WO2017084617A1 - 油缸以及包括该油缸的制动夹钳装置 - Google Patents

油缸以及包括该油缸的制动夹钳装置 Download PDF

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Publication number
WO2017084617A1
WO2017084617A1 PCT/CN2016/106408 CN2016106408W WO2017084617A1 WO 2017084617 A1 WO2017084617 A1 WO 2017084617A1 CN 2016106408 W CN2016106408 W CN 2016106408W WO 2017084617 A1 WO2017084617 A1 WO 2017084617A1
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WIPO (PCT)
Prior art keywords
cylinder
reset piston
piston
screw
screw sleeve
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PCT/CN2016/106408
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English (en)
French (fr)
Inventor
雷国伟
朱君华
陈炳伟
韩红文
金璟
Original Assignee
中车戚墅堰机车车辆工艺研究所有限公司
常州中车铁马科技实业有限公司
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Application filed by 中车戚墅堰机车车辆工艺研究所有限公司, 常州中车铁马科技实业有限公司 filed Critical 中车戚墅堰机车车辆工艺研究所有限公司
Priority to CN201680065855.XA priority Critical patent/CN108474429B/zh
Publication of WO2017084617A1 publication Critical patent/WO2017084617A1/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
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position

Definitions

  • the invention belongs to the technical field of basic braking, and relates to a cylinder for outputting a braking force and a brake clamping device capable of realizing gap self-adjustment using the cylinder.
  • a braking force is applied to a brake disc by a brake caliper device to effect a basic brake, wherein a cylinder (ie, a brake cylinder) in the brake caliper device is used to output a braking force.
  • a cylinder ie, a brake cylinder
  • the brake pad wear and other factors will cause the gap between the brake disc and the brake disc to expand. Therefore, the output distance of the output shaft of the cylinder needs to be self-adjusted to ensure the brake disc.
  • the gap with the brake disc is kept substantially constant, ie the gap self-adjustment is achieved.
  • the cylinder of the existing brake caliper generally adopts a plurality of thread-locking structures (ie, a screw adjusting mechanism) to perform the above adjustment.
  • a screw adjusting mechanism ie, a screw adjusting mechanism
  • the structure of the mechanism is complicated, the parts are large, and the volume is large, and the hydraulic pressure is used.
  • a cylinder with limited working space is relatively unsuitable.
  • the use of the conventional gap adjustment structure at the same time, the assembly process is very cumbersome and the processing cost is high; further, the screw adjustment mechanism uses a lot of tapered surfaces to achieve the clutch action under a small stroke of the cylinder, which is not very reliable. The amount of single adjustment of the spiral adjustment is small.
  • a cylinder for outputting a braking force having a cylinder (13) having a reset piston (2), a spring base (12) and located therein a first elastic member (16) between the reset piston (2) and the spring base (12);
  • the reset piston (2) has a stepped through hole (2-1) disposed in an axial direction, and the reset piston (2) is at least on an inner wall at a substantially central portion of the stepped through hole (2-1) Having a rear side step (2-1-1), and a rear end of the stepped through hole (2-1) of the reset piston (2) is fixedly coupled to the reset piston end cover (8);
  • the cylinder further includes: an adjusting screw (6) and a screw sleeve (5) disposed in the axial direction, a face ring clutch (7), an adjusting spring (10), an adjusting spring end cover (11), a guiding rod (3) and a second elastic member (17);
  • the adjusting screw (6) is located in the stepped through hole (2-1) of the resetting piston (2) and the rear end thereof is capable of passing the end ring gear clutch (7) and the resetting piston end cover (8)
  • the adjusting screw (6) has a boss (6-1) in a substantially middle portion thereof, and the second elastic member (17) is fitted on the adjusting screw (6) and located at the boss (6-1)
  • the rear end of the second elastic member (17) abuts against the front end of the boss (6-1), and the second elastic member ( The front end of 17) is abutted against the rear side step (2-1-1) in the stepped through hole (2-1) of the reset piston (2);
  • the screw sleeve (5) is fitted to the adjusting screw (6) a projection on the front side of the boss (6-1) and non-self-locking threaded connection with the adjusting screw (6);
  • the face ring clutch (7) is fitted on one end of the rear side of the boss (6-1) of the adjusting screw (6), and includes a first end ring gear (7-1) and a second end face.
  • a ring gear (7-2) the first end ring gear (7-1) is fixed on the reset piston end cover (8), and the second end ring gear (7-2) is relatively close to the convex
  • the table (6-1) is fixed to the adjusting screw (6);
  • the adjustment spring (10) is mounted between the guide rod (3) and the screw sleeve (5) and can be placed by the adjustment spring end cover (11)
  • an anti-rotation mechanism is arranged between the screw sleeve (5) and the reset piston (2).
  • a brake caliper apparatus including the oil cylinder of the present invention is provided.
  • FIG. 1 is a cross-sectional view of a cylinder in accordance with an embodiment of the present invention.
  • Figure 2 is a cross-sectional view of the reset piston in the cylinder of the embodiment of Figure 1.
  • Figure 3 is a left side elevational view of the reset piston in the cylinder of the embodiment of Figure 1.
  • Figure 4 is a front elevational view of the first end ring gear/second end ring gear in the cylinder of the embodiment of Figure 1.
  • Figure 5 is a cross-sectional view along line A-A of the first end ring gear/second end ring gear in the cylinder of the embodiment of Figure 1.
  • Figure 6 is a cross-sectional view taken along the line B-B of the first end ring gear/second end ring gear in the cylinder of the embodiment shown in Figure 1.
  • Figure 7 is a cross-sectional view of the screw sleeve in the cylinder of the embodiment shown in Figure 1.
  • Figure 8 is a cross-sectional view of a cylinder in accordance with still another embodiment of the present invention.
