WO2021088340A1 - 旋转角度控制装置、自动间隙调整臂及汽车制动器 - Google Patents

旋转角度控制装置、自动间隙调整臂及汽车制动器 Download PDF

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Publication number
WO2021088340A1
WO2021088340A1 PCT/CN2020/088459 CN2020088459W WO2021088340A1 WO 2021088340 A1 WO2021088340 A1 WO 2021088340A1 CN 2020088459 W CN2020088459 W CN 2020088459W WO 2021088340 A1 WO2021088340 A1 WO 2021088340A1
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WO
WIPO (PCT)
Prior art keywords
hole
worm
rotation angle
control device
clutch sleeve
Prior art date
Application number
PCT/CN2020/088459
Other languages
English (en)
French (fr)
Inventor
叶天赠
叶嘉达
廖子润
蔡用杰
Original Assignee
Bpw(梅州）车轴有限公司
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 Bpw(梅州）车轴有限公司 filed Critical Bpw(梅州）车轴有限公司
Priority to SG11202105337XA priority Critical patent/SG11202105337XA/en
Priority to EP20820039.4A priority patent/EP3848605B1/en
Priority to RU2021114049A priority patent/RU2770333C1/ru
Priority to AU2020294274A priority patent/AU2020294274B2/en
Priority to JP2021523605A priority patent/JP7209827B2/ja
Publication of WO2021088340A1 publication Critical patent/WO2021088340A1/zh

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    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/58—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with eccentric or helical body
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/62—Slack adjusters mechanical self-acting in both directions for adjusting excessive and insufficient play
    • F16D65/70—Slack adjusters mechanical self-acting in both directions for adjusting excessive and insufficient play for angular adjustment of two concentric parts of the brake control system
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/52—Rotating members in mutual engagement with non-parallel stationary axes, e.g. worm or bevel gears
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/68—Lever-link mechanisms, e.g. toggles with change of force ratio
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/561—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting within the confines of a drum brake
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H1/222—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes
    • F16H1/225—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with non-parallel axes with two or more worm and worm-wheel gearings
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0213—Support of worm gear shafts
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F16H2057/0221—Axial adjustment
    • 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
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring
    • F16H2057/127—Self-adjusting during operation, e.g. by a spring using springs

Definitions

  • the present disclosure is based on the application with the CN application number 201911064001.1 and the filing date of November 4, 2019, and claims priority.
  • the disclosure of the CN application is hereby incorporated into the present disclosure as a whole.
  • the present disclosure relates to the technical field of automobile brakes, in particular to a rotation angle control device, an automatic gap adjustment arm and an automobile brake.
  • the automatic gap adjustment arm of the automobile brake realizes the automatic adjustment function of the brake gap by controlling the rotation angle of the adjustment arm.
  • the rotation angle control device is realized by mutually meshing unidirectional ratchet teeth.
  • a rotation angle control device including:
  • the transmission gear is sleeved on the mandrel
  • the clutch sleeve is sleeved on the mandrel and has a first axial counterbore located on the end surface of the clutch sleeve on the side away from the transmission gear;
  • the outer support spring is sleeved on the mandrel and has an outer circular surface that is in interference fit with the inner surface of the first axial counterbore and the second axial counterbore.
  • the transmission gear is configured to rotate relative to the second worm in the first rotation direction to the top position.
  • the clutch sleeve is driven to rotate in the same direction along the first rotation direction, so that the friction force of the first axial counterbore of the clutch sleeve on the outer circular surface of the outer support spring causes the The outer support spring rotates and shrinks radially inward, so that the clutch sleeve rotates and slips relative to the outer support spring and the second worm, and is opposed to the clutch sleeve in a second rotation direction opposite to the first rotation direction.
  • the second worm When the second worm rotates to abut against the clutch sleeve, it drives the clutch sleeve to rotate in the same direction in the second rotation direction, so as to pass the first axial counterbore of the clutch sleeve to the outer support spring
  • the friction force of the outer circular surface causes the outer support spring to rotate and radially outwardly support, so that the clutch sleeve, the outer support spring and the second worm are relatively locked and rotate synchronously.
  • the transmission gear has a slot extending in the axial direction
  • an end of the clutch sleeve away from the second worm has an insert block that can be axially inserted into the slot, and the insert block is opposite to The slot is rotatable, and the circumferential width of the insert block is smaller than the circumferential width of the slot to form a preset rotation gap between the transmission gear and the clutch sleeve.
  • the rotation angle control device further includes:
  • the return torsion spring is sleeved on the core shaft and is located between the transmission gear and the clutch sleeve, wherein the hooks at both ends of the return torsion spring are respectively buckled on the side of the slot On the wall and the insert block.
  • the outer support spring is a right-handed outer support spring
  • the first rotation direction is a counterclockwise direction
  • the second rotation direction is a clockwise direction
  • the rotation angle control device further includes:
  • the spacer is located between the outer support spring and the mandrel, and the outer diameter of the spacer is smaller than the size of the inner hole when the outer support spring shows a shrinking trend, and the outer diameter of the spacer It is also smaller than the inner hole size of the outer support spring after interference assembly.
  • the axial length of the spacer is smaller than the sum of the depths of the first axial counterbore and the second axial counterbore.
  • the rotation angle control device further includes:
  • a shaft sleeve one end abuts against the end of the second worm, and the other end has a gap elimination cavity
  • the gap elimination spring is sleeved in the gap elimination cavity
  • the shaft sleeve is sleeved on the mandrel, and is connected with the mandrel through a buckle.
  • the sleeve further has a fifth through hole that penetrates the gap elimination cavity, and the inner wall of the fifth through hole has an elastic block that extends into the gap elimination cavity.
  • the side of the clamping block facing the fifth through hole has a guiding inclined surface, and the mandrel has a clamping slot matching the elastic clamping block.
  • an automatic gap adjustment arm including:
  • the housing has a first through hole and a second through hole that communicate with each other, and a mounting hole that is parallel to the axis of the first through hole and communicates with both the first through hole and the second through hole;
  • the worm gear is arranged in the first through hole
  • the first worm is arranged in the second through hole and is matched with the worm wheel;
  • a coil spring arranged at one end of the first worm
  • the clutch gear is sleeved on the other end of the first worm
  • the control disk assembly is provided at one end of the first through hole and includes a ring gear
  • the aforementioned rotation angle control device is arranged in the mounting hole,
  • the transmission gear in the rotation angle control device meshes with the ring gear
  • the second worm in the rotation angle control device meshes with the clutch gear
  • control panel assembly further includes:
  • a cover plate covering one side of the first through hole along the axial direction of the first through hole and shielding the opening of the mounting hole;
  • control arm and the gear ring are respectively located on both sides of the cover plate, and are fixedly connected with the gear ring,
  • control arm and the gear ring can rotate synchronously with respect to the cover plate.
