WO2024078097A1 - 带间隙调整功能的液压制动缸及液压制动夹钳装置 - Google Patents

带间隙调整功能的液压制动缸及液压制动夹钳装置 Download PDF

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Publication number
WO2024078097A1
WO2024078097A1 PCT/CN2023/109795 CN2023109795W WO2024078097A1 WO 2024078097 A1 WO2024078097 A1 WO 2024078097A1 CN 2023109795 W CN2023109795 W CN 2023109795W WO 2024078097 A1 WO2024078097 A1 WO 2024078097A1
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WO
WIPO (PCT)
Prior art keywords
piston
cylinder
transmission shaft
hydraulic brake
cylinder body
Prior art date
Application number
PCT/CN2023/109795
Other languages
English (en)
French (fr)
Inventor
王龙泉
刘德学
李�杰
孙博
沈铭乾
吴世应
李金花
Original Assignee
中车制动系统有限公司
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 中车制动系统有限公司 filed Critical 中车制动系统有限公司
Publication of WO2024078097A1 publication Critical patent/WO2024078097A1/zh

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Classifications

    • 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
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • 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
    • F16D65/72—Slack adjusters hydraulic
    • 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
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
    • 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
    • F16D2125/02—Fluid-pressure mechanisms
    • F16D2125/08—Seals, e.g. piston seals
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present application belongs to the technical field of rail transit vehicle braking, and in particular relates to a hydraulic brake cylinder and a hydraulic brake caliper device with a clearance adjustment function.
  • the defects of the active hydraulic brake cylinder without clearance adjustment function are: in the relief state, the brake pad of the hydraulic brake caliper without automatic reset function can move along the brake pad installation axis, and this movement may cause the brake pad and the brake disc to be non-parallel, resulting in adverse conditions such as eccentric wear of the brake pad, metal inlay between the brake disc and the brake pad, and sparks between the two during line operation; and when the oil pressure is first unloaded, the brake pad will be close to or loosely attached to the brake disc, increasing the friction and wear between the brake pad and the brake disc; and the hydraulic brake caliper with automatic reset function becomes thinner as the brake pad wears, resulting in a longer braking response time and an excessive braking distance, affecting driving safety.
  • Chinese invention patent CN115978113A discloses an active hydraulic brake caliper with automatic brake pad clearance adjustment function, which uses a return spring and a rectangular spring to cooperate and automatically adjust the clearance. A set gap is generated to achieve the separation of the brake pad and the brake disc after the brake is released, but there are still problems such as complex structure of the hydraulic brake cylinder and high requirements on spring performance.
  • the purpose of the present application is to solve one of the above-mentioned technical problems and to provide a hydraulic brake cylinder and a hydraulic brake caliper device with a clearance adjustment function.
  • a first aspect of the present application provides a hydraulic brake cylinder with a clearance adjustment function, comprising:
  • the oil cylinder body has an oil cylinder cavity inside, one end of the oil cylinder body in the axial direction is provided with an opening, and a stop sleeve is installed at the opening;
  • a piston is disposed in the oil cylinder cavity, the piston is coaxially arranged with the main axis of the oil cylinder body, the piston radially closes the oil cylinder cavity, and can move relative to the oil cylinder cavity; the piston divides the oil cylinder cavity into a first oil chamber and a second oil chamber;
  • a transmission shaft is disposed in the second oil chamber, one end of the transmission shaft is fixedly connected to the piston, and one end of the transmission shaft away from the piston extends out of the cylinder body through the stop sleeve;
  • a first oil circuit which is provided on the oil cylinder body and communicated with the first oil chamber;
  • a second oil circuit which is provided on the cylinder body and communicated with the second oil chamber;
  • the clearance adjustment ring is arranged on the transmission shaft.
  • the clearance adjustment ring can move axially in the second oil chamber along with the transmission shaft, and can be blocked and limited by the stop sleeve to produce axial elastic deformation.
  • a plurality of ear seats protruding in the radial direction of the cylinder body are arranged along the inner wall of the cylinder body at the second oil chamber, and the plurality of ear seats are evenly distributed circumferentially on the inner wall of the cylinder body; the clearance adjustment ring is arranged between the ear seat and the stop sleeve, and can be blocked and limited by the ear seat.
  • the gap adjustment ring is interference connected to the transmission On the driving shaft, the clearance adjustment ring has radial elastic force to generate friction between the clearance adjustment ring and the transmission shaft.
  • the piston thrust generated by the hydraulic pressure loaded during braking is the first piston thrust
  • the piston thrust generated by the hydraulic pressure loaded during brake release is the second piston thrust
  • the friction force between the clearance adjustment ring and the transmission shaft is less than the first piston thrust and greater than the second piston thrust
  • the movable distance of the gap adjustment ring between the ear seat and the stop sleeve is the rated withdrawal distance ⁇ of the gap adjustment ring, ⁇ +1.5mm, wherein ⁇ is the gate gap.
  • a plurality of sealing grooves are provided on the inner wall of the cylinder body between the piston and the cylinder body, and a sealing component is installed in each sealing groove.
  • the sealing component is used to achieve sealing between the cylinder body and the piston and/or guide the piston.
  • a cylinder bushing hole is provided on the cylinder body, and a cylinder bushing is interference-connected in the cylinder bushing hole; an air passage is provided on the cylinder body, and the air passage connects the outside atmosphere with the cylinder bushing hole.
  • one end of the transmission shaft extending out of the cylinder body is connected to a cover body component, a cover body bushing hole is opened on the cover body component, and a cover body bushing is interference-connected in the cover body bushing hole.
  • a first sealing member for sealing is provided between the stop sleeve and the cylinder body.
  • a second sealing member for sealing and a guide ring for guiding the transmission shaft are provided between the stop sleeve and the transmission shaft.
  • a dust cover is provided between the cylinder body and the protruding end of the transmission shaft, and one end of the dust cover is connected to the outer wall of the cylinder body, and the other end is connected to the transmission shaft.
  • a second aspect of the present application provides a hydraulic brake caliper device, comprising a hydraulic brake cylinder as described in any one of the above items, and a brake caliper lever mounted on the hydraulic brake cylinder.
  • the hydraulic brake cylinder provided in at least one embodiment of the present application realizes an automatic clearance adjustment function through the cooperation between the clearance adjustment ring and the stop sleeve, and can adjust the clearance between the brake pad and the brake disc; during the braking process, when the brake pad is worn, the piston movement stroke in the hydraulic brake cylinder increases, which can quickly compensate for the increase in braking stroke caused by the wear of the brake pad and the brake disc or other factors, and the braking response is rapid, thereby improving the braking sensitivity and driving safety;
  • the hydraulic brake cylinder provided in at least one embodiment of the present application fixes the movable distance of the clearance adjustment ring between the ear seat and the stop sleeve through the limiting effect of the ear seat and the stop sleeve on the clearance adjustment ring, and compensates for the wear clearance during the braking process when the wear clearance first appears.