  • front is defined as the direction of the braking force output by the cylinder, and the direction opposite to the direction is defined as “rear”, and therefore, the components in the cylinder have corresponding front/rear ends, or front Side/back side.
  • the cylinder of the embodiment of the present invention is a cylinder for a brake caliper having a cylinder 13 in which a piston 1 and a reset piston 2 are axially mounted from front to rear.
  • the elastic member 16 and the spring base 12 in an embodiment, the rear end of the cylinder 13 is open, and the cylinder 13 is closed by the rear end fixedly connecting the base rear cover 9, and the base rear cover 9 is detachably mounted.
  • the components provided inside the cylinder block 13 are relatively easy to install.
  • the front end of the reset piston 2 abuts against the piston 1, the piston 1 is used to form a sealing oil chamber, and the reset piston 2 is used to form a further sealing oil chamber, through which the corresponding inlet and outlet oil pipes can be Input or output liquid medium such as oil to any of the above sealed oil chambers.
  • the piston 1 and the reset piston 2 and the cylinder 13 respectively form respective oil chambers, that is, two oil chambers, one oil chamber can be used for braking system to automatically control the clamping and relief of the clamp, and the other
  • the oil chamber can be used for emergency relief in case of failure; it should be understood that the two oil chambers constructed above can be replaced with each other as necessary to provide redundancy and prevent inoperability due to failure of a single oil chamber seal; it should also be understood that When only one of the two oil chambers constructed above can work normally, the function of the present application does not affect, and the two oil chambers can work normally to make the reliability higher.
  • the base back cover 9 can be integrally formed with the spring base 12.
  • the first elastic member 16 is a disc spring and is fitted on the reset piston 2, wherein the front end of the first elastic member 16 abuts against the reset piston 2, and the rear end of the first elastic member 16 abuts against the front end of the spring base 12; The rear end of the spring base 12 abuts against the base back cover 9.
  • the forward piston 2 can be supplied with a forward force.
  • the inside of the cylinder further has an adjusting screw 6 , a screw sleeve 5 , a face ring clutch 7 , a reset piston end cover 8 , an adjusting spring 10 , an adjusting spring end cover 11 , a guiding rod 3 and a second elastic member. 17, they are mainly used to form the gap self-adjusting mechanism of the cylinder.
  • the axial direction of the adjusting screw 6 and the screw sleeve 5 corresponds to the axial direction of the cylinder, and is used for outputting a braking force.
  • the braking force can be output forward along the adjusting screw 6 and the screw sleeve 5.
  • the front end of the reset piston 2 abuts against the piston 1, and the rear end of the reset piston 2 is detachably fixedly provided with a reset piston end cover 8, which in this embodiment is in the axial direction.
  • a stepped through hole 2-1 is provided, the rear end of the stepped through hole 2-1 is provided with an internal thread, and the reset piston end cover 8 is provided with an external thread, so that the two can be screwed and fixedly connected.
  • the adjusting screw 6 is inserted through the stepped through hole 2-1 and located in the stepped through hole 2-1 of the resetting piston 2, and the rear end of the adjusting screw 6 is assembled and connected with the resetting piston end cover 8 through the end face ring clutch 7 to ensure the adjusting screw 6 It is possible to move leftward or rightward with the reset piston 2 or to adjust the relative rotation of the screw 6, in particular, the rear end of the adjusting screw 6 projects into the center hole of the reset piston end cap 8 and the center hole of the reset piston end cap 8 Cooperating, thereby ensuring that the rear end of the adjusting screw 6 can be rotated relative to the reset piston end cap 8.
  • a boss 6-1 is disposed substantially in the middle of the adjusting screw 6, which may specifically but not limited to the annular boss 6-1, the right side of the annular boss 6-1
  • a non-self-locking external thread may be disposed on the adjusting screw 6 at one end, and the screw sleeve 5 is set on the right end of the annular boss 6-1 of the adjusting screw 6, and the screw sleeve 5 is provided with a non-self-locking internal thread,
  • a non-self-locking screw connection can be achieved with the adjusting screw 6, so that if the adjusting screw 6 is subjected to a rearward thrust, the adjusting screw 6 can be rotated relative to the screw sleeve 5 to move to the left relative to the screw sleeve 5.
  • the corresponding screw sleeve 5 of the stepped through hole 2-1 is provided with an axial groove 2-2, and the screw sleeve 5 is further provided with a fixing pin 5-1.
  • the end of the fixing pin 5-1 is located in the axial groove 2-2 in the stepped through hole 2-1 of the reset piston 2, thereby restricting the rotation of the screw sleeve 5 when the adjusting screw 6 rotates, so that the screw sleeve 5 Can only move axially.
  • the axial groove 2-2 and the fixing pin 5-1 and the like in the above embodiment form an anti-rotation mechanism between the screw sleeve 5 and the reset piston 2 according to an embodiment of the present invention.
  • the face ring clutch 7 is fitted on the adjusting screw 6 and located on the left end of the annular boss 6-1, specifically at the rear end of the adjusting screw 6 and the reset piston end cap.
  • the face ring clutch 7 comprises a first end ring gear 7-1 and a second end ring gear 7-2; wherein the first end ring gear 7-1 and the reset piston end cover 8 Integrally formed, or the outer diameter of the first end ring gear 7-1 is interference-fitted with the central hole of the reset piston end cap 8, and the second end ring gear 7-2 is fixed to the adjusting screw 6 and to the annular boss 6
  • the rear end of the -1 is offset, and the inner hole of the second end ring gear 7-2 can be interference fit with the adjusting screw 6; when the first end ring gear 7-1 and the second end ring gear 7-2 are separated
  • the end ring gear clutch 7 is in a disengaged state or a disengaged state.
  • the first end ring gear 7-1 cannot limit the rotation of the adjusting screw 6 fixedly coupled with the second end ring gear 7-2;
  • the end ring gear 7-1 and the second end ring gear 7-2 are in contact with each other.