  • the mounting hole is a blind hole
  • the rotation angle control device further includes a shaft sleeve and a gap elimination spring
  • the shaft sleeve is sleeved on the mandrel and connected to the mandrel by a buckle
  • One end of the shaft sleeve abuts against the end of the second worm, and the other end has a gap elimination cavity.
  • One end of the gap elimination spring abuts in the gap elimination cavity, and the other end abuts in the installation hole.
  • the automatic gap adjustment arm further includes:
  • the upper cover and the lower cover are respectively arranged at both ends of the second through hole in the axial direction.
  • the housing further has a fourth through hole communicating with the second through hole
  • the automatic gap adjustment arm further includes an oil nozzle located in the fourth through hole and a cover attached to the fourth through hole. Dust cover on the nozzle.
  • an automobile brake which includes the aforementioned automatic gap adjustment arm.
  • Fig. 1 is a schematic structural exploded view of an embodiment of an automatic gap adjustment arm of the present disclosure
  • FIG. 2 is a schematic structural exploded view of an embodiment of the rotation angle control device of the present disclosure
  • FIG. 3 is a partial cross-sectional view of the installation structure of an embodiment of the rotation angle control device of the present disclosure
  • FIG. 4 is a schematic diagram of the external structure of an embodiment of the rotation angle control device of the present disclosure.
  • Figure 5 is a cross-sectional view of the A-A section in Figure 4.
  • Figure 6 is a cross-sectional view of the B-B section in Figure 4.
  • Fig. 7 is a structural diagram of a control panel assembly in an embodiment of the automatic gap adjustment arm of the present disclosure
  • Fig. 8 is a cross-sectional view of a shaft sleeve in an embodiment of the rotation angle control device of the present disclosure.
  • a specific device when it is described that a specific device is located between the first device and the second device, there may or may not be an intermediate device between the specific device and the first device or the second device.
  • the specific device When it is described that a specific device is connected to another device, the specific device may be directly connected to the other device without an intervening device, or may not be directly connected to the other device but with an intervening device.
  • N teeth due to factors such as the strength of the one-way ratchet, generally N teeth (usually N is 10-20 teeth) can be arranged in the circumferential direction as the adjustment transmission mechanism.
  • N usually N is 10-20 teeth
  • the gear tooth meshing part of the driving one-way ratchet crosses one tooth, it rotates during the brake return and drives the adjustment mechanism to compensate for the gap.
  • the rotation angle of the adjusting arm is greater than the set value, but not enough to drive the gear tooth meshing part of the one-way ratchet to mesh to the next tooth, it can only be compensated slowly by other mechanisms, which makes the automatic adjustment action of the adjusting arm lag. For example: After a car is newly assembled with an automatic adjustment arm and adjusted the initial gap, it needs to step on the brakes 30-60 feet to reach the set gap. Moreover, after the automatic adjustment of the adjusting arm is completed, the brake clearance fluctuates greatly.
  • the present disclosure provides a rotation angle control device, an automatic gap adjustment arm and an automobile brake, which can realize the automatic adjustment action of the adjustment arm more quickly and reliably.
  • the automatic gap adjustment arm includes: a housing 1, a worm wheel 4, a first worm 5, a coil spring 6, a clutch gear 7, a control disc assembly, and a rotation angle control device.
  • the housing 1 has a first through hole 2 and a second through hole 3 communicating with each other, and the axis of the first through hole 2 is parallel to each other and the same as the first through hole 2 and the second through hole 3 Connected mounting hole 10.
  • the worm wheel 4 is arranged in the first through hole 2, and the first worm 5 is arranged in the second through hole 3 to match the worm wheel 4.
  • the coil spring 6 is arranged at one end of the first worm 5, and the clutch gear 7 is sleeved on the other end of the first worm 5.
  • the control disk assembly is arranged at one end of the first through hole 2 and includes a ring gear 9.
  • the rotation angle control device is arranged in the mounting hole 10.
  • the rotation angle control device includes: a core shaft 12, a transmission gear 13, a clutch sleeve 15, a second worm 18 and an external support spring 16.
  • the transmission gear 13 is sleeved on the core shaft 12 and can mesh with the ring gear 9.
  • the clutch sleeve 15 is sleeved on the mandrel 12 and has a first axial counterbore 141 on the end surface of the clutch sleeve 15 away from the transmission gear 13.
  • the second worm 18 is sleeved on the core shaft 12 and has a second axial counterbore 161 located on the end surface of the second worm 18 adjacent to the transmission gear 13.
  • the outer support spring 16 is sleeved on the core shaft 12 and has an outer circular surface that is in interference fit with the inner hole surfaces of the first axial counterbore 141 and the second axial counterbore 161.
  • the second worm 18 can mesh with the clutch gear 7.
  • the outer circular surfaces at both ends of the outer support spring 16 are respectively in interference fit with the inner hole surfaces of the first axial counterbore 141 of the clutch sleeve 15 and the second axial counterbore 161 of the second worm 18. In this way, the outer circular surface of the outer support spring 16 and the inner surface of the first axial counterbore 141 and the second axial counterbore 161 respectively form a friction pair, thereby forming a torsion spring clutch mechanism.
  • the outer support spring 16 shows a tendency to deform in the retracting direction under the action of friction, so that the friction pair The pressure is reduced, so that the clutch sleeve 15 can overcome the frictional force and rotate relative to the second worm 18.
  • the outer support spring 16 appears outward under the action of friction.
  • the tendency of spreading makes the pressure of the friction pair increase as the torque of the clutch sleeve 15 rotates in the second rotation direction, so that the clutch sleeve 15 is limited by the frictional force and interacts with the outer support spring 16 and the second worm 18 In a locked state without relative rotation.
  • the outer support spring 16 acts as a one-way clutch during the entire process.