  • the moving distance of the clearance adjustment ring is still the rated retraction distance, so that the wear clearance does not need to be compensated again during the next braking process; in addition, it can also prevent the clearance adjustment ring from axially moving along the transmission shaft and falling out during the working process;
  • the hydraulic brake cylinder provided by at least one embodiment of the present application eliminates the traditional structure of butterfly spring energy storage and relief and oil filling braking, and can realize the braking, brake relief and clearance compensation functions through the oil pressure and oil pressure size on both sides of the piston.
  • the overall structure is simple, with fewer parts and a high degree of integration and modularization.
  • the hydraulic brake cylinder provided in at least one embodiment of the present application can adjust the position of the clearance adjustment ring on the transmission shaft by changing the oil pressure in the oil chambers on both sides of the piston, thereby adjusting the brake pad support opening of the brake caliper mechanism and setting the brake pad clearance, thereby facilitating brake pad replacement and later repair and maintenance;
  • the hydraulic brake caliper device provided in at least one embodiment of the present application has a hydraulic brake cylinder with a clearance adjustment function. Braking, brake relief and automatic clearance adjustment can be achieved by changing the oil pressure on both sides of the piston, which can achieve a quick braking response, improve braking sensitivity and driving safety.
  • FIG1 is a structural schematic diagram 1 of a hydraulic brake cylinder provided in an embodiment of the present application.
  • FIG2 is a second structural schematic diagram of a hydraulic brake cylinder provided in an embodiment of the present application.
  • FIG3 is a cross-sectional view of the hydraulic brake cylinder provided in an embodiment of the present application along the axial direction;
  • FIG4 is a partial enlarged view of the portion A in FIG3 ;
  • FIG5 is a third structural diagram of a hydraulic brake cylinder in an embodiment of the present application.
  • FIG6 is an exploded view of the hydraulic brake cylinder in FIG5 ;
  • FIG7 is a schematic structural diagram of a cylinder body in an embodiment of the present application.
  • FIG8 is a first structural schematic diagram of a hydraulic brake caliper device provided in an embodiment of the present application.
  • FIG9 is a second structural schematic diagram of the hydraulic brake caliper device provided in an embodiment of the present application.
  • first and second are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, features defined as “first” and “second” may explicitly or implicitly include one or more of the features.
  • the terms “installed”, “connected”, and “connected” should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two components.
  • installed e.g., it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two components.
  • the first aspect of the present application provides a hydraulic brake cylinder with a clearance adjustment function, the hydraulic brake cylinder comprising a cylinder body 1, the cylinder body 1 having a cylinder cavity 11 therein, an opening 19 (as shown in FIG. 7 ) being provided at one end of the cylinder body 1 in the axial direction, and a stopper sleeve 3 being installed at the opening 19.
  • the stopper sleeve 3 is connected to the cylinder body 1 as a whole through a threaded connection, and is in a sealed configuration to prevent oil leakage.
  • a piston 2 is provided in the oil cylinder cavity 11, the piston 2 is coaxially arranged with the main axis of the oil cylinder body 1, the piston 2 radially closes the oil cylinder cavity 11, and can move relative to the oil cylinder cavity 11; the piston 2 divides the oil cylinder cavity into a first oil chamber 1101 and a second oil chamber 1102. It can be understood that during the braking or brake release process, with the axial movement of the piston 2, the volumes of the first oil chamber 1101 and the second oil chamber 1102 will change.
  • a transmission shaft 4 is provided in the second oil chamber 1102 for transmitting the braking force, and one end of the transmission shaft 4 is fixedly connected to the piston 2.
  • the end of the transmission shaft 4 away from the piston 2 extends out of the cylinder body 1 through the stop sleeve 3.
  • the transmission shaft 4 is connected to the piston 2 through a threaded connection.
  • the transmission shaft 4 and the stop sleeve 3 are sealed to prevent oil leakage.
  • the cylinder body 1 is provided with a first oil circuit 12 connected with the first oil chamber 1101, which is used to load hydraulic pressure to push the piston 2 to move toward the stop sleeve 3 for braking, and a second oil circuit 13 connected with the second oil chamber 1102, which is used to load hydraulic pressure to push the piston 2 to move away from the stop sleeve 3 for braking relief.
  • a clearance adjustment ring 5 is provided on the transmission shaft 4.
  • the clearance adjustment ring 5 can move axially in the second oil chamber 1102 along with the transmission shaft 4, and can be stopped and limited by the stop sleeve 3 to generate axial elastic deformation.
  • the hydraulic brake cylinder has an automatic clearance adjustment function.
  • the piston 2 drives the transmission shaft 4 to move axially toward the opening 19, so that the transmission shaft 4 moves out of the cylinder body 1.
  • the clearance adjustment ring 5 moves
  • the stopper sleeve 3 is in contact with the clearance adjustment ring 5
  • the clearance adjustment ring 5 is elastically deformed, so that the transmission shaft 4 can continue to extend outward for a distance until the brake pad clamps the brake disc.
  • the clearance adjustment ring 5 is made of high-strength high-stress elastic rubber. During braking, the clearance adjustment ring 5 can be kept at the blocking limit position after being blocked by the stop sleeve 3. Under the push of the hydraulic pressure in the first oil chamber 1101, within the deformation range of the clearance adjustment ring 5, the transmission shaft 4 can continue to extend.
  • the clearance adjustment ring 5 is interference-connected to the transmission shaft 4. Specifically, the inner hole surface of the clearance adjustment ring 5 is interference-fitted with the outer cylindrical surface of the transmission shaft 4, and there is friction between the clearance adjustment ring 5 and the transmission shaft 4. At the same time, since the clearance adjustment ring 5 itself has radial elastic force, it is not easy to slide relative to the transmission shaft 4. However, it can be understood that when there is a wear gap, when the clearance adjustment ring 5 is limited by the stop sleeve 3, the brake pad has not clamped the brake disc. Since the braking force during the braking process is very large, it is usually greater than the friction between the clearance adjustment ring 5 and the transmission shaft 4, the transmission shaft 4 will move relative to the clearance adjustment ring 5 until the wear gap is compensated.
  • a plurality of ear seats 14 protruding in the radial direction of the cylinder body 1 are arranged along the inner wall of the cylinder body 1 at the second oil chamber 1102, and the plurality of ear seats 14 are evenly distributed circumferentially on the inner wall of the cylinder body 1.
  • three ear seats 14 are evenly arranged circumferentially on the inner wall of the cylinder body 1.
