内圈322和丝杆进行支撑。
可选地，如图4所示，限位部件34为限位销，限位销贯穿于轴承内圈322并在朝向从动件33的一侧形成有一碰撞部342，从动件33上设置有用于与碰撞部342发生接触限位的碰撞结构。当从动件33朝向轴承内圈322(行星齿轮组件31方向)运动时，设于从动件33上的碰撞结构与轴承内圈322上的碰撞部342逐渐靠近，最后接触产生碰撞信号，电机接收到该碰撞信号后立即停止旋转，同时丝杆324停止旋转，活塞2进而停止运动，并停止在当前位置，通过设置限位部件34来限制从动件33运动，避免活塞2回程时从动件33与轴承内圈322发生碰撞干涉。实际应用中，还可通过限位部件34来进行活塞2的零点校准，确保活塞2每次工作时都是处于零点位置(定义：零点位置是指工作腔处于最大工作容积时活塞2所处的位置)。
具体地，限位部件34螺纹连接于轴承内圈322，可通过调节限位部件34穿过轴承内圈322的长度来控制碰撞部342的长度，限制活塞2向限位部件34的运动行程，调节工作腔的最大容积，且当限位部件34碰撞磨损后，也便于更换。
本实施例中，如图5所示，从动件33可为螺母，外螺纹331设于螺母外侧周向的下端，碰撞结构可为一体成型于螺母顶端的凸台341，凸台341与碰撞部342接触后，螺母(活塞2)立即停止运动，此时活塞2的位置为零点位置。其中，螺母的总长度为40.3mm(包含有3mm的凸台341),外螺纹331的长度为14mm。可以理解地，碰撞结构主要用于对碰撞部342 进行定位，故，碰撞结构也可为设于螺母顶面的沉槽。
本申请还提供了一种控制方法，用于控制上述的用于制动系统的活塞泵组,控制方法包括活塞2的零点校准，即工作前需要先将活塞2移动至零点位置，以确保活塞泵组最开始排出液体的压力为预期的值，制动效果稳定。为了便于理解，本实施例将结合电机进行说明，具体步骤如下：
S10、控制电机启动沿第一方向旋转，带动行星齿轮组件31沿第一方向旋转，进而带动丝杆传动组件32沿第一方向旋转，从动件33随丝杆传动组件32的旋转靠近限位部件34运动，活塞2随从动件33靠近行限位部件34运动；
S11、当从动件33的碰撞结构接触到限位部件34时，产生碰撞信号，电机的转数传感器接收该碰撞信号后反馈给电机控制器，电机控制器生成停止运转指令，并执行该停止运转指令，电机停止沿第一方向旋转，以致行星齿轮组件31和丝杆传动组件32停止旋转，从而使从动件33和活塞2停止轴向运动，此时活塞2所处位置即为零点位置。通过限位的方式还可以实现活塞2在零点位置自动停止，避免活塞2与其他部件发生碰撞。
可选地，控制方法还包括在步骤S11后控制活塞2在下止点自动停止轴向运动，下止点为距离泵体1底部内壁预设距离的位置，具体指当活塞2与泵体1底部内壁(工作腔底部)之间的距离等于预设距离时活塞2所处的位置。
可选地，控制活塞2在下止点自动停止轴向运动的步骤，包括：
S20、当活塞2在零点位置停止后，控制电机沿第二方向旋转，带动行星齿轮组件31沿第二方向旋转，进而带动丝杆传动组件32沿第二方向旋转，从动件33随丝杆传动组件32的旋转远离限位部件34运动，工作腔的工作容积随着活塞2的运动逐渐变小，工作腔被压缩产生压力将工作腔内的液体从排出阀口向外排出，且排出的液体具有一定的压力，并实时获取电机的当前旋转圈数(可电机控制器通过转数传感器来获取电机输出轴的旋转圈数)或丝杆传动组件32的当前旋转圈数(即丝杆324的旋转圈数，可通过获取电机的旋转圈数从而间接得知丝杆324的旋转圈数)；
S21、判断当前旋转圈数是否超过预设圈数阈值，来确定活塞2是否运动至下止点，其中，预设圈数阈值是指活塞2从零点位置运动至下止点时电机输出轴的旋转圈数或丝杆324的旋转圈数，若电机的当前旋转圈数或丝杆传动组件32的当前旋转圈数未超过预设圈数阈值，则执行步骤S20；若电机的当前旋转圈数或丝杆传动组件32的当前旋转圈数等于预设圈数阈值，则执行步骤S22。