  • the end ring gear clutch 7 is in a fitted state, and the second end ring gear 7-2 is fixed.
  • the rotation of the adjusting screw 6 that is fixed together is blocked by the first end ring gear 7-1.
  • a second elastic member 17 is provided on the right side of the annular boss 6-1, which is also located in the stepped through hole 2-1 of the reset piston 2, and is set in the adjustment.
  • the front end of the second elastic member 17 and the rear side step 2 in the stepped through hole 2-1 of the reset piston 2 1-1 is offset.
  • the second elastic member 17 can provide a rearward thrust to the adjusting screw 6 when compressed, so that the adjusting screw 6 rotates backward relative to the screw sleeve 5 (if the first end ring gear 7-1 and the second end ring gear 7- 2 phase separation).
  • the second elastic member 17 may be a disc spring or other type of energy storage element
  • the first elastic member 16 may also be a disc spring or other type of energy storage element.
  • the disc spring is used for the first elastic member 16 and/or the second elastic member 17, energy can be stored and released better.
  • the screw sleeve 5 is located at the right end of the annular boss 6-1.
  • the guide rod 3 is placed on the front end of the screw sleeve 5, and the guide rod 3 is specifically passed through the center hole of the piston 1, and protrudes from the front end of the reset piston 2 into the stepped through hole 2-1-1 of the reset piston 2.
  • the guide rods 3 are axially slidably engaged with the piston 1 and the reset piston 2, respectively.
  • the front end of the guide rod 3 is screwed to the cylinder block 13 to restrict the movement of the guide rod 3 in the left-right direction when the screw sleeve 5 moves left and right relative to the guide rod 3, and the assembly is simple.
  • the rear end of the guiding rod 3 is fixedly provided with an adjusting spring end cover 11, for example, a threaded connection between the guiding rod 13 and the adjusting spring end cover 11, and the adjusting spring end cover 11 is fitted on the screw sleeve 5, ensuring that the screw sleeve 5 can be opposite
  • the adjustment spring end cover 11 moves left and right.
  • the adjusting spring 10 is disposed between the guiding rod 3 and the screw sleeve 5, and the adjusting spring 10 is also fitted on the screw sleeve 5, and the adjusting spring 10 is in an interference fit with the outer circumferential surface of the screw sleeve 5, for example, the adjusting spring 10 is hung on the screw On the sleeve 5, in this way, by adjusting the friction between the spring 10 and the screw sleeve 5, the adjustment spring 10 can provide an axial force, in particular a forward axial force, to the screw sleeve 5 under certain conditions.
  • the screw sleeve 5 drives the adjustment spring 10 to move axially rearward
  • the rear end of the adjustment spring 10 abuts against the adjustment spring end cover 11 and is prevented from moving backward, and the adjustment spring 10 provides the forward axial direction to the screw sleeve 5.
  • the force can prevent the screw sleeve 5 from moving backward.
  • the manner of assembling between the adjusting spring 10 and the screw sleeve 5 is not limited to the above embodiment, and other adjustments of the spring end cover 11 by the adjusting spring 10 can be provided to the screw sleeve 5 when the axial upper limit position is provided.
  • the way the axial force is assembled when the adjusting spring 10 abuts against the adjusting spring end cover 11 and provides a forward axial force to the screw sleeve 5, the first end ring gear 7-1 and the second end ring gear 7-2 are separated and The second elastic member 17 is compressed to push the adjusting screw 6 to rotate backward relative to the screw sleeve 5 (because the screw sleeve 5 is restricted from being rotated by the anti-rotation mechanism).
  • the middle portion of the guide bar 3 has an annular step 3-1 that abuts against the cylinder block 13, for example, as shown in Figs. 1 and 8 with an annular step.
  • the front end of the guide rod 3 is fixedly coupled to the cylinder block 13 by a nut 18.
  • the first elastic member 16 is fitted on the reset piston 2 , the front end thereof abuts the reset piston 2 , the rear end thereof abuts against the front end of the spring base 12 , and the rear end of the spring base 12 and the base rear cover 9 offset.
  • the cylinder further has a screw sleeve end cover 4 .
  • One end of the screw sleeve end cover 4 is fitted on the front end of the adjusting screw 6 and is screwed to the screw sleeve 5 , and the other end of the screw sleeve end cover 4 has a ring shape.
  • Block 4-1 which can be used to transmit the force of the screw sleeve 5.
  • the adjusting spring 10 is hooped with the screw sleeve 5 , that is, when the axial force of the screw sleeve 5 is greater than the friction between the screw sleeve 5 and the adjusting spring 10 , the screw sleeve 5 and the adjusting spring An axial relative slip occurs between 10.
  • the corresponding adjusting spring 10 in the guiding rod 3 is further provided with a bushing 14 which is disposed in the guiding rod 3 opposite to the adjusting spring 10 so as to protect the parts (for example, the adjusting spring) 10) and the role of lubrication.
  • the cylinder setting mode of the embodiment shown in FIG. 8 is substantially the same as the cylinder setting mode of the embodiment shown in FIG. 1, and details are not described herein.
  • the oil chamber of the cylinder discharges oil, and after losing the oil pressure, the first elastic member 16 in a compressed state pushes the reset piston 2 and the piston 1 to the right, and is screwed to the reset piston 2 at the same time.
  • the resetting piston end cap 8 will push the adjusting screw 6 to the right by the end ring gear clutch 7, and the screw sleeve 5 which is screwed by the adjusting screw 6 is moved to the right, and finally the screw sleeve end cover which is screwed with the screw sleeve 5 4 Transfer or output braking force outward.
  • the rotation of the screw 6 causes the total length of the adjusting screw 6 and the screw sleeve 5 to be screwed to increase, which serves as a compensation for the gap adjustment.