  • this embodiment uses the outer support spring 16 as the one-way clutch, which can be divided infinitely in the circumferential direction, thereby achieving faster stepless adjustment and avoiding the lagging of the automatic adjustment function of the related technology. Problems, and then to ensure driving safety. Moreover, after the automatic adjustment of the adjusting arm is completed, the brake gap fluctuation is small.
  • the outer support spring of this embodiment shows an outward expansion trend when it is locked.
  • Using this outward expansion trend can increase the external support spring and the first axial direction.
  • the friction force between the counterbore and the inner bore surface of the second axial counterbore thereby realizing the self-locking effect.
  • a greater locking force can be achieved compared with the holding spring, thereby transmitting greater torque and avoiding slippage failure, thereby ensuring the adjustment arm
  • the automatic adjustment function will not fail to ensure driving safety.
  • the transmission gear 13 can rotate relative to the second worm 18 to abut against the clutch sleeve 15 in the first rotation direction, it drives the clutch sleeve 15 to rotate in the same direction in the first rotation direction to pass the clutch sleeve 15
  • the friction force of the first axial counterbore 141 of the sleeve 15 on the outer circular surface of the outer support spring 16 causes the outer support spring 16 to rotate and contract radially inwardly, so that the clutch sleeve 15 is relative to the outer
  • the support spring 16 and the second worm 18 rotate and slip.
  • the transmission gear 13 can also drive the clutch sleeve 15 to rotate in the second rotation direction relative to the second worm 18 to abut against the clutch sleeve 15 in a second rotation direction opposite to the first rotation direction. Rotate in the same direction so that the friction force of the first axial counterbore 141 of the clutch sleeve 15 on the outer circular surface of the outer support spring 16 causes the outer support spring 16 to rotate and radially outwardly support.
  • the clutch sleeve 15 is relatively locked with the outer support spring 16 and the second worm 18 to rotate synchronously.
  • the outer support spring 16 is a right-handed outer support spring
  • the first rotation direction is a counterclockwise direction
  • the second rotation direction is a clockwise direction.
  • the ring gear 9 drives the transmission gear 13 to rotate counterclockwise.
  • the transmission gear 13 rotates by the preset rotation gap ⁇
  • it will drive the clutch sleeve 15 to rotate counterclockwise
  • the outer support spring 16 will deform in the inward direction under the action of friction.
  • the pressure of the friction pair formed by the inner hole surface of the clutch sleeve 15 and the outer circular surface of the outer support spring 16 decreases, and the friction force decreases accordingly.
  • the clutch sleeve 15 rotates relative to the second worm 18 against the frictional force, and the rotation angle is the rotation angle of the clutch sleeve 15 minus the preset rotation gap ⁇ .
  • the ring gear 9 drives the transmission gear 13 to rotate clockwise.
  • the transmission gear 13 rotates by the preset rotation gap ⁇ , it will drive the clutch sleeve 15 to rotate clockwise, and the outer support spring 16 will deform in the outward spreading direction under the action of friction.
  • the clutch sleeve 15 is limited by friction and is locked with the outer support spring 16 and the second worm 18 to form an integral rigid structure. At this time, the clutch sleeve 15 drives the second worm 18 to rotate clockwise to eliminate the excessive rotation angle exceeding the set value ⁇ °.
  • the rotation angle control device further includes a spacer 17.
  • the spacer 17 is located between the outer support spring 16 and the mandrel 12, and the outer diameter of the spacer 17 is smaller than the inner hole size of the outer support spring 16 when the outer support spring 16 shows a shrinking trend.
  • the outer diameter of the spacer 17 is also smaller than the inner hole size of the outer support spring 16 after interference assembly.
  • the spacer 17 located between the outer support spring 16 and the core shaft 12 can maintain the coaxial relationship among the clutch sleeve 15, the outer support spring 16 and the second worm 18 when the force is locked, and the outer support spring 16 acts To the limit effect, the risk of excessive tangential deformation of the outer support spring 16 resulting in misalignment between the clutch sleeve 15 and the second worm 18 is reduced, thereby effectively increasing the service life of the product.
  • the axial length of the spacer sleeve 17 is less than the sum of the depths of the first axial counterbore 141 and the second axial counterbore 161, so as to avoid the gap between the clutch sleeve 15 and the second worm 18
  • the axial position of the camera causes restrictions.
  • the transmission gear 13 has an axially extending slot 13a
  • the end of the clutch sleeve 15 away from the second worm 18 has an axially inserted slot 13a.
  • INSERT 15a The insert block 15a is rotatable relative to the slot 13a, and the circumferential width of the insert block 15a is smaller than the circumferential width of the slot 13a to form a gap between the transmission gear 13 and the clutch sleeve 15 The preset rotation gap between.
  • the number of the slots 13a of the transmission gear 13 and the insert blocks 15a of the clutch sleeve 15 can be one or more respectively.
  • the number of slots 13a and insert blocks 15a are both two, and the matching structure of the two slots 13a and the two insert blocks 15a can achieve a greater bearing capacity between the transmission gear 13 and the clutch sleeve 15. The structure is more reliable.
  • the slot 13a has a first side wall 171 and a second side wall 172.
  • the first side wall 171 abuts against the side wall of the insert block 15a of the clutch sleeve 15, and the transmission gear 13 drives the clutch sleeve 15 to rotate clockwise.
  • the second side wall 172 abuts against the side wall of the insert block 15a of the clutch sleeve 15, and the transmission gear 13 drives the clutch sleeve 15 to counterclockwise.
  • the hour hand rotates.
  • the rotation angle control device further includes a return torsion spring 14.
  • the return torsion spring 14 is sleeved on the core shaft 12 and is located between the transmission gear 13 and the clutch sleeve 15.
  • the hooks at both ends of the return torsion spring 14 are respectively buckled on the side wall of the slot 13a and the insert block 15a, so that the return torsion spring 14 can protect the transmission gear 13 and the clutch sleeve 15 from external force. Maintain the set position in the state.
  • the rotation angle control device further includes: a shaft sleeve 19 and a gap elimination spring 20.
  • One end of the sleeve 19 abuts against the end of the second worm 18, and the other end has a gap elimination cavity 19a.
  • the gap elimination spring 20 is sleeved in the gap elimination cavity 19a.
  • the shaft sleeve 19 is sleeved on the mandrel 12 and is connected with the mandrel 12 through a buckle.