  • the clearance adjustment ring 5 is arranged between the ear seat 14 and the stop sleeve 3, and the clearance adjustment ring 5 can be blocked and limited by the ear seat 4 when the brake is released.
  • the ear seat 14 and the stop sleeve 3 are used to limit the movement of the clearance adjustment ring 5, and the braking, braking relief and clearance compensation functions can be realized through the difference in hydraulic pressure in the oil chambers on both sides of the piston 2.
  • the position of the clearance adjustment ring 5 on the transmission shaft 4 is adjusted, and then the brake pad support opening of the brake caliper mechanism is adjusted, and the clearance of the brake pad is set, which is convenient for the maintenance and replacement of the brake pad; it can also prevent the clearance adjustment ring 5 from axially moving along the transmission shaft 4 and falling out during operation.
  • the piston thrust generated by the hydraulic pressure loaded during the braking process is the first piston thrust
  • the piston thrust generated by the hydraulic pressure loaded during the brake release process is the second piston thrust.
  • the friction between the clearance adjustment ring 5 and the transmission shaft 4 is less than the first piston thrust and greater than the second piston thrust.
  • the movable distance of the gap adjustment ring 5 between the ear seat 14 and the stop sleeve 3 is the rated withdrawal distance ⁇ of the gap adjustment ring 5.
  • the rated withdrawal distance ⁇ is the movable distance of the gap adjustment ring 5 between the ear seat 14 and the stop sleeve 3 when the gap adjustment ring 5 is not deformed.
  • the distance between the ear seat 14 and the stop sleeve 3 is d
  • the length of the gap adjustment ring 5 in the natural state L
  • the rated withdrawal distance ⁇ d-L.
  • the moving distance (rated withdrawal distance ⁇ ) of the clearance adjustment ring 5 during each brake relief process is fixed, and the wear clearance is compensated during the braking process when the wear clearance first appears.
  • the moving distance of the clearance adjustment ring 5 is still the rated withdrawal distance ⁇ , so that the wear clearance does not need to be compensated again during the next braking process.
  • the clearance adjustment ring 5 and the transmission shaft 4 move relative to each other, so that the position of the clearance adjustment ring 5 on the transmission shaft 4 moves by g toward the direction close to the piston 2.
  • the piston moves by g toward the direction close to the opening 19 relative to the position before braking. Therefore, the wear gap g has been compensated in this braking relief process.
  • the transmission shaft 4 No additional g movement is required to achieve clamping braking.
  • the spacing between the ear seat 14 and the stop sleeve 3 and the rated back distance ⁇ of the clearance adjustment ring 5 can be set according to the requirements of the brake pad clearance. In some embodiments, when the brake pad clearance is ⁇ , the rated back distance ⁇ of the clearance adjustment ring 5 is ⁇ +1.5mm.
  • the brake pad clearance refers to the distance between the brake pad and the brake disc in the relieved state.
  • the maximum movement distance of the piston 2 is the distance between the end of the piston 2 away from the first oil chamber and the ear seat 14 in the brake release state, and the maximum adjustment amount of the hydraulic brake cylinder is the same as the maximum movement distance of the piston 2; the one-time adjustment amount of the hydraulic brake cylinder is the same as the brake pad clearance, but does not exceed the maximum adjustment amount of the hydraulic brake cylinder.
  • a plurality of sealing grooves 15 are provided on the inner wall of the cylinder body between the outer cylindrical surface of the piston 2 and the cylinder body 1, and a sealing component 16 is installed in each sealing groove 15, and the sealing component 16 is used to achieve the seal between the cylinder body 1 and the piston 2 and/or guide the piston 2.
  • two sealing grooves 15 are provided on the cylinder body 1, which are a guide ring installation groove and a sealing ring installation groove, respectively.
  • the sealing component installed in the guide ring installation groove is a guide ring
  • the sealing component installed in the sealing ring installation groove is an O-ring.
  • the sealing groove 15 is always located between the cylinder cavity 11 and the piston 2, that is, the sealing groove 15 is always located between the inner wall surface of the cylinder body 1 and the outer cylindrical surface of the piston 2, so as to realize the sealing and guiding function between the piston 2 and the cylinder body 1.
  • a plurality of sealing grooves 15 are provided on the outer cylindrical surface of the piston 2.
  • Each sealing groove 15 is equipped with a sealing component 16, which is used to achieve sealing between the cylinder body 1 and the piston 2 and/or guide the piston 2.
  • two sealing grooves 15 are provided on the outer cylindrical surface of the piston 2, namely, a guide ring installation groove and a sealing ring installation groove.
  • the sealing component installed in the guide ring installation groove is a guide ring
  • the sealing component installed in the sealing ring installation groove is an O-ring.
  • the sealing groove 15 is always located between the inner wall surface of the cylinder body 1 and the outer cylindrical surface of the piston 2.
  • a cylinder bushing hole 16 is provided on the cylinder body 1, and a cylinder bushing 17 is interference-connected in the cylinder bushing hole 16.
  • the cylinder bushing 17 is connected to the cylinder body 1 as a whole by being pressed into the cylinder bushing hole 16, and the cylinder bushing 17 is interference-fitted with the cylinder bushing hole 16, and is used to be connected to the brake caliper lever.
  • two pairs of cylinder bushings 17 and cylinder bushing holes 16 are provided, and the two cylinder bushing holes 16 are vertically coaxial and symmetrically arranged on the cylinder body 1.
  • the cylinder liner hole 16 can be a cylindrical hole or a cylindrical stepped hole, and correspondingly, the cylinder liner 17 can be a cylindrical structure or a flanged stepped cylindrical structure. It is understandable that the shape of the cylinder liner hole 16 matches the structure of the cylinder liner 17.
  • an air passage 18 is provided on the cylinder body 1, and the air passage 18 connects the cylinder bushing hole 16 with the outside atmosphere.
  • the air in the cylinder bushing hole 16 is discharged through the air passage 18.
  • the air passage 18 is a circular small-diameter channel.
  • the end of the transmission shaft 4 extending out of the oil cylinder body 1 is connected to a cover body component 6 for transmitting the braking force, and a cover body bushing hole 61 is provided on the cover body component 6, and a cover body bushing 62 is interference-connected in the cover body bushing hole 61.
  • the transmission shaft 4 and the cover body component 6 are fastened by bolts; the cover body bushing 62 is connected to the cover body component 6 by being pressed into the cover body bushing hole 61, and the cover body bushing 62 is interference-fitted with the cover body bushing hole 61, and is used to connect with the brake caliper lever.
  • the cover body Two pairs of bushings 62 and cover bushing holes 61 are provided, and the two cover bushing holes 61 are vertically coaxial and symmetrically arranged on the cover component 6 .