S22、电机的当前旋转圈数或丝杆传动组件32的当前旋转圈数等于预设圈数阈值，电机控制器会生成停止运转指令，并执行该停止运转指令，电机停止沿第二方向旋转，行星齿轮组件31和丝杆传动组件32停止沿第二方向旋转，进而控制从动件33(活塞2)停止运 动，活塞2停止在下止点，即活塞2一旦到达下止点就自动停止运动，避免活塞2与工作腔的底面发生碰撞。
若电机的当前旋转圈数或丝杆传动组件32的当前旋转圈数未超过预设圈数阈值，则电机控制器生成继续运转指令，并执行该继续运转指令，控制电机继续沿第二方向旋转，直至电机的当前旋转圈数或丝杆传动组件32的当前旋转圈数等于预设圈数阈值(活塞2运动至下止点)，控制电机停止沿第二方向旋转。
本实施例中，第一方向和第二方向根据丝杆324的螺纹旋向来决定的，例如：若丝杆324的螺纹为右旋，则第一方向为逆时针方向，从动件33相对丝杆324向上移动，第二方向为顺时针方向，从动件33相对丝杆324向下移动；若丝杆324的螺纹为左旋，则第一方向为顺时针方向，从动件33相对丝杆324向上移动，第二方向为逆时针方向，从动件33相对丝杆324向下移动。
本申请用于制动系统的活塞泵组的操作过程如下：先对活塞2进行零点校准，然后再控制活塞2从零点位置向下运动至下止点，排出工作腔内的液体进行制动，最后控制活塞2回程，从下止点向上运动，往工作腔内吸入液体。具体地，根据使用需求，活塞泵组的工作可以是一个连续的过程，即活塞2零点校准后，活塞2在零点位置和下止点之间进行连续往复运动。
本申请实施例所提供的一种用于制动系统的活塞泵组及其控制方法，与现有技术相比，本申请具有以下有益效果：
1、通过在丝杆传动组件32与从动件33之间设置有用于限制从动件33运动的限位部件34，这样，可以避免从动件33在向上运动(工作腔的工作容积变大)时从动件33与别的部件发生碰撞干涉，同时，还可以通过限位部件34来实现活塞2的零点校准，即当从动件33被限位部件34阻挡停止运动后，工作腔的工作容积最大，此时活塞2处于零点位置，以保证活塞泵组排出的液体具有足够的压力，来为制动系统提供稳定的制动压力；
2、从动件33与活塞2采用螺纹连接的方式固定，可以很好地避免因过盈压装出现活塞2膨胀变形问题，保证活塞2与工作腔具有较好的同轴度，活塞2与工作腔配合紧密，工作腔容积的变化过程气密性好；
3、从动件33与活塞2采用螺纹连接的方式，活塞2与从动件33为面接触，增大受力面积，可以很好的避免应力集中，从而提高活塞2的使用寿命；
4、轴承内圈322与丝杆324采用一体成型的结构，结构强度高，不会出现轴承内圈322与丝杆324过盈压装时轴承内圈322发生变形的现象，从而保证活塞泵组整体结构的稳定性。
5、丝杆324采用中空结构设计，可避免活塞2远离限位部件34运动(向下运动)时， 活塞2与丝杆324之间产生负压，或者，可避免活塞2靠近限位部件34运动(向上运动)时，活塞2与丝杆324之间产生正压，从而致使活塞2运动时阻力增加，进而导致驱动活塞2运动时所需能耗增加；
6、通过判断当前旋转圈数与预设圈数阈值的关系，来确认活塞2与工作腔底面之间的距离，即控制活塞2在下止点处自动停止运动，以避免活塞2远离限位部件34运动(向下运动)时，活塞2与工作腔的底面发生碰撞，从而进一步延长了活塞2的使用寿命。
在本申请的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本申请的描述中，“多个”的含义是两个以上，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的 技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本申请的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本申请的限制，本领域的普通技术人员在本申请的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (10)