  • This adjustment mode is achieved by changing the total length of the adjusting screw 6 and the screw sleeve 5 after screwing. Adjusting the compensation, even in the small stroke of the piston, the amount of single adjustment can be large.
  • the degree of above rotation can be completely achieved according to the amount of gap change, and therefore has a function of self-adjustment of the gap.
  • the inside of the cylinder of the above embodiment has few components, wherein the gap adjusting mechanism inside the cylinder adopts friction sliding to realize the clutching function, which can replace the taper structure used in the conventional cylinder to realize the clutching function, and only needs to adjust the screw 6 and A set of non-self-locking thread pairs are arranged between the screw sleeves 5 to reduce the number of screw pairs; therefore, the internal structure of the oil cylinder is simple and the volume is small, which is also beneficial to reducing the volume of the oil cylinder as a whole, and is very suitable for the small cylinder size. Use under conditions. Moreover, the assembly process of the cylinder is simple, the processing cost is low, and the reliability of the cylinder is good.
  • the cylinder of the above embodiment can be applied to a brake caliper device for outputting a braking force.
  • the brake caliper device can be applied to a rail vehicle, such as a low floor rail vehicle. It should be understood that the brake caliper device of the embodiment of the present invention can also be applied to other vehicles with similar working conditions, such as mine engineering vehicles and the like.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
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Abstract

一种油缸以及包括该油缸的制动夹钳装置，属于基础制动技术领域。该油缸具有缸体(13)，所述缸体内装有活塞(1)、复位活塞(2)、弹簧底座(12)和位于所述复位活塞(2)和弹簧底座(12)之间的第一弹性件(16)，并且还包括在轴向上设置的调节螺杆(6)、螺杆套(5)、端面齿圈离合器(7)、复位活塞端盖(8)、调节簧(10)、调节簧端盖(11)、导向杆(3)和第二弹性件(17)。该油缸内部结构简单、体积小、易组装、成本低，并且包括该油缸的制动夹钳装置能够自动调节间隙。

Description

油缸以及包括该油缸的制动夹钳装置 技术领域
本发明属于基础制动技术领域，涉及用于输出制动力的油缸以及使用该油缸的可实现间隙自调整的制动夹钳装置。
背景技术
在诸如轨道交通技术领域，通过制动夹钳装置输出制动力作用在制动盘上从而实现基础制动，其中，制动夹钳装置中的油缸(即制动缸)用于输出制动力。
在制动夹钳装置不停的工作过程中，闸片磨损等因素会导致制动盘与闸片之间的间隙扩大，因此，油缸的输出轴的输出距离需要相应地自调节以保证闸片与制动盘之间的间隙基本保持恒定，即实现间隙自调整。
现有的制动夹钳的油缸一般采用多个螺纹自锁的结构(即螺旋调节机构)进行上述调节，然而，这种机构的结构复杂、零部件较多、体积很大，对于使用液压力工作的空间有限的油缸，是相对不大合适的。并且，采用传统的间隙调整结构，同时会使组装工艺十分繁琐，加工成本较高；进一步，这种螺旋调节机构用到很多锥面配合以在油缸小行程下实现离合器作用，不是很可靠，这种螺旋调节单次调节量较小。