  • the cover bushing hole 61 can be a cylindrical hole or a cylindrical stepped hole, and correspondingly, the cover bushing 62 can be a cylindrical structure or a flanged stepped cylindrical structure. It can be understood that the shape of the cover bushing hole 61 matches the structure of the cover bushing 62.
  • a first sealing member 7 is provided between the stop sleeve 3 and the oil cylinder body 1 and on one side close to the oil cylinder cavity, for achieving a seal between the stop sleeve 3 and the oil cylinder body 1 to prevent oil leakage during braking and brake release.
  • the first sealing member 7 is an O-ring.
  • a guide ring 9 for guiding and a second sealing member 8 for sealing are provided between the stop sleeve 3 and the transmission shaft 4.
  • the second sealing member 8 is an O-ring.
  • a dustproof sealing ring may be provided at one end of the stop sleeve 3 close to the cover body component 6 to prevent external dust and water stains from entering and contaminating the internal movement mechanism.
  • a dust cover 10 is provided between the cylinder body 1 and the protruding end of the transmission shaft 4.
  • One end of the dust cover 10 is connected to the outer wall of the cylinder body 1, and the other end is connected to the transmission shaft 4 or the cover body 6, which is used to further prevent external dust and water stains from entering and contaminating the internal moving mechanism.
  • the transmission shaft 4 will overcome the friction force under the action of the first piston thrust and move relative to the clearance adjustment ring 5, and the piston 2 and the transmission shaft 4 continue to move forward until the brake pad and the brake disc are pressed tightly to generate braking force.
  • the wear clearance is compensated by the movement of the transmission shaft 4 relative to the clearance adjustment ring 5.
  • the transmission shaft 4 only needs to move axially by the rated back-off distance ⁇ to make the brake pad stick to the brake disc without the need for clearance compensation again.
  • the first piston thrust generated by the hydraulic pressure in the first oil chamber 1101 is quickly withdrawn, and hydraulic oil is added to the second oil chamber 1102 through the second oil circuit 13.
  • the hydraulic pressure in the second oil chamber 1102 generates a piston thrust on the piston 2 in the cylinder cavity 11, pushing the piston 2, the transmission shaft 4 and the clearance adjustment ring 5 to move away from the stop sleeve 3.
  • the clearance adjustment ring 5 is tightly attached to the ear seat 14. The clearance adjustment ring 5 cannot move anymore due to the obstruction of the ear seat 14, and the piston 2 and the transmission shaft 4 also stop moving.
  • the distance between the clearance adjustment ring 5 and the stop sleeve 3 is maintained at the rated withdrawal distance ⁇ , that is, it reaches the set position, and the brake pad also reaches the position of maintaining a normal gap with the brake disc, and the clearance compensation action is completed.