  • the sleeve 19 also has a fifth through hole 28 that penetrates the gap elimination cavity 19a, and the inner wall of the fifth through hole 28 has an elastic block extending into the gap elimination cavity 19a. 29.
  • the elastic blocking block 29 has a guiding inclined surface 31 on one side facing the fifth through hole 28, and the mandrel 12 has a clamping slot 30 matching the elastic blocking block 29.
  • the front end of the mandrel 12 passes through the transmission gear 13, the return torsion spring 14, the clutch sleeve 15, the outer support spring 16, the spacer 17, the second worm 18 and the fifth through hole 28 to make the elastic block 29 is embedded in the slot 30 of the mandrel 12, which is simple and convenient to assemble.
  • the sleeve 19 may have a plurality of elastic blocks 29.
  • the card slot 30 may be a circular card slot.
  • control panel assembly in the automatic gap adjustment arm may further include a cover plate 22 and a control arm 8.
  • the cover plate 22 covers one side of the first through hole 2 along the axial direction of the first through hole 2 and blocks the opening of the mounting hole 10.
  • the mounting hole 10 may be a stepped hole, and the mounting hole 10 is shielded on one side by the cover plate 22 to facilitate the processing of the mounting hole 10, reduce production costs, and achieve the effect of waterproof and dustproof.
  • the control arm 8 and the gear ring 9 are respectively located on both sides of the cover plate 22, and are fixedly connected with the gear ring 9 (for example, riveting, etc.).
  • the control arm 8 and the ring gear 9 can rotate synchronously with respect to the cover 22.
  • the aforementioned gap elimination spring 20 can abut one end into the gap elimination cavity 19 a and the other end into the mounting hole 10.
  • the automatic gap adjustment arm further includes: an upper cover 23 and a lower cover 24 respectively provided at both ends of the second through hole 3 in the axial direction.
  • the upper cover 23 and the lower cover 24 can seal both ends of the second through hole 3.
  • the housing 1 also has a fourth through hole communicating with the second through hole 3, and the automatic gap adjustment arm further includes an oil nozzle 25 located in the fourth through hole and a cover on the oil nozzle 25 The dust cover 26. Lubricating oil or the like can be injected into the housing 1 through the oil nozzle 25 to reduce wear, improve performance, and prolong service life.
  • the various embodiments of the above-mentioned automatic gap adjustment arm can be applied to automobile brakes. Therefore, the present disclosure also provides an automobile brake including any of the aforementioned automatic gap adjustment arms.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Mechanical Operated Clutches (AREA)