有鉴于此，有必要提出一种新型的制动夹钳装置用油缸。
发明内容
按照本发明的一方面，提供一种一种油缸，用于输出制动力，其具有缸体(13)，所述缸体(13)内装有复位活塞(2)、弹簧底座(12)和位于所述复位活塞(2)和弹簧底座(12)之间的第一弹性件(16)；
所述复位活塞(2)具有在轴向上设置的台阶通孔(2-1)，且所述复位活塞(2)在所述台阶通孔(2-1)的大致中部处的内壁上至少具有后侧台阶(2-1-1)，并且所述复位活塞(2)的台阶通孔(2-1)的后端与复位活塞端盖(8)固定连接；
所述油缸还包括：在轴向上设置的调节螺杆(6)、螺杆套(5)、 端面齿圈离合器(7)、调节簧(10)、调节簧端盖(11)、导向杆(3)和第二弹性件(17)；
其中，所述调节螺杆(6)位于所述复位活塞(2)的台阶通孔(2-1)中并且其后端能够通过端面齿圈离合器(7)与所述复位活塞端盖(8)连接，所述调节螺杆(6)的大致中部具有凸台(6-1)，所述第二弹性件(17)套装在所述调节螺杆(6)上并位于所述凸台(6-1)与所述后侧台阶(2-1-1)之间，所述第二弹性件(17)的后端与所述凸台(6-1)的前端相抵，所述第二弹性件(17)的前端与所述复位活塞(2)的台阶通孔(2-1)中的后侧台阶(2-1-1)相抵；所述螺杆套(5)套装在所述调节螺杆(6)的凸台(6-1)的前侧一端上并且与所述调节螺杆(6)非自锁螺纹连接；
其中，所述端面齿圈离合器(7)套装在所述调节螺杆(6)的凸台(6-1)的后侧一端上，并包括第一端面齿圈(7-1)和第二端面齿圈(7-2)，所述第一端面齿圈(7-1)固定在所述复位活塞端盖(8)上，所述第二端面齿圈(7-2)相对靠近所述凸台(6-1)地固定在所述调节螺杆(6)上；
其中，所述导向杆(3)套装在所述螺杆套(5)上并相对所述缸体(13)固定，所述调节簧端盖(11)套装在所述螺杆套(5)上且固定于所述导向杆(3)的后端，所述调节簧(10)安装在所述导向杆(3)与螺杆套(5)之间并能够被所述调节簧端盖(11)在轴向上限位，所述调节簧(10)通过其被所述调节簧端盖(11)在轴向上限位时能够向所述螺杆套(5)提供轴向力的方式装配在所述螺杆套(5)上；
其中，所述螺杆套(5)与所述复位活塞(2)之间设有防转机构。
按照本发明的又一方面，提供一种制动夹钳装置，其包括本发明的油缸。
根据以下描述和附图,本发明的以上特征、操作和相应带来的效果将变得更加显而易见。
附图说明
从结合附图的以下详细说明中，将会使本发明的上述和其他目的及优点更加完整清楚，其中，相同或相似的要素采用相同的标号表示。
图1是按照本发明一实施例的油缸的剖视图。
图2是图1所示实施例的油缸中的复位活塞的剖视图。
图3是图1所示实施例的油缸中的复位活塞的左视图。
图4是图1所示实施例的油缸中的第一端面齿圈/第二端面齿圈的主视图。
图5是图1所示实施例的油缸中的第一端面齿圈/第二端面齿圈的A-A剖视图。
图6是图1所示实施例的油缸中的第一端面齿圈/第二端面齿圈的B-B剖视图。
图7是图1所示实施例的油缸中的螺杆套的剖视图。
图8是按照本发明又一实施例的油缸的剖视图。
具体实施方式
下面介绍的是本发明的多个可能实施例中的一些，旨在提供对本发明的基本了解，并不旨在确认本发明的关键或决定性的要素或限定所要保护的范围。容易理解，根据本发明的技术方案，在不变更本发明的实质精神下，本领域的一般技术人员可以提出可相互替换的其他实现方式。因此，以下具体实施方式以及附图仅是对本发明的技术方案的示例性说明，而不应当视为本发明的全部或者视为对本发明技术方案的限定或限制。
在描述中，为描述的清楚，“前”定义为油缸输出的制动力的方向，与该方向相反的方向定义为“后”，因此，油缸中的部件具有相应的前端/后端、或者前侧/后侧。
在附图中，未作特别说明的情况下，所有剖面均是沿油缸的轴向上剖切的，并且，基于附图中的方位，方位术语“右”与以上所定义的方向“前”相对应，方位术语“左”与以上所定义的方向“后”相对应。
如图1所示，本发明实施例的油缸是一种制动夹钳用油缸，其具有缸体13，缸体13内从前向后依次轴向地装有活塞1、复位活塞2、第一弹性件16和弹簧底座12，在一实施例中，缸体13的后端是开放的，其通过后端固定连接底座后盖9的方式封闭缸体13，底座后盖9是可拆卸地安装在缸体13上，因此，缸体13内部设置的部件安装比较方便。其中，复位活塞2的前端与活塞1相抵，活塞1用于形成一密封油室，复位活塞2用于形成又一密封油室，通过相应的进出油管可以 向以上任意密封油室输入或输出油等液体介质。在该实施例中，活塞1和复位活塞2分别和缸体13构成各自的油腔，即两个油腔，一个油腔可以用于制动***自动控制夹钳的制动和缓解，另外一个油腔可以用于故障时紧急缓解；应当理解，以上构成的两个油腔之间必要时可以相互替换，从而起到冗余作用，防止因为单个油腔密封失效导致无法工作；还应当理解，以上构成的两个油腔中只有一个油腔能够正常工作时，本申请的功能不影响，两个油腔都能够正常工作时可以使可靠度更高。
在又一替换实施例中，底座后盖9可以与弹簧底座12一体地形成。
具体地，第一弹性件16是碟簧且套装在复位活塞2上，其中，第一弹性件16的前端与复位活塞2相抵，第一弹性件16的后端与弹簧底座12的前端相抵；弹簧底座12的后端与所述底座后盖9相抵。这样在第一弹性件16被压缩时，可以向复位活塞2提供向前的力。
继续如图1所示，油缸的内部还具有调节螺杆6、螺杆套5、端面齿圈离合器7、复位活塞端盖8、调节簧10、调节簧端盖11、导向杆3和第二弹性件17，它们主要地用于形成油缸的间隙自调整机构。其中，调节螺杆6、螺杆套5的轴向即对应于油缸的轴向，其用于输出制动力，例如，制动力可以沿调节螺杆6、螺杆套5向前输出。