  • the second piston thrust F generated by the hydraulic pressure loaded in the second oil chamber 1102 when the brake is released should be less than the friction force F S between the clearance adjustment ring 5 and the transmission shaft 4, that is, F ⁇ F S.
  • a second aspect of the present application provides a hydraulic brake caliper device, as shown in FIGS. 8 and 9 , comprising:
  • the hydraulic brake cylinder 100 described in any of the above embodiments further includes a brake caliper lever 200 installed on the hydraulic brake cylinder 100, and a pair of brake pad holders 300 for installing brake pads are installed on the brake caliper lever 200.
  • the two brake pad holders 300 are arranged opposite to each other and can approach or move away from each other under the action of the hydraulic brake cylinder 100.
  • the brake caliper lever 200 is hinged with the cylinder bushing 17 and the cover bushing 62 by bolts, and then installed on the hydraulic brake cylinder 100.
  • Brake pads are respectively installed on the two brake pad holders 300.
  • the two brake pads are opposite to each other and clamp the brake disc during the braking process.
  • the specific structure and installation method of the brake caliper lever 200, the brake pad holder 300 and the brake pad are prior arts, and are not described in detail in this application.
  • the hydraulic brake caliper device provided in the above embodiments of the present application whose hydraulic brake cylinder has a clearance adjustment function, can realize braking, brake relief and automatic clearance adjustment by changing the oil pressure on both sides of the piston 2, which can achieve the effect of rapid braking response, improved braking sensitivity and driving safety.

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  • General Engineering & Computer Science (AREA)
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Abstract

一种带间隙调整功能的液压制动缸，包括油缸缸体（1）以及设于油缸缸体内的活塞（2）、传动轴（4）和间隙调节环（5），其中油缸缸体轴向方向的一端设置有开口（19），开口处安装有止挡套（3），传动轴一端与活塞连接，远离活塞的一端经止挡套伸出至油缸缸体外；传动轴上设置有间隙调节环，间隙调节环能随传动轴在第二油腔（1102）内做轴向运动，且能够被止挡套阻挡限位，产生轴向变形；该装置通过改变活塞两侧的油压及油压大小即可实现制动、制动缓解及间隙调整功能，结构简单，提高了制动的灵敏度和行车的安全性；还涉及一种液压制动夹钳装置。

Description

带间隙调整功能的液压制动缸及液压制动夹钳装置
本申请要求在2023年05月30日提交中国专利局、申请号为202310627748.3、申请名称为“一种带间隙调整功能的主动式液压制动缸”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请属于轨道交通车辆制动技术领域，尤其涉及一种带间隙调整功能的液压制动缸及液压制动夹钳装置。
背景技术
随着轨道交通技术的快速发展，轨道车辆种类愈发增多，车辆转向架向轻量化及紧凑化的方向发展。相比气动制动系统，液压制动系统具有结构紧凑、体积小、重量轻、制动功率大等优点，因而在低地板有轨电车、跨座式单轨车辆、磁浮列车等轨道车辆上应用。
在现有的液压基础制动技术中，不具有间隙调节功能的主动式液压制动缸的缺陷在于：在缓解状态下，不具有自动复位功能的液压制动夹钳的闸片可以沿闸片安装轴窜动，这种窜动可能会导致闸片与制动盘不平行对齐，在线路运行过程中发生闸片偏磨、制动盘闸片间金属镶嵌、两者之间产生火花等不良状况；且刚开始油压卸载时，闸片会贴靠或虚贴于制动盘，增加闸片与制动盘的摩擦磨损；而具有自动复位功能的液压制动夹钳随着闸片的磨损厚度变薄，导致制动响应时间变长、制动距离超标影响行车安全。
对于能实现间隙调节功能的主动式液压制动缸而言，现有技术中也有一些设计，如中国发明专利CN115978113A公开了一种带闸片间隙自动调整功能的主动式液压制动夹钳，使用了利用了回位弹簧和矩形弹簧配合动作自动 产生设定间隙，实现了在制动缓解后闸片和制动盘的分离，但仍存在液压制动缸结构复杂，对弹簧性能要求较高的问题。
发明内容
本申请的目的在于解决上述技术问题之一，提供一种带间隙调整功能的液压制动缸及液压制动夹钳装置。
本申请第一方面提供一种带间隙调整功能的液压制动缸，包括：
油缸缸体，其内部具有油缸腔体，所述油缸缸体轴向方向的一端设置有开口，开口处安装有止挡套；
活塞，其设于所述油缸腔体内，所述活塞与所述油缸缸体的主轴线同轴设置，所述活塞沿径向封闭所述油缸腔体，且可相对所述油缸腔体运动；所述活塞将所述油缸腔体分为第一油腔与第二油腔；
传动轴，其设于所述第二油腔内，所述传动轴一端与所述活塞固定连接，所述传动轴远离所述活塞的一端经所述止挡套伸出至所述油缸缸体外；
第一油路，其设于所述油缸缸体上且与所述第一油腔连通；
第二油路，其设于所述油缸缸体上且与所述第二油腔连通；
间隙调节环，其设于所述传动轴上，所述间隙调节环能随所述传动轴在所述第二油腔内做轴向运动，且能够被所述止挡套阻挡限位，产生轴向弹性变形。