  • Braking Arrangements (AREA)

Abstract

一种旋转角度控制装置，包括：芯轴（12）；传动齿轮（13），套设在芯轴（12）上；离合套（15），套设在芯轴（12）上，且具有位于离合套（15）远离传动齿轮（13）一侧的端面上的第一轴向沉孔（141）；第二蜗杆（18），套设在芯轴（12）上，且具有位于第二蜗杆（18）邻近传动齿轮（13）一侧的端面上的第二轴向沉孔（161）；和外撑弹簧（16），套设在芯轴（12）上，且具有与第一轴向沉孔（141）和第二轴向沉孔（161）的内孔面过盈配合的外圆面。还涉及包括旋转角度控制装置的自动间隙调整臂，以及包括自动间隙调整臂的汽车制动器。

Description

旋转角度控制装置、自动间隙调整臂及汽车制动器
相关申请的交叉引用
本公开是以CN申请号为201911064001.1，申请日为2019年11月4日的申请为基础，并主张优先权，该CN申请的公开内容在此作为整体引入本公开中。
技术领域
本公开涉及汽车制动器技术领域，特别是一种旋转角度控制装置、自动间隙调整臂及汽车制动器。
背景技术
汽车制动器的自动间隙调整臂通过控制调整臂旋转角度来实现制动间隙的自动调整功能。当调整臂的旋转角度大于设定值时其自动调整功能会被触发。在相关技术中，旋转角度控制装置是通过相互啮合的单向棘轮齿来实现的。
发明内容
在本公开的一个方面，提供一种旋转角度控制装置，包括：
芯轴；
传动齿轮，套设在所述芯轴上；
离合套，套设在所述芯轴上，且具有位于所述离合套远离所述传动齿轮一侧的端面上的第一轴向沉孔；
第二蜗杆，套设在所述芯轴上，且具有位于所述第二蜗杆邻近所述传动齿轮一侧的端面上的第二轴向沉孔；和
外撑弹簧，套设在所述芯轴上，且具有与所述第一轴向沉孔和所述第二轴向沉孔的内孔面过盈配合的外圆面。
在一些实施例中，所述传动齿轮与所述离合套之间在周向上具有预设转动间隙，所述传动齿轮被配置为在第一转动方向上相对所述第二蜗杆转动至抵顶所述离合套时，带动所述离合套沿所述第一转动方向同向转动，以通过所述离合套的第一轴向沉孔对所述外撑弹簧的外圆面的摩擦力使所述外撑弹簧转动而径向内缩，从而使所述离合套相对于所述外撑弹簧和所述第二蜗杆转动打滑，以及在与所述第一转动方向相反 的第二转动方向上相对所述第二蜗杆转动至抵顶所述离合套时，带动所述离合套沿所述第二转动方向同向转动，以通过所述离合套的第一轴向沉孔对所述外撑弹簧的外圆面的摩擦力使所述外撑弹簧转动而径向外撑，从而使所述离合套与所述外撑弹簧和所述第二蜗杆相对锁止而同步转动。
在一些实施例中，所述传动齿轮具有沿轴向延伸的插槽，所述离合套远离所述第二蜗杆的一端具有能够轴向插入所述插槽的插块，所述插块相对于所述插槽可转动，且所述插块的周向宽度小于所述插槽的周向宽度，以形成所述传动齿轮与所述离合套之间的预设转动间隙。
在一些实施例中，所述旋转角度控制装置还包括：
回位扭簧，套设在所述芯轴上，且位于所述传动齿轮和所述离合套之间，其中，所述回位扭簧两端的搭钩分别搭扣在所述插槽的侧壁和所述插块上。
在一些实施例中，所述外撑弹簧为右旋外撑弹簧，所述第一转动方向为逆时针方向，所述第二转动方向为顺时针方向。
在一些实施例中，所述旋转角度控制装置还包括：
隔套，位于所述外撑弹簧与所述芯轴之间，且所述隔套的外圆直径小于所述外撑弹簧呈现内缩趋势时的内孔尺寸，所述隔套的外圆直径也小于所述外撑弹簧过盈装配后的内孔尺寸。
在一些实施例中，所述隔套的轴向长度小于所述第一轴向沉孔和所述第二轴向沉孔的深度之和。
在一些实施例中，所述旋转角度控制装置还包括：
轴套，一端与所述第二蜗杆的端部相抵，另一端具有间隙消除腔；和
间隙消除弹簧，套装在所述间隙消除腔内，
其中，所述轴套套在所述芯轴上，并通过卡扣与所述芯轴连接。
在一些实施例中，所述轴套还具有与所述间隙消除腔贯通的第五通孔，所述第五通孔的内壁具有伸入所述间隙消除腔内的弹性卡块，所述弹性卡块朝向所述第五通孔的一侧具有导向斜面，所述芯轴具有与所述弹性卡块相匹配的卡槽。
在本公开的一个方面，提供了一种自动间隙调整臂，包括：
壳体，具有相互连通的第一通孔和第二通孔，以及与所述第一通孔轴线相互平行、且与所述第一通孔和所述第二通孔均连通的安装孔；
蜗轮，设置在所述第一通孔内；
第一蜗杆，设置在所述第二通孔内，与所述蜗轮相匹配；
螺旋弹簧，设置在所述第一蜗杆的一端；
离合齿轮，套设在所述第一蜗杆的另一端；
控制盘组件，设置在所述第一通孔的一端，且包括齿圈；和
前述的旋转角度控制装置，设置在所述安装孔内，
其中，所述旋转角度控制装置中的传动齿轮与所述齿圈啮合，所述旋转角度控制装置中的第二蜗杆与所述离合齿轮啮合。
在一些实施例中，所述控制盘组件还包括：
盖板，沿所述第一通孔的轴向覆盖在所述第一通孔的一侧，并遮挡所述安装孔的孔口；和
控制臂，与所述齿圈分别位于所述盖板的两侧，且与所述齿圈固定连接，
其中，所述控制臂和所述齿圈相对于所述盖板可同步转动。
在一些实施例中，所述安装孔为盲孔，所述旋转角度控制装置还包括轴套和间隙消除弹簧，所述轴套套在所述芯轴上，并通过卡扣与所述芯轴连接，所述轴套的一端与所述第二蜗杆的端部相抵，另一端具有间隙消除腔，所述间隙消除弹簧一端抵在所述间隙消除腔内，另一端抵在所述安装孔内。
在一些实施例中，所述自动间隙调整臂还包括：
上封盖和下封盖，分别设置在所述第二通孔沿轴向的两端。
在一些实施例中，所述壳体还具有与所述第二通孔连通的第四通孔，所述自动间隙调整臂还包括位于所述第四通孔内的油嘴和盖合在所述油嘴上的防尘罩。
在本公开的一个方面，提供一种汽车制动器，包括前述的自动间隙调整臂。
附图说明
构成说明书的一部分的附图描述了本公开的实施例，并且连同说明书一起用于解释本公开的原理。
参照附图，根据下面的详细描述，可以更加清楚地理解本公开，其中：
图1是本公开自动间隙调整臂的一实施例的结构分解示意图；
图2是本公开旋转角度控制装置的一实施例的结构分解示意图；
图3是本公开旋转角度控制装置的一实施例的安装结构的局部剖视图；
图4是本公开旋转角度控制装置的一实施例的外部结构示意图；
图5是图4中A-A截面的剖视图；
图6是图4中B-B截面的剖视图；
图7是本公开自动间隙调整臂的一实施例中控制盘组件的结构示意图；
图8是本公开旋转角度控制装置的一实施例中轴套的剖视图。
