WO2017084617A1

WO2017084617A1 - Cylinder and brake clamp device including same

Info

Publication number: WO2017084617A1
Application number: PCT/CN2016/106408
Authority: WO
Inventors: 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
Priority date: 2015-11-20
Filing date: 2016-11-18
Publication date: 2017-05-26
Also published as: CN108474429A; CN105351405B; CN105351405A; CN108474429B

Abstract

Disclosed are a cylinder and a brake clamp device including same, belonging to the field of basic braking technology. The cylinder is provided with a cylinder body (13), which is internally installed with a piston (1), a reset piston (2), a spring base (12) and a first elastic member (16) located between the reset piston (2) and the spring base (12), and further comprises an adjusting screw (6), a screw sleeve (5), an end face toothed ring clutch (7), a reset piston end cover (8), an adjusting spring (10), an adjusting spring end cover (11), a guide rod (3) and a second elastic member (17) which are arranged in the axial direction. The cylinder has a simple internal structure, a small volume and low costs, is easy and convenient to assemble, and the brake clamp device including the cylinder can automatically adjust a gap.

Description

Cylinder and brake clamp device including the same

Technical field

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.

Background technique

In the field of rail transit technology, for example, 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.

During the non-stop operation of the brake caliper device, 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. However, 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. Moreover, 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.

In view of this, it is necessary to propose a new type of cylinder for a brake caliper device.

Summary of the invention

According to an aspect of the invention, there is provided 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);

Wherein 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) Connecting, 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) Between the rear side step (2-1-1), 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);

Wherein 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);

Wherein the guiding rod (3) is fitted on the screw sleeve (5) and fixed relative to the cylinder (13), and the adjusting spring end cover (11) is fitted on the screw sleeve (5) and Fixed to the rear end of the guide rod (3), 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 axial upper limit position at which the adjusting spring (10) is fitted to the screw by means of which the adjusting spring end cap (11) is capable of providing an axial force to the screw sleeve (5) at an axial upper limit position Set (5);

Wherein, an anti-rotation mechanism is arranged between the screw sleeve (5) and the reset piston (2).

According to still another aspect of the present invention, a brake caliper apparatus including the oil cylinder of the present invention is provided.

The above features, operations, and corresponding effects of the present invention will become more apparent from the following description and drawings.

DRAWINGS

The above and other objects and advantages of the present invention will be more fully understood from the aspects of the appended claims.

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.

detailed description

The following is a description of some of the various possible embodiments of the invention, which are intended to provide a basic understanding of the invention and are not intended to identify key or critical elements of the invention or the scope of the invention. It is to be understood that, in accordance with the technical aspects of the present invention, those skilled in the art can suggest other alternatives that are interchangeable without departing from the spirit of the invention. Therefore, the following detailed description and the accompanying drawings are merely illustrative of the embodiments of the invention, and are not intended to

In the description, for the sake of clarity of description, "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.

In the drawings, all sections are cut along the axial direction of the cylinder without specific explanation, and based on the orientation in the drawing, the orientation term "right" and the direction defined above are "front". Correspondingly, the orientation term "left" corresponds to the direction "back" defined above.

As shown in FIG. 1 , 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. On the cylinder block 13, therefore, the components provided inside the cylinder block 13 are relatively easy to install. Wherein, 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. In this embodiment, 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.

In yet another alternative embodiment, the base back cover 9 can be integrally formed with the spring base 12.

Specifically, 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. Thus, when the first elastic member 16 is compressed, the forward piston 2 can be supplied with a forward force.

As shown in FIG. 1 , 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. For example, the braking force can be output forward along the adjusting screw 6 and the screw sleeve 5.

As shown in Figures 1, 2 and 3, 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.

In an embodiment, as shown in FIG. 2, 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. In an embodiment, as shown in FIGS. 1, 2, 3, and 7, 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.