在本申请第一方面的一些实施例中，沿所述第二油腔处的所述油缸缸体的内壁设置有多个向所述油缸缸体径向方向突出的耳座，多个所述耳座周向均匀分布在所述油缸缸体的内壁上；所述间隙调节环设置在所述耳座与所述止挡套之间，且能够被所述耳座阻挡限位。
在本申请第一方面的一些实施例中，所述间隙调节环过盈连接在所述传 动轴上，所述间隙调节环具有径向弹力以在所述间隙调节环和所述传动轴之间产生摩擦力。
在本申请第一方面的一些实施例中，制动过程中加载的液压所产生的活塞推力为第一活塞推力，制动缓解过程中加载的液压所产生的活塞推力为第二活塞推力，所述间隙调节环与所述传动轴之间的摩擦力小于所述第一活塞推力且大于所述第二活塞推力。
在本申请第一方面的一些实施例中，所述间隙调节环在所述耳座与所述止挡套之间的可移动距离为所述间隙调节环的额定退距λ，λ≈ζ+1.5mm，其中，ζ为闸片间隙。
在本申请第一方面的一些实施例中，所述活塞与所述油缸缸体之间的缸体内壁上开设有多个密封沟槽，每一密封沟槽内均安装有密封元器件，所述密封元器件用于实现所述油缸缸体与所述活塞之间的密封和/或对所述活塞进行导向。
在本申请第一方面的一些实施例中，所述油缸缸体上开设有油缸衬套孔，所述油缸衬套孔内过盈连接有油缸衬套；所述油缸缸体上开设有空气通路，所述空气通路连通外界大气与所述油缸衬套孔。
在本申请第一方面的一些实施例中，所述传动轴伸出所述油缸缸体的一端连接有盖体组成，所述盖体组成上开设有盖体衬套孔，所述盖体衬套孔内过盈连接有盖体衬套。
在本申请第一方面的一些实施例中，所述止挡套与所述油缸缸体之间设置有用于密封的第一密封件。
在本申请第一方面的一些实施例中，所述止挡套与传动轴之间设置有用于密封的第二密封件和用于对所述传动轴导向的导向环。
在本申请第一方面的一些实施例中，所述油缸缸体与所述传动轴的伸出端之间设置有防尘罩，所述防尘罩一端连接在所述油缸缸体的外壁上，另一端连接在所述传动轴上。
本申请第二方面提供一种液压制动夹钳装置，包括如上任一项所述的液压制动缸，以及安装于所述液压制动缸上的制动夹钳杠杆。
本申请的有益效果在于：
(1)本申请至少一个实施例所提供的液压制动缸，通过间隙调节环与止挡套的配合实现了间隙自动调整功能，可调整闸片与制动盘之间的间隙；制动过程中，在闸片磨损的情况下液压制动缸内活塞移动行程增大，能快速补偿由于闸片和制动盘磨耗或其它因素而引起的制动行程的增大，制动响应迅速，提高了制动的灵敏度和行车的安全性；
(2)本申请至少一个实施例所提供的液压制动缸，通过耳座和止挡套对间隙调节环的限位作用，将间隙调节环在耳座与止挡套之间的可移动距离固定下来，在首次出现磨耗间隙的制动过程中对磨耗间隙进行补偿，在后续制动缓解过程中，间隙调节环的移动距离仍为额定退距，使得下一次制动过程中无需再次对磨耗间隙进行补偿；此外，还可以避免间隙调节环在工作过程中出现沿传动轴的轴向窜动而脱出；
(3)本申请至少一个实施例所提供的液压制动缸，取消了蝶簧蓄能缓解、充油制动的传统结构，通过活塞两侧油压及油压大小即可实现制动、制动缓解及间隙补偿功能，整体结构简单，零部件少，整体化、模块化程度高；
(4)本申请至少一个实施例所提供的液压制动缸，可通过改变活塞两侧的油腔油压设置间隙调节环在传动轴上的位置，进而调整制动夹钳机构的闸片托开度，设定闸片间隙，方便闸片更换，便于后期维修保养；
(5)本申请至少一个实施例所提供的液压制动夹钳装置，其液压制动缸具有间隙调整功能，通过改变活塞两侧油压大小即可实现制动、制动缓解以及间隙自动调整，能够达到制动响应迅速、提高制动的灵敏度和行车安全性的效果。
附图说明
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将结合附图来详细说明本申请的具体实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本申请实施例所提供的液压制动缸的结构示意图一；
图2为本申请实施例所提供的液压制动缸的结构示意图二；
图3为本申请实施例所提供的液压制动缸沿轴向的剖面图；
图4为图3中部位A的局部放大图；
图5为本申请实施例中液压制动缸的结构示意图三；
图6为图5中液压制动缸的爆炸图；
图7为本申请实施例中油缸缸体的结构示意图；
图8为本申请实施例所提供的液压制动夹钳装置的结构示意图一；
图9为本申请实施例所提供的液压制动夹钳装置的结构示意图二；
图中：
1、油缸缸体；11、油缸腔体；1101、第一油腔；1102、第二油腔；12、
第一油路；13、第二油路；14、耳座；15、密封沟槽；16、油缸衬套孔；17、油缸衬套；18、空气通路；19、开口；2、活塞；3、止挡套；4、传动轴；5、间隙调节环；6、盖体组成；61、盖体衬套孔；62、盖体衬套；7、第一密封件；8、第二密封件；9、导向环；10、防尘罩；100、液压制动缸；200、 制动夹钳杠杆；300、闸片托。
具体实施方式
为了使本申请的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本申请进行描述和说明。应当理解，此处所描述的具体实施例仅仅用以解释本申请，并不用于限定本申请。基于本申请提供的实施例，本领域普通技术人员在没有作出创造性劳动的前提下所获得的所有其他实施例，都属于本申请保护的范围。
显而易见地，下面描述中的附图仅仅是本申请的一些示例或实施例，对于本领域的普通技术人员而言，在不付出创造性劳动的前提下，还可以根据这些附图将本申请应用于其他类似情景。
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。
除非另作定义，本申请所涉及的技术术语或者科学术语应当为本申请所属技术领域内具有一般技能的人士所理解的通常意义。本申请所涉及的“一”、“一个”、“一种”等类似词语并不表示数量限制，可表示单数或复数。本申请所涉及的术语“包括”、“包含”、“具有”以及它们任何变形，意图在于覆盖不排他的包含。
在本申请的描述中，需要说明的是，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；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。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本申请中的具体含义。
如图1-图6所示，本申请第一方面提供一种带间隙调整功能的液压制动缸，该液压制动缸包括油缸缸体1，油缸缸体1内部具有油缸腔体11，油缸缸体1轴向方向的一端设置有开口19(如图7所示)，开口19处安装有止挡套3。可选地，止挡套3与油缸缸体1之间通过螺纹连接成一体，且呈密封设置，避免油液渗漏。
进一步参见图3、图4和图6，油缸腔体11内设有活塞2，活塞2与油缸缸体1的主轴线同轴设置，活塞2沿径向封闭油缸腔体11，且可相对油缸腔体11运动；活塞2将油缸腔体分为第一油腔1101与第二油腔1102。可以理解的是，在制动或制动缓解过程中，随着活塞2的轴向运动，第一油腔1101和第二油腔1102的体积会发生变化。
第二油腔1102内设有传动轴4，用于制动力的传递，传动轴4一端与活塞2固定连接。传动轴4远离活塞2的一端经止挡套3伸出至油缸缸体1外。在一些实施例中，传动轴4与活塞2之间通过螺纹连接。此外，传动轴4与止挡套3之间呈密封设置，避免油液渗漏。
油缸缸体1上设置有与第一油腔1101连通的第一油路12，用于加载液压推动活塞2向止挡套3方向移动进行制动，以及与第二油腔1102连通的第二油路13，用于加载液压推动活塞2向远离止挡套3的方向移动进行制动缓解。