如图1、2、3所示，复位活塞2的前端与活塞1相抵，复位活塞2的后端可拆卸地固定设置有复位活塞端盖8，在该实施例中，复位活塞2在轴向上设置有台阶通孔2-1，台阶通孔2-1的后端设置有内螺纹，复位活塞端盖8设置有外螺纹，从而二者可以实现螺纹固定连接。
调节螺杆6是贯穿台阶通孔2-1并位于复位活塞2的台阶通孔2-1中，调节螺杆6的后端通过端面齿圈离合器7与复位活塞端盖8装配连接，确保调节螺杆6能够与复位活塞2一起向左、向右移动或调节螺杆6相对转动，具体地，调节螺杆6的后端伸入复位活塞端盖8的中心孔中且与复位活塞端盖8的中心孔间隙配合，从而保证调节螺杆6的后端能够相对复位活塞端盖8转动。
在一实施例中，如图2所示，在调节螺杆6的大致中部设置有凸台6-1，其具体可以但不限于为环形凸台6-1，环形凸台6-1的右侧一端的调节螺杆6上可以设置非自锁的外螺纹，螺杆套5套装在调节螺杆6的环形凸台6-1的右侧一端上，螺杆套5上设置有非自锁的内螺纹，其 可以与调节螺杆6实现非自锁螺纹连接，从而，如果调节螺杆6受到向后的推力，调节螺杆6可以相对螺杆套5自旋转，实现相对螺杆套5向左移动。在一实施例中，如图1、2、3、7所示，台阶通孔2-1中对应螺杆套5设置有轴向槽2-2，螺杆套5上还装有固定销5-1,固定销5-1的端部位于复位活塞2的台阶通孔2-1中的轴向槽2-2内，从而，在调节螺杆6自旋转时限制螺杆套5的转动，使螺杆套5只能轴向移动。以上实施例中的轴向槽2-2和固定销5-1等形成了本发明一实施例的螺杆套5与复位活塞2之间的防转机构。
如图1、4、5、6所示，端面齿圈离合器7套装在调节螺杆6上并位于环形凸台6-1的左侧一端上，具***于调节螺杆6的后端与复位活塞端盖8之间；在一实施例中，端面齿圈离合器7包括第一端面齿圈7-1和第二端面齿圈7-2；其中，第一端面齿圈7-1与复位活塞端盖8一体地制成，或者第一端面齿圈7-1的外径与复位活塞端盖8的中心孔过盈配合，第二端面齿圈7-2固定在调节螺杆6上且与环形凸台6-1的后端相抵，第二端面齿圈7-2的内孔可以与所述调节螺杆6过盈配合；在第一端面齿圈7-1和第二端面齿圈7-2相分离时，端面齿圈离合器7处于分离状态或脱开状态，此时，第一端面齿圈7-1不能限制与第二端面齿圈7-2固定连接在一起的调节螺杆6的转动；在第一端面齿圈7-1和第二端面齿圈7-2相互贴合，它们之间的齿相对啮合时，端面齿圈离合器7处于贴合状态，与第二端面齿圈7-2固定连接在一起的调节螺杆6的转动被第一端面齿圈7-1阻止。
在该实施例中，继续如图1所示，在环形凸台6-1的右侧设置有第二弹性件17，其也位于复位活塞2的台阶通孔2-1中，并且套装在调节螺杆6上，其中，第二弹性件17的后端与环形凸台6-1的前端相抵，第二弹性件17的前端与复位活塞2的台阶通孔2-1中的后侧台阶2-1-1相抵。第二弹性件17在压缩时可以为调节螺杆6提供向后的推力，从而使调节螺杆6相对螺杆套5向后地自转(如果第一端面齿圈7-1和第二端面齿圈7-2相分离)。具体地，第二弹性件17可以为碟簧或其他类型的蓄能元件，以上第一弹性件16也可以碟簧或其他类型的蓄能元件。在第一弹性件16和/或第二弹性件17使用碟簧时，可以较好地储存和释放能量。
继续如图1、8所示，螺杆套5位于环形凸台6-1的右侧一端的调 节螺杆6上，导向杆3套装在螺杆套5的前端上，导向杆3具体是穿过活塞1的中心孔，且从复位活塞2前端伸入复位活塞2的台阶通孔2-1-1内；导向杆3分别与活塞1和复位活塞2轴向滑动配合。其中，导向杆3的前端与缸体13螺纹固定连接，从而在螺杆套5相对于导向杆3左右移动时限制导向杆3在左右方向移动，并且装配简单。导向杆3的后端固定设置有调节簧端盖11，例如导向杆13与调节簧端盖11之间以螺纹方式连接且调节簧端盖11套装在螺杆套5上，确保螺杆套5能够相对于调节簧端盖11左右移动。
调节簧10设置在导向杆3与螺杆套5之间，且调节簧10也套装在螺杆套5上，并且调节簧10与螺杆套5的外周面过盈配合，例如调节簧10箍接在螺杆套5上，这样，通过调节簧10与螺杆套5之间的摩擦力，调节簧10在一定条件下能够向螺杆套5提供轴向力，特别是向前的轴向力。例如，在螺杆套5带动调节簧10向后轴向移动时，调节簧10的后端与调节簧端盖11相抵并被阻止向后运动，调节簧10向螺杆套5提供向前的轴向力，能够阻止螺杆套5向后移动。
需要理解的是，调节簧10与螺杆套5之间装配方式并不限于以上实施例，还可以使用其他的通过调节簧10被调节簧端盖11在轴向上限位时能够向螺杆套5提供轴向力的装配方式。这样，在调节簧10与所述调节簧端盖11相抵并向螺杆套5提供向前的轴向力时，第一端面齿圈7-1和第二端面齿圈7-2相分离且所述第二弹性件17压缩，从而向后地推动所述调节螺杆6相对螺杆套5自转(因为此时螺杆套5被防转机构限制转动)。
具体地，导向杆3的中部具有与缸体13相抵的环形台阶3-1，例如如图1和图8所示具有环形台阶。在图8所示实施例的油缸中，具体地，导向杆3的前端通过螺母18固定连接在缸体13上。
继续如图1所示，第一弹性件16时套装在复位活塞2上，其前端与复位活塞2相抵，其后端与弹簧底座12的前端相抵；并且弹簧底座12的后端与底座后盖9相抵。具体地，还可以在底座后盖9安装密封盖15，密封盖15可以起防尘作用。
继续如图1所示，油缸还具有螺杆套端盖4，螺杆套端盖4的一端套装在调节螺杆6的前端上并且与螺杆套5螺纹连接，螺杆套端盖4的另一端具有环形止挡4-1，其可以用于传递螺杆套5的力。