  1. 一种用于制动系统的活塞泵组，包括活塞、具有工作腔的泵体和用于带动所述活塞在所述工作腔内运动的传动机构，其特征在于，所述传动机构包括丝杆传动组件、从动件和用于将动力传递给所述丝杆传动组件的行星齿轮组件，所述从动件与所述活塞固定连接，所述丝杆传动组件用于带动所述从动件相对所述工作腔运动，所述丝杆传动组件与所述从动件之间设置有用于限制所述从动件运动的限位部件。
  2. 如权利要求1所述的用于制动系统的活塞泵组，其特征在于，所述行星齿轮组件包括主动轮、内齿环、行星盖和多个行星齿轮，多个所述行星齿轮分别与所述内齿环啮合连接，所述行星齿轮位于所述主动轮与所述内齿环之间，且所述主动轮分别与每一个行星齿轮啮合连接，所述行星盖通过定位结构与所述内齿环配合连接。
  3. 如权利要求2所述的用于制动系统的活塞泵组，其特征在于，所述定位结构包括设于所述行星盖内圈周向的凹槽和设于所述内齿环外圈周向用于与所述凹槽配合的凸起，或者，所述定位结构包括设于所述行星盖内圈周向的凸起和设于所述内齿环外圈周向用于与所述凸起配合的凹槽。
  4. 如权利要求2或3所述的用于制动系统的活塞泵组，其特征在于，所述丝杆传动组件包括轴承外圈、轴承内圈、轴承保持架和丝杆，所述轴承外圈套设于所述轴承内圈外，所述轴承保持架设于所述轴承外圈与所述轴承内圈之间，所述轴承保持架设置有多个用于容置滚珠的容置腔，所述轴承内圈与所述丝杆的一端固定连接，所述从动件与所述丝杆螺纹连接，每一个所述行星齿轮通过行星销设于所述轴承内圈的顶面上，且所述行星盖与所述轴承外圈固定连接。
  5. 如权利要求4所述的用于制动系统的活塞泵组，其特征在于，所述丝杆与所述轴承内圈为一体成型结构。
  6. 如权利要求5所述的一种用于制动系统的活塞泵组，其特征在于，所述丝杆为中空结构，沿所述丝杆的轴向方向设置有一通孔。
  7. 如权利要求4-6中任一项所述的用于制动系统的活塞泵组，其特征在于，所述限位部件为限位销，所述限位销贯穿于所述轴承内圈形成有一碰撞部，所述从动件上设置有用于与所述碰撞部进行接触限位的碰撞结构。
  8. 一种控制方法，其特征在于，用于控制如权利要求1至7中任一项所述的用于制动系统的活塞泵组,所述控制方法包括活塞的零点校准，具有包括以下步骤：
    S10、控制电机沿第一方向旋转，带动行星齿轮组件沿第一方向旋转，进而带动丝杆传动组件沿第一方向旋转，从动件随所述丝杆传动组件的旋转靠近限位部件运动；
    S11、当所述从动件的碰撞结构接触到所述限位部件时，控制所述电机停止运转，以致所述行星齿轮组件和所述丝杆传动组件停止旋转，从而使所述从动件和所述活塞停止轴向运动，此时活塞所处位置为零点位置。
  9. 如权利要求8所述的控制方法，其特征在于，所述控制方法还包括在步骤S11后控制所述活塞在下止点自动停止轴向运动，所述下止点为距离泵体底部内壁预设距离的位置。
  10. 如权利要求9所述的控制方法，其特征在于，控制所述活塞在下止点自动停止轴向运动的步骤，包括：
    S20、控制所述电机沿第二方向旋转，带动所述行星齿轮组件沿第二方向旋转，从而带动所述丝杆传动组件沿第二方向旋转，所述从动件随所述丝杆传动组件的旋转远离所述限位部件运动，并实时获取所述电机的当前旋转圈数或所述丝杆传动组件的当前旋转圈数；
    S21、判断所述当前旋转圈数是否超过预设圈数阈值；若所述当前旋转圈数未超过所述预设圈数阈值，则执行步骤S20，若所述当前旋转圈数等于所述预设圈数阈值，则执行步骤S22，
    S22、控制所述电机停止沿第二方向旋转，以致所述行星齿轮组件和所述丝杆传动组件停止沿第二方向旋转，从而使所述从动件和所述活塞停止轴向运动，此时所述活塞所处位置为所述下止点。
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