传动轴4上设置有间隙调节环5，间隙调节环5能随传动轴4在第二油腔1102内做轴向运动，且能够被止挡套3阻挡限位，产生轴向弹性变形。
在上述示意性实施例中，液压制动缸具有间隙自动调整功能，在制动过程中，在油缸腔体11内液压的作用下，活塞2带动传动轴4沿轴向朝向开口19方向运动，使得传动轴4做伸出油缸缸体1的运动，当间隙调节环5运动 至与止挡套3接触时，间隙调节环5沿该方向的运动被止挡套3限制，但在液压的作用下，间隙调节环5发生弹性变形，使得传动轴4可继续向外伸出一段距离至闸片夹紧制动盘。通过改变活塞2两侧油压大小即可实现制动、制动缓解以及间隙自动调整，能够达到制动响应迅速、提高制动的灵敏度和行车安全性的效果。
在一些实施例中，间隙调节环5选用强度高的高应力弹性橡胶。制动时，间隙调节环5被止挡套3阻挡限位后能够保持在阻挡限位处，在第一油腔1101内液压的推动下，在间隙调节环5的变形范围内，传动轴4能够继续做伸出运动。
在一些实施例中，间隙调节环5过盈连接在传动轴4上。具体的，间隙调节环5的内孔表面与传动轴4的外圆柱面过盈配合，间隙调节环5与传动轴4之间具有摩擦力，同时由于间隙调节环5本身具有径向弹力，不易与传动轴4产生相对滑动。但可以理解的是，当在存在磨耗间隙的情况下，当间隙调节环5被止挡套3限位时闸片还未夹紧制动盘，由于制动过程中的制动力很大，通常会大于间隙调节环5与传动轴4之间的摩擦力，则传动轴4会发生与间隙调节环5的相对运动直至磨耗间隙被补偿。
本申请一些实施例中，沿第二油腔1102处的油缸缸体1的内壁设置有多个向油缸缸体1径向方向突出的耳座14，多个耳座14周向均匀分布在油缸缸体1的内壁上。在一些实施例中，耳座14在油缸缸体1的内壁上周向均匀设置有3个。间隙调节环5设置在耳座14与止挡套3之间，在制动缓解时，间隙调节环5能够被耳座4阻挡限位。
采用耳座14与止挡套3对间隙调节环5的移动进行限位，可以通过活塞2两侧油腔内液压的不同实现制动、制动缓解与间隙补偿功能，同时，可以通 过改变活塞2两侧液压的大小调节间隙调节环5在传动轴4上的位置，进而调整制动夹钳机构的闸片托开度，设定闸片的间隙，方便闸片的维修更换；也可以避免间隙调节环5在工作过程中出现沿传动轴4的轴向窜动而脱出。
制动过程中加载的液压所产生的活塞推力为第一活塞推力，制动缓解过程中加载的液压所产生的活塞推力为第二活塞推力。在一些实施例中，间隙调节环5与传动轴4之间的摩擦力小于第一活塞推力且大于第二活塞推力。在制动过程中，在存在磨耗间隙的情况下，在第一活塞推力的作用下，传动轴4可相对于间隙调节环5继续做伸出运动直至磨耗间隙被补偿。在制动缓解过程中，间隙调节环5与传动轴4不发生相对位移。
间隙调节环5在耳座14与止挡套3之间的可移动距离为间隙调节环5的额定退距λ，此处，需要说明的是，额定退距λ是在间隙调节环5不发生变形的情况下，间隙调节环5在耳座14与止挡套3之间的可移动距离。例如，耳座14与止挡套3之间的距离为d，间隙调节环5自然状态下的长度为L，则额定退距λ＝d-L。
通过设置耳座14，将每次制动缓解过程中间隙调节环5的移动距离(额定退距λ)进行固定，在首次出现磨耗间隙的制动过程中对磨耗间隙进行补偿，在后续制动缓解过程中，间隙调节环5的移动距离仍为额定退距λ，使得下一次制动过程中无需再次对磨耗间隙进行补偿。
例如，在前一次制动过程中，由于磨耗间隙g的存在，间隙调节环5与传动轴4发生相对运动，使得间隙调节环5在传动轴4上的位置向靠近活塞2的方向移动g，在后续制动缓解过程中，由于间隙调节环5的额定退距λ固定，则缓解后，活塞相对于制动前的位置向靠近开口19的方向移动g，则磨耗间隙g在本次制动缓解过程中已被补偿，在下一次进行制动的过程中，传动轴4 不需再额外移动g即可实现夹紧制动。
耳座14与止挡套3之间的间距以及间隙调节环5的额定退距λ可根据闸片间隙的要求进行设置。在一些实施例中，当闸片间隙为ζ时，间隙调节环5的额定退距λ≈ζ+1.5mm。其中，闸片间隙是指在缓解状态下闸片与制动盘之间的距离。
需要说明的是，由于轨道车辆优先采用电制动，在进行液压制动时速度已较低，故闸片与制动盘的磨耗很小，制动时间隙调节环5在运动额定退距λ后需要相对传动轴4的摩擦运动距离很短。
需要说明的是，活塞2的最大运动距离为制动缓解状态下活塞2远离第一油腔的端部与耳座14之间的距离，液压制动缸的最大调整量与活塞2的最大运动距离相同；液压制动缸的一次调整量与闸片间隙相同，但不超过液压制动缸的最大调整量。
在一些实施例中，活塞2外圆柱面与油缸缸体1之间的缸体内壁上开设有多个密封沟槽15，每一个密封沟槽15内均安装有密封元器件16，密封元器件16用于实现油缸缸体1与活塞2之间的密封和/或对活塞2进行导向。可选地，油缸缸体1上开设有两个密封沟槽15，分别为导向环安装沟槽和密封圈安装沟槽，导向环安装沟槽中安装的密封元器件为导向环，密封圈安装沟槽中安装的密封元器件为O形密封圈。
需要说明是，在上述实施例中，活塞2在油缸腔体11内轴向运动时，密封沟槽15始终位于油缸腔体11与活塞2之间，即密封沟槽15始终位于油缸缸体1的内壁表面与活塞2的外圆柱面之间，以实现活塞2与油缸缸体1之间的密封和导向作用。
在另一些实施例中，活塞2的外圆柱面上开设有多个密封沟槽15，每一 个密封沟槽15内均安装有密封元器件16，密封元器件16用于实现油缸缸体1与活塞2之间的密封和/或对活塞2进行导向。可选地，活塞2的外圆柱面上开设有两个密封沟槽15，分别为导向环安装沟槽和密封圈安装沟槽，导向环安装沟槽中安装的密封元器件为导向环，密封圈安装沟槽中安装的密封元器件为O形密封圈。在这种情况下，密封沟槽15始终位于油缸缸体1的内壁表面与活塞2的外圆柱面之间。
在一些实施例中，油缸缸体1上开设有油缸衬套孔16，油缸衬套孔16内过盈连接有油缸衬套17。油缸衬套17通过压入油缸衬套孔16内与油缸缸体1连为一体，油缸衬套17与油缸衬套孔16过盈配合，用于与制动夹钳杠杆连接，在本实施例中，油缸衬套17与油缸衬套孔16设置两对，两个油缸衬套孔16在油缸缸体1上呈垂向同轴且对称设置。
在一些实施例中，油缸衬套孔16可以是圆柱形孔也可以是圆柱状阶梯孔，相应的，油缸衬套17可以是圆柱形结构也可以是带法兰阶梯圆柱形结构。可以理解的是，油缸衬套孔16的形状与油缸衬套17的结构相匹配。
在一些实施例中，油缸缸体1上开设有空气通路18，空气通路18连通油缸衬套孔16与外界大气。在油缸衬套17压入油缸衬套孔16时通过空气通路18将油缸衬套孔16内的空气排出。可选地，空气通路18为圆形小直径通道。
在一些实施例中，传动轴4伸出油缸缸体1的一端连接有用于传递制动力的盖体组成6，盖体组成6上开设有盖体衬套孔61，盖体衬套孔61内过盈连接有盖体衬套62。可选地，传动轴4与盖体组成6之间通过螺栓连接紧固；盖体衬套62通过压入盖体衬套孔61内与盖体组成6连为一体，盖体衬套62与盖体衬套孔61过盈配合，用于与制动夹钳杠杆连接。在本实施例中，盖体 衬套62与盖体衬套孔61设置两对，两个盖体衬套孔61在盖体组成6上呈垂向同轴且对称设置。
在一些实施例中，盖体衬套孔61可以是圆柱形孔也可以是圆柱状阶梯孔，相应的，盖体衬套62可以是圆柱形结构也可以是带法兰阶梯圆柱形结构。可以理解的是盖体衬套孔61的形状与盖体衬套62的结构相匹配。
在一些实施例中，如图4所示，止挡套3与油缸缸体1之间且靠近油缸腔体的一侧设置有第一密封件7，用于实现止挡套3与油缸缸体1之间的密封，避免制动与制动缓解过程中油液渗漏。可选地，第一密封件7为O形密封圈。