继续如图1所示，由于调节簧10与螺杆套5箍接连接，即当螺杆套5轴向受力大于螺杆套5与调节簧10之间的摩擦力时，螺杆套5会与调节簧10之间产生轴向相对滑动。在一较佳的实施例中，导向杆3内对应调节簧10还设置有衬套14，衬套14在导向杆3内相向于调节簧10设置，从而，可以起到保护零件(例如调节簧10)及润滑的作用。
需要说明的是，在未作具体区别说明的情况下，图8所示实施例的油缸设置方式与图1所示实施例的油缸设置方式基本相同，在此不作赘述。
以下具体说明本发明图1和图8所示实施例的油缸的工作原理。
本发明的油缸在使用时，油缸的油室排出油，失去油压后，处于压缩状态的第一弹性件16会推动复位活塞2和活塞1向右移动，同时，与复位活塞2螺纹连接的复位活塞端盖8会通过端面齿圈离合器7推动调节螺杆6向右移动，并由调节螺杆6带动与其螺纹连接的螺杆套5向右移动，最终通过与螺杆套5螺纹连接的螺杆套端盖4向外传递或输出制动力。此时,由于端面齿圈离合器7的第一端面齿圈7-1与第二端面齿圈7-2相贴合，限制了调节螺杆6的转动，而螺杆套5在固定销5-1和轴向槽2-2的作用下其转动也被限制，螺杆套5只能轴向移动,因而调节螺杆6和螺杆套5之间不能相对转动，调节螺杆6与螺杆套5的总长保持不变。
当油缸的油室通油时，在油压的作用下活塞1与复位活塞2开始向左移动，同理，调节螺杆5、螺杆套5和调节簧10也向左移动，直到箍接连接在螺杆套5上的调节簧10的左侧与调节簧端盖11相抵；由于调节簧10是与螺杆套5箍接连接，若此时油压继续作用使调节螺杆6向左移动，调节簧10与螺杆套5之间的摩擦力(即向右的轴向力)会阻碍螺杆套5向左移动，使螺杆套5基本停止移动；此时螺纹连接在复位活塞2上的复位活塞端盖8继续随复位活塞2一起向左移动，使得凸台6-1压缩第二弹性件17，同时固定在复位活塞端盖8上的第一端面齿圈7-1与固定在调节螺杆6上的第二端面齿圈7-2由原来的贴合状态变为分离状态或脱开状态；又由于螺杆套5与调节螺杆6为非自锁螺纹连接且固定销5-1限制了螺杆套5的转动，因此在第二弹性件17的推力作用下调节螺杆6进行自转，直到第二端面齿圈7-1与第一端面齿圈7-2再次贴合，调节螺杆6停止转动不再向左伸出。以上调节 螺杆6的自转导致调节螺杆6与螺杆套5螺纹连接后的总长度增加，起到了间隙调节补偿的作用，这种调节方式通过改变调节螺杆6与螺杆套5螺纹连接后的总长度，来实现调节补偿，即使在活塞小行程时，单次的调节量也可以很大。以上自转的程度完全可根据间隙变化量来自适用地完成，因此，也具有间隙自调节的功能。
以上实施例的油缸内部的零部件少，其中，油缸内部的间隙调节机构采用摩擦滑动实现离合功能，其可以替代传统油缸中使用的锥面结构来实现离合功能，而且，只需要调节螺杆6和螺杆套5之间设置一套非自锁螺纹副，减少螺旋副数量；因此，导致油缸的内部结构简单、体积小，也有利于整体减小油缸的体积，非常适合于要求油缸体积小的工况条件下使用。并且，油缸的组装工艺也简单、加工成本低，油缸的可靠性好。
以上实施例的油缸可以应用于制动夹钳装置上，用来输出制动力。该制动夹钳装置可以应用在轨道车辆上，例如低地板的轨道车辆。应当理解，本发明实施例的制动夹钳装置还可以应用于其他类似工况要求的车辆上，例如矿山工程车辆等。
以上例子主要说明了本发明的油缸以及制动夹钳装置。尽管只对其中一些本发明的实施方式进行了描述，但是本领域普通技术人员应当了解，本发明可以在不偏离其主旨与范围内以许多其他的形式实施。因此，所展示的例子与实施方式被视为示意性的而非限制性的，在不脱离如所附各权利要求所定义的本发明精神及范围的情况下，本发明可能涵盖各种的修改与替换。

Claims (19)

  1. 一种油缸，用于输出制动力，其具有缸体(13)，所述缸体(13)内装有复位活塞(2)、弹簧底座(12)和位于所述复位活塞(2)和弹簧底座(12)之间的第一弹性件(16)；其特征在于：
    所述复位活塞(2)具有在轴向上设置的台阶通孔(2-1)，且所述复位活塞(2)在所述台阶通孔(2-1)的大致中部处的内壁上至少具有后侧台阶(2-1-1)，并且所述复位活塞(2)的台阶通孔(2-1)的后端与复位活塞端盖(8)固定连接；
    所述油缸还包括：在轴向上设置的调节螺杆(6)、螺杆套(5)、端面齿圈离合器(7)、调节簧(10)、调节簧端盖(11)、导向杆(3)和第二弹性件(17)；
    其中，所述调节螺杆(6)位于所述复位活塞(2)的台阶通孔(2-1)中并且其后端能够通过端面齿圈离合器(7)与所述复位活塞端盖(8)连接，所述调节螺杆(6)的大致中部具有凸台(6-1)，所述第二弹性件(17)套装在所述调节螺杆(6)上并位于所述凸台(6-1)与所述后侧台阶(2-1-1)之间，所述第二弹性件(17)的后端与所述凸台(6-1)的前端相抵，所述第二弹性件(17)的前端与所述复位活塞(2)的台阶通孔(2-1)中的后侧台阶(2-1-1)相抵；所述螺杆套(5)套装在所述调节螺杆(6)的凸台(6-1)的前侧一端上并且与所述调节螺杆(6)非自锁螺纹连接；
    其中，所述端面齿圈离合器(7)套装在所述调节螺杆(6)的凸台(6-1)的后侧一端上，并包括第一端面齿圈(7-1)和第二端面齿圈(7-2)，所述第一端面齿圈(7-1)固定在所述复位活塞端盖(8)上，所述第二端面齿圈(7-2)相对靠近所述凸台(6-1)地固定在所述调节螺杆(6)上；
    其中，所述导向杆(3)套装在所述螺杆套(5)上并相对所述缸体(13)固定，所述调节簧端盖(11)套装在所述螺杆套(5)上且固定于所述导向杆(3)的后端，所述调节簧(10)安装在所述导向杆(3)与螺杆套(5)之间并能够被所述调节簧端盖(11)在轴向上限位，所述调节簧(10)通过其被所述调节簧端盖(11)在轴向上限位时能够向所述螺杆套(5)提供轴向力的方式装配在所述螺杆套(5)上；