应当明白，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。此外，相同或类似的参考标号表示相同或类似的构件。
具体实施方式
现在将参照附图来详细描述本公开的各种示例性实施例。对示例性实施例的描述仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。本公开可以以许多不同的形式实现，不限于这里所述的实施例。提供这些实施例是为了使本公开透彻且完整，并且向本领域技术人员充分表达本公开的范围。应注意到：除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、材料的组分、数字表达式和数值应被解释为仅仅是示例性的，而不是作为限制。
本公开中使用的“第一”、“第二”以及类似的词语并不表示任何顺序、数量或者重要性，而只是用来区分不同的部分。“包括”或者“包含”等类似的词语意指在该词前的要素涵盖在该词后列举的要素，并不排除也涵盖其他要素的可能。“上”、“下”、“左”、“右”等仅用于表示相对位置关系，当被描述对象的绝对位置改变后，则该相对位置关系也可能相应地改变。
在本公开中，当描述到特定器件位于第一器件和第二器件之间时，在该特定器件与第一器件或第二器件之间可以存在居间器件，也可以不存在居间器件。当描述到特定器件连接其它器件时，该特定器件可以与所述其它器件直接连接而不具有居间器件，也可以不与所述其它器件直接连接而具有居间器件。
本公开使用的所有术语(包括技术术语或者科学术语)与本公开所属领域的普通技术人员理解的含义相同，除非另外特别定义。还应当理解，在诸如通用字典中定义的术语应当被解释为具有与它们在相关技术的上下文中的含义相一致的含义，而不应用理想化或极度形式化的意义来解释，除非这里明确地这样定义。
对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为说明书的一部分。
在一些相关技术中，迫于单向棘轮的强度等因素，一般可在圆周方向设置N齿(通 常N为10-20齿)作为调整传动机构。当调整臂旋转角度大于设定值，且驱动单向棘轮的轮齿啮合部位跨过一齿时，在制动回程时旋转，并带动调整机构补偿间隙。当调整臂旋转角度大于设定值，但又不足于驱动单向棘轮的轮齿啮合部位啮合至下一个齿时，则只能通过其他机构慢慢补偿，这使得调整臂的自动调整动作滞后。例如：汽车在新装配自动调整臂并调整好初始间隙后，需踩刹车30-60脚才能达到设定的间隙。而且调整臂在自动调整完成后，刹车间隙波动较大。
有鉴于此，本公开提供一种旋转角度控制装置、自动间隙调整臂及汽车制动器，能够更快速可靠地实现调整臂的自动调整动作。
如图1所示，为本公开自动间隙调整臂的一实施例的结构分解示意图。参考图1，在一些实施例中，自动间隙调整臂，包括：壳体1、蜗轮4、第一蜗杆5、螺旋弹簧6、离合齿轮7、控制盘组件和旋转角度控制装置。壳体1具有相互连通的第一通孔2和第二通孔3，以及与所述第一通孔2轴线相互平行、且与所述第一通孔2和所述第二通孔3均连通的安装孔10。
蜗轮4设置在所述第一通孔2内，第一蜗杆5设置在所述第二通孔3内，与所述蜗轮4相匹配。螺旋弹簧6设置在所述第一蜗杆5的一端，离合齿轮7套设在所述第一蜗杆5的另一端。控制盘组件设置在所述第一通孔2的一端，且包括齿圈9。旋转角度控制装置，设置在所述安装孔10内。
如图2所示，为本公开旋转角度控制装置的一实施例的结构分解示意图。参考图2，并结合参考图3-图6，在一些实施例中，旋转角度控制装置，包括：芯轴12、传动齿轮13、离合套15、第二蜗杆18和外撑弹簧16。传动齿轮13套设在所述芯轴12上，且可与齿圈9啮合。离合套15套设在所述芯轴12上，且具有位于所述离合套15远离所述传动齿轮13一侧的端面上的第一轴向沉孔141。第二蜗杆18套设在所述芯轴12上，且具有位于所述第二蜗杆18邻近所述传动齿轮13一侧的端面上的第二轴向沉孔161。外撑弹簧16套设在所述芯轴12上，且具有与所述第一轴向沉孔141和所述第二轴向沉孔161的内孔面过盈配合的外圆面。第二蜗杆18可与所述离合齿轮7啮合。
在本实施例中，外撑弹簧16两端的外圆面分别与离合套15的第一轴向沉孔141和第二蜗杆18的第二轴向沉孔161的内孔面过盈配合。这样可使得外撑弹簧16的外圆面分别与第一轴向沉孔141和第二轴向沉孔161的内孔面组成摩擦副，从而形成扭簧离合器机构。
当第二蜗杆18固定，且离合套15具有在第一转动方向(例如逆时针)上的旋转趋势时，外撑弹簧16在摩擦力的作用下呈现往内缩方向变形的趋势，使得摩擦副的压力减小，从而使得离合套15能够克服摩擦力与第二蜗杆18相对转动。当所述第二蜗杆18固定，且离合套15具有在与第一转动方向相反的第二转动方向(例如顺时针)上的旋转趋势时，外撑弹簧16在摩擦力的作用下呈现向外撑开的趋势，使得摩擦副的压力随离合套15在第二转动方向上转动的扭矩增大而增大，从而使得离合套15受限于摩擦力而与外撑弹簧16和第二蜗杆18呈锁止状态而无相对转动。此时，外撑弹簧16在整个过程中充当单向离合作用。
相比于使用单向棘轮的相关技术，本实施例采用外撑弹簧16作为单向离合器，能够在圆周方向上无限等分，从而实现更快速的无极调节，避免相关技术的自动调整功能滞后的问题，进而保证行车安全。并且，在调整臂自动调整完成后，刹车间隙波动较小。
相比于采用抱紧弹簧(也称涨紧弹簧)的相关技术，本实施例的外撑弹簧在锁止时呈现外涨趋势，利用这种外涨趋势能够增加外撑弹簧与第一轴向沉孔和第二轴向沉孔的内孔面之间的摩擦力，从而实现自锁效果。换句话说，通过采用外撑弹簧与轴向沉孔的摩擦配合，相比于抱紧弹簧能够实现更大的锁止力，从而传递更大的扭矩，并避免打滑失效，进而保证调整臂的自动调整功能不会失效，保证行车安全。
参考图6，在一些实施例中，传动齿轮13与所述离合套15之间在周向上具有预设转动间隙α。传动齿轮13能够在第一转动方向上相对所述第二蜗杆18转动至抵顶所述离合套15时，带动所述离合套15沿所述第一转动方向同向转动，以通过所述离合套15的第一轴向沉孔141对所述外撑弹簧16的外圆面的摩擦力使所述外撑弹簧16转动而径向内缩，从而使所述离合套15相对于所述外撑弹簧16和所述第二蜗杆18转动打滑。
传动齿轮13还能够在与所述第一转动方向相反的第二转动方向上相对所述第二蜗杆18转动至抵顶所述离合套15时，带动所述离合套15沿所述第二转动方向同向转动，以通过所述离合套15的第一轴向沉孔141对所述外撑弹簧16的外圆面的摩擦力使所述外撑弹簧16转动而径向外撑，从而使所述离合套15与所述外撑弹簧16和所述第二蜗杆18相对锁止而同步转动。