在一些实施例中，止挡套3与传动轴4之间设置有用于导向的导向环9以及用于密封的第二密封件8。可选地，第二密封件8为O形密封圈。
在一些实施例中，止挡套3靠近盖体组成6的一端可加设防尘密封圈，用于防止外界的灰尘、水渍进入，污染内部运动机构。
在一些实施例中，油缸缸体1与传动轴4的伸出端之间设置有防尘罩10，防尘罩10一端连接在油缸缸体1的外壁上，另一端连接在传动轴4或盖体组成6上，用于进一步防止外界灰尘、水渍进入，污染内部运动机构。
以下具体说明本申请实施例所提供的液压制动缸的工作原理：
在正常间隙状态下制动时，通过第一油路12在第一油腔1101内加入液压油，第一油腔1101内的液压对油缸腔体11内的活塞2产生活塞推力，推动活塞2、传动轴4与间隙调节环5一同向止挡套3方向移动，在移动额定退距λ距离后，间隙调节环5与止挡套3紧贴，此时，闸片贴在制动盘上，由于间隙调节环5能产生轴向弹性形变，活塞2与传动轴4继续移动一个轴向弹性形变e位移后停止移动，闸片紧贴在制动盘上，产生制动力。
在闸片有磨损间隙状态下制动时，通过第一油路12在第一油腔1101内加入液压油，第一油腔1101内的液压对油缸腔体11内的活塞2产生活塞推力，推动活塞2、传动轴4与间隙调节环5一同向止挡套3方向移动，在移动额定退距λ距离后，间隙调节环5与止挡套3紧贴，受止挡套3阻挡间隙调节环5不能再移动，由于闸片的磨损厚度超过间隙调节环5的轴向弹性形变，活塞2与传动轴4在移动位移e后继续向前移动，此时，由于第一油腔1101内液压产生的第一活塞推力大于由间隙调节环5径向弹力所产生的摩擦力，传动轴4将在第一活塞推力的作用下克服摩擦力与间隙调节环5发生相对运动，活塞2与传动轴4继续向前移动直至将闸片与制动盘压紧产生制动力。通过传动轴4相对于间隙调节环5的运动对磨损间隙进行补偿，在下次制动过程中传动轴4只需轴向移动额定退距λ即可使闸片贴在制动盘上，而无需再次进行间隙补偿。
在制动缓解时，第一油腔1101内液压所产生的第一活塞推力迅速退去，同时通过第二油路13在第二油腔1102内加入液压油，第二油腔1102内的液压对油缸腔体11内的活塞2产生活塞推力，推动活塞2、传动轴4与间隙调节环5一同向远离止挡套3的方向移动，在移动额定退距λ距离后，间隙调节环5与耳座14紧贴，受耳座14的阻挡间隙调节环5不能再移动，活塞2与传动轴4也不再移动，此时间隙调节环5与止挡套3之间的距离保持为额定退距λ，即达到设定位置，闸片也达到与制动盘保持正常间隙的位置，间隙补偿动作执行完毕。需要说明的是，制动缓解时第二油腔1102内加载的液压所产生的第二活塞推力F应小于间隙调节环5与传动轴4之间的摩擦力FS，即F＜FS。
本申请第二方面提供一种液压制动夹钳装置，如图8和图9所示，包括 上述任一项实施例所述的液压制动缸100，还包括安装于液压制动缸100上的制动夹钳杠杆200，在制动夹钳杠杆200上安装有一对用于安装闸片的闸片托300，两个闸片托300相对设置且可在液压制动缸100的作用下相互靠近或远离。
制动夹钳杠杆200通过螺栓与油缸衬套17和盖体衬套62铰接，进而安装于液压制动缸100上，在两个闸片托300上分别安装有闸片，两个闸片相对且在制动过程中夹紧制动盘。其中，制动夹钳杠杆200、闸片托300以及闸片的具体结构和安装方式为现有技术，本申请不做赘述。
本申请以上实施例所提供的液压制动夹钳装置，其液压制动缸具有间隙调整功能，通过改变活塞2两侧油压大小即可实现制动、制动缓解以及间隙自动调整，能够达到制动响应迅速、提高制动的灵敏度和行车安全性的效果。
最后应当说明的是：本说明书中各个实施例采用递进的方式描述，每个实施例重点说明的都是与其他实施例的不同之处，各个实施例之间相同相似部分互相参见即可。
以上实施例仅用以说明本申请的技术方案而非对其限制；尽管参照较佳实施例对本申请进行了详细的说明，所属领域的普通技术人员应当理解：依然可以对本申请的具体实施方式进行修改或者对部分技术特征进行等同替换；而不脱离本申请技术方案的精神，其均应涵盖在本申请请求保护的技术方案范围当中。

Claims (12)

  1. 一种带间隙调整功能的液压制动缸，其特征在于，包括：
    油缸缸体，其内部具有油缸腔体，所述油缸缸体轴向方向的一端设置有开口，开口处安装有止挡套；
    活塞，其设于所述油缸腔体内，所述活塞与所述油缸缸体的主轴线同轴设置，所述活塞沿径向封闭所述油缸腔体，且可相对所述油缸腔体运动；所述活塞将所述油缸腔体分为第一油腔与第二油腔；
    传动轴，其设于所述第二油腔内，所述传动轴一端与所述活塞固定连接，所述传动轴远离所述活塞的一端经所述止挡套伸出至所述油缸缸体外；
    第一油路，其设于所述油缸缸体上且与所述第一油腔连通；
    第二油路，其设于所述油缸缸体上且与所述第二油腔连通；
    间隙调节环，其设于所述传动轴上，所述间隙调节环能随所述传动轴在所述第二油腔内做轴向运动，且能够被所述止挡套阻挡限位，产生轴向弹性变形。
  2. 根据权利要求1所述的液压制动缸，其特征在于，沿所述第二油腔处的所述油缸缸体的内壁设置有多个向所述油缸缸体径向方向突出的耳座，多个所述耳座周向均匀分布在所述油缸缸体的内壁上；所述间隙调节环设置在所述耳座与所述止挡套之间，且能够被所述耳座阻挡限位。
  3. 根据权利要求1或2所述的液压制动缸，其特征在于，所述间隙调节环过盈连接在所述传动轴上，所述间隙调节环具有径向弹力以在所述间隙调节环和所述传动轴之间产生摩擦力。
  4. 根据权利要求3所述的液压制动缸，其特征在于，制动过程中加载的液压所产生的活塞推力为第一活塞推力，制动缓解过程中加载的液压所产生 的活塞推力为第二活塞推力，所述间隙调节环与所述传动轴之间的摩擦力小于所述第一活塞推力且大于所述第二活塞推力。
  5. 根据权利要求2所述的液压制动缸，其特征在于，所述间隙调节环在所述耳座与所述止挡套之间的可移动距离为所述间隙调节环的额定退距λ，λ≈ζ+1.5mm，其中，ζ为闸片间隙。
  6. 根据权利要求1所述的液压制动缸，其特征在于，所述活塞与所述油缸缸体之间的缸体内壁上开设有多个密封沟槽，每一密封沟槽内均安装有密封元器件，所述密封元器件用于实现所述油缸缸体与所述活塞之间的密封和/或对所述活塞进行导向。
  7. 根据权利要求1所述的液压制动缸，其特征在于，所述油缸缸体上开设有油缸衬套孔，所述油缸衬套孔内过盈连接有油缸衬套；所述油缸缸体上开设有空气通路，所述空气通路连通外界大气与所述油缸衬套孔。
  8. 根据权利要求1所述的液压制动缸，其特征在于，所述传动轴伸出所述油缸缸体的一端连接有盖体组成，所述盖体组成上开设有盖体衬套孔，所述盖体衬套孔内过盈连接有盖体衬套。
  9. 根据权利要求1所述的液压制动缸，其特征在于，所述止挡套与所述油缸缸体之间设置有用于密封的第一密封件。
  10. 根据权利要求1所述的液压制动缸，其特征在于，所述止挡套与传动轴之间设置有用于密封的第二密封件和用于对所述传动轴导向的导向环。
  11. 根据权利要求1所述的液压制动缸，其特征在于，所述油缸缸体与所述传动轴的伸出端之间设置有防尘罩，所述防尘罩一端连接在所述油缸缸体的外壁上，另一端连接在所述传动轴上。
  12. 一种液压制动夹钳装置，其特征在于，包括如权利要求1-11任一项 所述的液压制动缸，以及安装于所述液压制动缸上的制动夹钳杠杆。
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