    其中，所述螺杆套(5)与所述复位活塞(2)之间设有防转机构。
  2. 如权利要求1所述的油缸，其特征在于，所述防转机构通过以下方式实现：所述螺杆套(5)上还装有固定销(5-1),所述固定销(5-1)的相对所述螺杆套(5)外凸的端部位于所述复位活塞(2)的台阶通孔(2-1)中的轴向槽(2-2)内。
  3. 如权利要求1所述的油缸，其特征在于，所述第二端面齿圈(7-2)与所述调节螺杆(6)的所述凸台(6-1)的后端相抵。
  4. 如权利要求1所述的油缸，其特征在于，所述复位活塞端盖(8)在所述台阶通孔(2-1)中与所述复位活塞(2)螺纹连接。
  5. 如权利要求1所述的油缸，其特征在于，所述导向杆(3)的前端与所述缸体(13)螺纹连接。
  6. 如权利要求1所述的油缸，其特征在于，所述缸体(13)上固定连接有底座后盖(9)，所述弹簧底座(12)的后端与所述底座后盖(9)相抵。
  7. 如权利要求6所述的油缸，其特征在于，所述第一弹性件(16)套装在复位活塞(2)上，且所述第一弹性件(16)的前端与复位活塞(2)相抵，所述第一弹性件(16)的后端与弹簧底座(12)的前端相抵；所述弹簧底座(12)的后端与所述底座后盖(9)相抵。
  8. 如权利要求6所述的油缸，其特征在于，所述底座后盖(9)上安装有密封盖(15)。
  9. 如权利要求1所述的油缸，其特征在于，所述调节簧(10)箍接在所述螺杆套(5)上。
  10. 如权利要求1所述的油缸，其特征在于，还具有螺杆套端盖(4)，所述螺杆套端盖(4)的后端套装在所述调节螺杆(6)的前端部，且与螺杆套(5)螺纹连接，所述螺杆套端盖(4)的前端具有环形止挡(4-1)。
  11. 如权利要求1所述的油缸，其特征在于，所述第一弹性件(16)和/或第二弹性件(17)为碟簧。
  12. 如权利要求1所述的油缸，其特征在于，所述导向杆(3)内相向于所述调节簧(10)设置有衬套(14)。
  13. 如权利要求1所述的油缸，其特征在于，所述导向杆(3)的前端通过螺母(18)固定连接在所述缸体(13)上，所述导向杆(3) 的中部具有与所述缸体(13)相抵的环形台阶(3-1)。
  14. 如权利要求1所述的油缸，其特征在于，所述调节螺杆(6)的后端伸入所述复位活塞端盖(8)的中心通孔中且与所述复位活塞端盖(8)的中心孔间隙配合。
  15. 如权利要求1所述的油缸，其特征在于，所述第一端面齿圈(7-1)与所述复位活塞端盖(8)一体地制成或所述第一端面齿圈(7-1)的外径与所述复位活塞端盖(8)的中心孔过盈配合；所述第二端面齿圈(7-2)的内孔与所述调节螺杆(6)过盈配合。
  16. 如权利要求1所述的油缸，其特征在于，所述复位活塞(2)的前端与所述活塞(1)相抵。
  17. 如权利要求16所述的油缸，其特征在于，所述导向杆(3)穿过所述活塞(1)的中心孔，且从复位活塞(2)前端伸入复位活塞(2)的台阶通孔(2-1-1)内；所述导向杆(3)分别与活塞(1)和复位活塞(2)轴向滑动配合。
  18. 一种制动夹钳装置，包括如权利要求1-17中任一项所述的油缸。
  19. 如权利要求18所述的制动夹钳装置，其特征在于，所述制动夹钳装置用于轨道车辆。
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CN109248944A (zh) * 2018-11-27 2019-01-22 安徽德系重工科技有限公司 一种数控弯管机弹性夹持装置
CN113074614A (zh) * 2021-03-08 2021-07-06 安徽省恒泰动力科技有限公司 基于自动送料机构的活塞圆度测试装置
CN113294462A (zh) * 2021-04-29 2021-08-24 中车青岛四方车辆研究所有限公司 一种弹簧动力单元
CN114109958A (zh) * 2021-09-30 2022-03-01 中国北方车辆研究所 液压式转向对中油缸
CN114992262A (zh) * 2022-06-30 2022-09-02 中车青岛四方车辆研究所有限公司 一体式弹簧动力单元
CN116255407A (zh) * 2023-05-12 2023-06-13 中车戚墅堰机车车辆工艺研究所有限公司 一种带磨损自补偿功能的液压控制混合制动器

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CN113074614B (zh) * 2021-03-08 2023-10-03 安徽省恒泰动力科技有限公司 基于自动送料机构的活塞圆度测试装置
CN113294462A (zh) * 2021-04-29 2021-08-24 中车青岛四方车辆研究所有限公司 一种弹簧动力单元
CN114109958A (zh) * 2021-09-30 2022-03-01 中国北方车辆研究所 液压式转向对中油缸
CN114109958B (zh) * 2021-09-30 2024-01-30 中国北方车辆研究所 液压式转向对中油缸
CN114992262A (zh) * 2022-06-30 2022-09-02 中车青岛四方车辆研究所有限公司 一体式弹簧动力单元
CN114992262B (zh) * 2022-06-30 2024-04-19 中车青岛四方车辆研究所有限公司 一体式弹簧动力单元
CN116255407A (zh) * 2023-05-12 2023-06-13 中车戚墅堰机车车辆工艺研究所有限公司 一种带磨损自补偿功能的液压控制混合制动器

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