As shown in Figures 1, 4, 5 and 6, 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. In an embodiment, 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. At this time, 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. When the teeth between the two are engaged 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.

In this embodiment, continuing as shown in FIG. 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. On the screw 6, wherein the rear end of the second elastic member 17 abuts against the front end of the annular boss 6-1, 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). Specifically, the second elastic member 17 may be a disc spring or other type of energy storage element, and the first elastic member 16 may also be a disc spring or other type of energy storage element. When 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.

Continued as shown in Figures 1 and 8, the screw sleeve 5 is located at the right end of the annular boss 6-1. On the screw 6, 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. For example, when 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.

It should be understood that 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. Thus, 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).

Specifically, 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. In the cylinder of the embodiment shown in Fig. 8, specifically, the front end of the guide rod 3 is fixedly coupled to the cylinder block 13 by a nut 18.

As shown in FIG. 1 , 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. Specifically, it is also possible to mount a sealing cover 15 on the base rear cover 9, which can function as a dustproof.

As shown in FIG. 1 , 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.

As shown in FIG. 1 , since 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. In a preferred embodiment, 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.

It should be noted that, in the case where the difference is not specifically described, 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 working principle of the cylinder of the embodiment shown in Figs. 1 and 8 of the present invention will be specifically described below.

When the cylinder of the present invention is in use, 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. At this time, since the first end ring gear 7-1 of the face ring clutch 7 is fitted to the second end ring gear 7-2, the rotation of the adjusting screw 6 is restricted, and the screw sleeve 5 is at the fixing pin 5-1 and The rotation of the axial groove 2-2 is also restricted, and the screw sleeve 5 can only move axially, so that the adjustment screw 6 and the screw sleeve 5 cannot rotate relative to each other, and the total length of the adjustment screw 6 and the screw sleeve 5 remains unchanged. .

When the oil chamber of the oil cylinder is oiled, the piston 1 and the reset piston 2 start to move to the left under the action of the oil pressure. Similarly, the adjusting screw 5, the screw sleeve 5 and the adjusting spring 10 are also moved to the left until the hoop is connected. The left side of the adjusting spring 10 on the screw sleeve 5 abuts against the adjusting spring end cover 11; since the adjusting spring 10 is hooped and connected with the screw sleeve 5, if the oil pressure continues to act to move the adjusting screw 6 to the left, the adjusting spring 10 The frictional force with the screw sleeve 5 (i.e., the axial force to the right) hinders the movement of the screw sleeve 5 to the left, so that the screw sleeve 5 substantially stops moving; at this time, the reset piston end cover 8 screwed onto the reset piston 2 Continue to move to the left with the reset piston 2, so that the boss 6-1 compresses the second elastic member 17, while the first end ring gear 7-1 fixed to the reset piston end cover 8 and the first fixed to the adjusting screw 6 The second end ring gear 7-2 is changed from the original fitting state to the disengaged state or the disengaged state; and since the screw sleeve 5 and the adjusting screw 6 are non-self-locking screw connections and the fixing pin 5-1 limits the rotation of the screw sleeve 5 Therefore, the adjusting screw 6 is rotated by the thrust of the second elastic member 17 until the second end surface 7-1 ring with 7-2 ring gear attached to the first end face again, adjustment screw 6 projecting to the left is no longer stopped. Above adjustment 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.

The above examples mainly illustrate the cylinder and the brake caliper device of the present invention. Although only a few of the embodiments of the present invention have been described, it will be understood by those skilled in the art that the invention may be practiced in many other forms without departing from the spirit and scope of the invention. Accordingly, the present invention is to be construed as illustrative and not restrictive, and the invention may cover various modifications without departing from the spirit and scope of the invention as defined by the appended claims With replacement.