在一些实施例中，外撑弹簧16为右旋外撑弹簧，所述第一转动方向为逆时针方向，所述第二转动方向为顺时针方向。举例来说，在汽车刹车动作时，齿圈9带动传 动齿轮13逆时针旋转。传动齿轮13旋转预设转动间隙α后，将带动离合套15逆时针旋转，外撑弹簧16在摩擦力的作用下呈现往内缩方向变形的趋势。离合套15的内孔面与外撑弹簧16的外圆面形成的摩擦副压力减小，摩擦力随之减小。离合套15克服摩擦力与第二蜗杆18相对转动，旋转角度为离合套15的旋转角度减去预设转动间隙α。
在汽车刹车动作完成后回位时，齿圈9带动传动齿轮13顺时针旋转。传动齿轮13旋转预设转动间隙α后，将带动离合套15顺时针旋转，外撑弹簧16在摩擦力的作用下呈现向外撑开方向变形的趋势。离合套15受限于摩擦力而与外撑弹簧16和第二蜗杆18锁止形成整体刚性结构。此时离合套15带动第二蜗杆18顺时针旋转，以消除超过设定值α°的超量旋转角。
参考图2、图3和图5，在一些实施例中，旋转角度控制装置还包括隔套17。隔套17位于所述外撑弹簧16与所述芯轴12之间，且所述隔套17的外圆直径小于所述外撑弹簧16呈现内缩趋势时的内孔尺寸。相应地，隔套17的外圆直径也小于所述外撑弹簧16过盈装配后的内孔尺寸。
位于外撑弹簧16与芯轴12之间的隔套17可使离合套15、外撑弹簧16及第二蜗杆18三者之间在锁止受力时保持同轴关系，对外撑弹簧16起到限位作用，降低外撑弹簧16切向过度变形而导致离合套15与第二蜗杆18之间错位的风险，从而有效提高产品使用寿命。
在一些实施例中，隔套17的轴向长度小于所述第一轴向沉孔141和所述第二轴向沉孔161的深度之和，以免对离合套15与第二蜗杆18之间的轴向位置造成限制。
参考图5和图6，在一些实施例中，传动齿轮13具有沿轴向延伸的插槽13a，所述离合套15远离所述第二蜗杆18的一端具有能够轴向插入所述插槽13a的插块15a。所述插块15a相对于所述插槽13a可转动，且所述插块15a的周向宽度小于所述插槽13a的周向宽度，以形成所述传动齿轮13与所述离合套15之间的预设转动间隙。
传动齿轮13的插槽13a和离合套15的插块15a的个数可以分别为一个或多个。可选地，插槽13a和插块15a的个数均为两个，两个插槽13a和两个插块15a的配合结构能够实现传动齿轮13和离合套15之间的更大承载能力，结构更加可靠。
在图6中，插槽13a具有第一侧壁171和第二侧壁172。当所述传动齿轮13顺时针旋转α°后，第一侧壁171与离合套15的插块15a的侧壁相抵，所述传动齿轮13带动所述离合套15顺时针旋转。然后，当所述传动齿轮13再逆时针旋转α°后，所 述第二侧壁172与所述离合套15的插块15a的侧壁相抵，所述传动齿轮13带动所述离合套15逆时针旋转。
参考图2-图6，在一些实施例中，旋转角度控制装置还包括回位扭簧14。回位扭簧14套设在所述芯轴12上，且位于所述传动齿轮13和所述离合套15之间。回位扭簧14两端的搭钩分别搭扣在所述插槽13a的侧壁和所述插块15a上，这样回位扭簧14能够使传动齿轮13与离合套15之间在不受外力的状态下维持在设定位置。
参考图3-图5和图8，在一些实施例中，旋转角度控制装置还包括：轴套19和间隙消除弹簧20。轴套19的一端与所述第二蜗杆18的端部相抵，另一端具有间隙消除腔19a。间隙消除弹簧20套装在所述间隙消除腔19a内。轴套19套在芯轴12，并通过卡扣与所述芯轴12连接。
在图8中，所述轴套19还具有与所述间隙消除腔19a贯通的第五通孔28，所述第五通孔28的内壁具有伸入所述间隙消除腔19a内的弹性卡块29，所述弹性卡块29朝向所述第五通孔28的一侧具有导向斜面31，所述芯轴12具有与所述弹性卡块29相匹配的卡槽30。
在装配时，芯轴12的前端依次穿过传动齿轮13、回位扭簧14、离合套15、外撑弹簧16、隔套17、第二蜗杆18和第五通孔28，使弹性卡块29嵌入芯轴12的卡槽30内，装配简单便利。为了使轴套19与芯轴12之间安装更牢固，轴套19可具有多个弹性卡块29。卡槽30可为环形卡槽。
参考图1和图7，在一些实施例中，自动间隙调整臂中的控制盘组件还可以包括盖板22和控制臂8。盖板22沿所述第一通孔2的轴向覆盖在所述第一通孔2的一侧，并遮挡所述安装孔10的孔口。该安装孔10可以为台阶孔，并由盖板22对安装孔10进行单侧遮挡，以方便安装孔10的加工，降低生产成本，实现防水防尘的效果。
控制臂8与所述齿圈9分别位于所述盖板22的两侧，且与所述齿圈9固定连接(例如铆接等)。控制臂8和所述齿圈9相对于所述盖板22可同步转动。前面提到的间隙消除弹簧20可以一端抵在间隙消除腔19a内，另一端抵在所述安装孔10内。
参考图1，在一些实施例中，自动间隙调整臂还包括：分别设置在所述第二通孔3沿轴向的两端的上封盖23和下封盖24。上封盖23和下封盖24能够对第二通孔3两端起到密封作用。另外，壳体1还具有与所述第二通孔3连通的第四通孔，所述自动间隙调整臂还包括位于所述第四通孔内的油嘴25和盖合在所述油嘴25上的防尘罩26。通过油嘴25可向壳体1内注入润滑油等，以减少磨损，提高性能，延长使用寿 命。
上述自动间隙调整臂的各实施例可应用于汽车制动器，因此本公开还提供了一种汽车制动器，包括前述任一种自动间隙调整臂。
至此，已经详细描述了本公开的各实施例。为了避免遮蔽本公开的构思，没有描述本领域所公知的一些细节。本领域技术人员根据上面的描述，完全可以明白如何实施这里公开的技术方案。
虽然已经通过示例对本公开的一些特定实施例进行了详细说明，但是本领域的技术人员应该理解，以上示例仅是为了进行说明，而不是为了限制本公开的范围。本领域的技术人员应该理解，可在不脱离本公开的范围和精神的情况下，对以上实施例进行修改或者对部分技术特征进行等同替换。本公开的范围由所附权利要求来限定。

Claims (15)

  1. 一种旋转角度控制装置，包括：
    芯轴(12)；
    传动齿轮(13)，套设在所述芯轴(12)上；
    离合套(15)，套设在所述芯轴(12)上，且具有位于所述离合套(15)远离所述传动齿轮(13)一侧的端面上的第一轴向沉孔(141)；
    第二蜗杆(18)，套设在所述芯轴(12)上，且具有位于所述第二蜗杆(18)邻近所述传动齿轮(13)一侧的端面上的第二轴向沉孔(161)；和
    外撑弹簧(16)，套设在所述芯轴(12)上，且具有与所述第一轴向沉孔(141)和所述第二轴向沉孔(161)的内孔面过盈配合的外圆面。
  2. 根据权利要求1所述的旋转角度控制装置，其中，所述传动齿轮(13)与所述离合套(15)之间在周向上具有预设转动间隙，所述传动齿轮(13)被配置为在第一转动方向上相对所述第二蜗杆(18)转动至抵顶所述离合套(15)时，带动所述离合套(15)沿所述第一转动方向同向转动，以通过所述离合套(15)的第一轴向沉孔(141)对所述外撑弹簧(16)的外圆面的摩擦力使所述外撑弹簧(16)转动而径向内缩，从而使所述离合套(15)相对于所述外撑弹簧(16)和所述第二蜗杆(18)转动打滑，以及在与所述第一转动方向相反的第二转动方向上相对所述第二蜗杆(18)转动至抵顶所述离合套(15)时，带动所述离合套(15)沿所述第二转动方向同向转动，以通过所述离合套(15)的第一轴向沉孔(141)对所述外撑弹簧(16)的外圆面的摩擦力使所述外撑弹簧(16)转动而径向外撑，从而使所述离合套(15)与所述外撑弹簧(16)和所述第二蜗杆(18)相对锁止而同步转动。
  3. 根据权利要求2所述的旋转角度控制装置，其中，所述传动齿轮(13)具有沿轴向延伸的插槽(13a)，所述离合套(15)远离所述第二蜗杆(18)的一端具有能够轴向插入所述插槽(13a)的插块(15a)，所述插块(15a)相对于所述插槽(13a)可转动，且所述插块(15a)的周向宽度小于所述插槽(13a)的周向宽度，以形成所述传动齿轮(13)与所述离合套(15)之间的预设转动间隙。
  4. 根据权利要求3所述的旋转角度控制装置，还包括：
    回位扭簧(14)，套设在所述芯轴(12)上，且位于所述传动齿轮(13)和所述离合套(15)之间，其中，所述回位扭簧(14)两端的搭钩分别搭扣在所述插槽(13a) 的侧壁和所述插块(15a)上。
  5. 根据权利要求1所述的旋转角度控制装置，其中，所述外撑弹簧(16)为右旋外撑弹簧，所述第一转动方向为逆时针方向，所述第二转动方向为顺时针方向。
  6. 根据权利要求1所述的旋转角度控制装置，还包括：
    隔套(17)，位于所述外撑弹簧(16)与所述芯轴(12)之间，且所述隔套(17)的外圆直径小于所述外撑弹簧(16)呈现内缩趋势时的内孔尺寸，所述隔套(17)的外圆直径也小于所述外撑弹簧(16)过盈装配后的内孔尺寸。
  7. 根据权利要求6所述的旋转角度控制装置，其中，所述隔套(17)的轴向长度小于所述第一轴向沉孔(141)和所述第二轴向沉孔(161)的深度之和。
  8. 根据权利要求1所述的旋转角度控制装置，还包括：
    轴套(19)，一端与所述第二蜗杆(18)的端部相抵，另一端具有间隙消除腔(19a)；和
    间隙消除弹簧(20)，套装在所述间隙消除腔(19a)内，
    其中，所述轴套(19)套在所述芯轴(12)上，并通过卡扣与所述芯轴(12)连接。
  9. 根据权利要求8所述的旋转角度控制装置，其中，所述轴套(19)还具有与所述间隙消除腔(19a)贯通的第五通孔(28)，所述第五通孔(28)的内壁具有伸入所述间隙消除腔(19a)内的弹性卡块(29)，所述弹性卡块(29)朝向所述第五通孔(28)的一侧具有导向斜面(31)，所述芯轴(12)(12)具有与所述弹性卡块(29)相匹配的卡槽(30)。
  10. 一种自动间隙调整臂，包括：
    壳体(1)，具有相互连通的第一通孔(2)和第二通孔(3)，以及与所述第一通孔(2)轴线相互平行、且与所述第一通孔(2)和所述第二通孔(3)均连通的安装孔(10)；
    蜗轮(4)，设置在所述第一通孔(2)内；
    第一蜗杆(5)，设置在所述第二通孔(3)内，与所述蜗轮(4)相匹配；
    螺旋弹簧(6)，设置在所述第一蜗杆(5)的一端；
    离合齿轮(7)，套设在所述第一蜗杆(5)的另一端；
    控制盘组件，设置在所述第一通孔(2)的一端，且包括齿圈(9)；和
    权利要求1～9任一所述的旋转角度控制装置，设置在所述安装孔(10)内，
    其中，所述旋转角度控制装置中的传动齿轮(13)与所述齿圈(9)啮合，所述旋转角度控制装置中的第二蜗杆(18)与所述离合齿轮(7)啮合。
  11. 根据权利要求10所述的自动间隙调整臂，其中，所述控制盘组件还包括：
    盖板(22)，沿所述第一通孔(2)的轴向覆盖在所述第一通孔(2)的一侧，并遮挡所述安装孔(10)的孔口；
    控制臂(8)，与所述齿圈(9)分别位于所述盖板(22)的两侧，且与所述齿圈(9)固定连接，
    其中，所述控制臂(8)和所述齿圈(9)相对于所述盖板(22)可同步转动。
  12. 根据权利要求10所述的自动间隙调整臂，其中，所述安装孔(10)为盲孔，所述旋转角度控制装置还包括轴套(19)和间隙消除弹簧(20)，所述轴套(19)套在所述第二蜗杆(18)上，并通过卡扣与所述芯轴(12)连接，所述轴套(19)的一端与所述第二蜗杆(18)的端部相抵，另一端具有间隙消除腔(19a)，所述间隙消除弹簧(20)一端抵在所述间隙消除腔(19a)内，另一端抵在所述安装孔(10)内。
  13. 根据权利要求10所述的自动间隙调整臂，还包括：
    上封盖(23)和下封盖(24)，分别设置在所述第二通孔(3)沿轴向的两端。
  14. 根据权利要求10所述的自动间隙调整臂，其中，所述壳体还具有与所述第二通孔(3)连通的第四通孔，所述自动间隙调整臂还包括位于所述第四通孔内的油嘴(25)和盖合在所述油嘴(25)上的防尘罩(26)。
  15. 一种汽车制动器，包括权利要求10～14任一所述的自动间隙调整臂。
PCT/CN2020/088459 2019-11-04 2020-04-30 旋转角度控制装置、自动间隙调整臂及汽车制动器 WO2021088340A1 (zh)

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EP3848605A1 (en) 2021-07-14
EP3848605A4 (en) 2022-03-30
RU2770333C1 (ru) 2022-04-15
JP7209827B2 (ja) 2023-01-20
CN110701223A (zh) 2020-01-17
JP2022532266A (ja) 2022-07-14
AU2020294274A1 (en) 2021-05-20
EP3848605B1 (en) 2024-02-28
AU2020294274B2 (en) 2023-02-09

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