Claims

A cylinder for outputting a braking force, having a cylinder (13) having a reset piston (2), a spring base (12), and a reset base (2) and a spring base a first elastic member (16) between (12); characterized in that:

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), a screw sleeve (5), a face ring clutch (7), an adjusting spring (10), an adjusting spring end cover (11), and a guiding rod (3) disposed in the axial direction. And a second elastic member (17);

Wherein 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) Connecting, 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) Between the rear side step (2-1-1), 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);

Wherein 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);

Wherein the guiding rod (3) is fitted on the screw sleeve (5) and fixed relative to the cylinder (13), and the adjusting spring end cover (11) is fitted on the screw sleeve (5) and Fixed to the rear end of the guide rod (3), 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 axial upper limit position at which the adjusting spring (10) is fitted to the screw by means of which the adjusting spring end cap (11) is capable of providing an axial force to the screw sleeve (5) at an axial upper limit position Set (5);

Wherein, an anti-rotation mechanism is arranged between the screw sleeve (5) and the reset piston (2).
A cylinder according to claim 1, wherein said anti-rotation mechanism is realized by: said screw sleeve (5) further comprising a fixing pin (5-1), said fixing pin (5-1) The convex end of the screw sleeve (5) is located in the axial groove (2-2) in the stepped through hole (2-1) of the reset piston (2).
A cylinder according to claim 1, wherein said second end ring gear (7-2) abuts against a rear end of said boss (6-1) of said adjusting screw (6).
A cylinder according to claim 1, characterized in that the reset piston end cap (8) is screwed into the stepped through hole (2-1) with the reset piston (2).
A cylinder according to claim 1, characterized in that the front end of the guide rod (3) is screwed to the cylinder (13).
The cylinder according to claim 1, wherein a base back cover (9) is fixedly coupled to the cylinder block (13), a rear end of the spring base (12) and the base rear cover (9) Offset.
A cylinder according to claim 6, wherein said first elastic member (16) is fitted over the reset piston (2), and the front end of said first elastic member (16) is opposed to the reset piston (2) 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 rear cover (9).
A cylinder according to claim 6, wherein a seal cover (15) is mounted on the base rear cover (9).
A cylinder according to claim 1, characterized in that the adjusting spring (10) is hooped on the screw sleeve (5).
The cylinder according to claim 1, further comprising a screw sleeve end cover (4), a rear end of the screw sleeve end cover (4) being fitted at a front end portion of the adjusting screw (6), and The screw sleeve (5) is screwed, and the front end of the screw sleeve end cover (4) has an annular stop (4-1).
A cylinder according to claim 1, wherein said first elastic member (16) and/or second elastic member (17) are disc springs.
A cylinder according to claim 1, characterized in that the guide rod (3) is provided with a bushing (14) facing the adjusting spring (10).
The cylinder according to claim 1, characterized in that the front end of the guide rod (3) is fixedly coupled to the cylinder block (13) by a nut (18), the guide rod (3) The middle portion has an annular step (3-1) that abuts the cylinder (13).
A cylinder according to claim 1, wherein a rear end of said adjusting screw (6) projects into a central through hole of said reset piston end cap (8) and with said reset piston end cap (8) The center hole clearance fits.
A cylinder according to claim 1, wherein said first end ring gear (7-1) is integrally formed with said reset piston end cap (8) or said first end ring gear (7- The outer diameter of 1) is interference fit with the central bore of the reset piston end cap (8); the inner bore of the second end ring gear (7-2) is interference fit with the adjusting screw (6).
A cylinder according to claim 1, characterized in that the front end of the reset piston (2) abuts against the piston (1).
A cylinder according to claim 16, wherein said guide rod (3) passes through a center hole of said piston (1) and extends from a front end of said reset piston (2) into a stepped passage of said reset piston (2) Inside the hole (2-1-1); the guide rod (3) is axially slidably engaged with the piston (1) and the reset piston (2), respectively.
A brake caliper apparatus comprising the cylinder of any of claims 1-17.
A brake caliper device according to claim 18, wherein said brake caliper device is for a rail vehicle.