Brake oil cylinder with adjustable pre-tightening force in thrust mode
By introducing a screw and a guide floating piston into the brake cylinder, the compression of the disc spring assembly can be continuously adjusted, solving the problem of brake force attenuation caused by wear in traditional brake systems, and achieving dynamic compensation of braking performance and reduction of maintenance costs.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- JIANGSU HENGLI HYDRAULIC
- Filing Date
- 2025-05-26
- Publication Date
- 2026-04-24
AI Technical Summary
Traditional braking systems in the marine field suffer from brake force decay due to the reduced compression of disc springs as they wear down, failing to meet the dual redundancy braking specifications of the ABS classification society. Furthermore, the lack of an effective preload adjustment mechanism in thrust mode leads to frequent and time-consuming maintenance.
A brake cylinder with adjustable preload in thrust mode was designed. Through the cooperation of the screw and the guide floating piston, the compression of the disc spring assembly can be continuously adjusted to dynamically compensate the braking force. The guide floating piston and thrust bearing are used to reduce friction, and a protective cover is used to ensure braking performance.
It achieves dynamic compensation of braking force as brake pad wear increases, ensuring the stability of braking performance, reducing maintenance frequency and cost, and meeting the requirements of dual-redundant braking specifications.
Smart Images
Figure CN224161985U_ABST
Abstract
Description
Technical Field
[0001] This utility model belongs to the field of brake cylinder technology, and particularly relates to a brake cylinder with adjustable preload in thrust mode. Background Technology
[0002] In the maritime field (ships, drilling platforms, etc.), the braking system of anchor winches and hoists is a core component ensuring the safe operation of the equipment. Traditional braking systems generally use a structure design where spring force provides braking force, and hydraulic pressure is used to push a piston to release the brake. This type of system faces the following drawbacks:
[0003] The contradiction between durability and the complexity of operating conditions: Ships are in a high-salt-spray, high-humidity environment for a long time, and the wear rate of brake pads is 2-3 times that of land equipment. The compression of disc springs in existing thrust-mode brake cylinders gradually decreases with wear, resulting in brake force attenuation, which cannot meet the "dual redundancy braking" specification requirements of the ABS classification society for lifting operations.
[0004] Therefore, the aforementioned deficiencies are technical problems that urgently need to be solved in this field.
[0005] It should be noted that the information disclosed in this background section is only for understanding the background technology of this application concept, and therefore, the above description is not considered to constitute information related to the technology. Utility Model Content
[0006] This disclosure provides at least one embodiment of a brake cylinder with adjustable preload in thrust mode.
[0007] In a first aspect, embodiments of this disclosure provide a brake cylinder with adjustable preload in thrust mode, comprising:
[0008] The cylinder block has a cylinder bottom and a piston rod at each end;
[0009] Disc spring assembly, located inside the cylinder, is used to provide braking thrust;
[0010] The preload adjustment mechanism, installed on the bottom side of the cylinder, includes:
[0011] The screw is threaded to the bottom of the cylinder;
[0012] A guide floating piston is sleeved on the outer wall of the piston rod and abuts against the disc spring assembly;
[0013] The screw drives the guide floating piston to move axially along the piston rod by rotation, thereby adjusting the compression of the disc spring assembly.
[0014] In one alternative embodiment, the screw is a hollow structure with an inner diameter larger than that of the piston rod, and the piston rod is adapted to reciprocate within the hollow structure.
[0015] In one alternative embodiment, the preload adjustment mechanism further includes a thrust bearing, with its two sides respectively abutting against the guide floating piston and the screw.
[0016] In one alternative embodiment, the preload adjustment mechanism further includes a protective cover, which is sealed to the cylinder body, filled with anti-corrosion lubricating grease, and the outer end of the screw protrudes from the protective cover.
[0017] In one optional embodiment, a fixed piston is fitted and fixed to the outer wall of the end of the piston rod away from the cylinder body, and one end of the disc spring assembly abuts against the fixed piston.
[0018] In one alternative embodiment, the piston rod has a rod head lug for engaging with the winch brake arm.
[0019] In one optional embodiment, the disc spring assembly includes multiple mating disc springs, with the compression deformation of a single disc spring ranging from 1 to 2.14 mm, and the total compression deformation of the disc spring assembly ranging from 88 to 188 mm.
[0020] In one optional embodiment, an oil inlet is provided on the outer wall of the cylinder body, the oil inlet is located between the cylinder body end and the fixed piston, and the oil inlet is connected to an external hydraulic pipeline.
[0021] In one alternative embodiment, the outer wall of the screw is provided with a trapezoidal thread, and the trapezoidal thread is located inside the protective cover.
[0022] The beneficial effect of this utility model is that it provides a brake cylinder with adjustable preload in thrust mode. Through the cooperation of the screw and the guide floating piston, the compression of the disc spring assembly can be continuously adjusted in thrust mode, so that the braking force is dynamically compensated as the brake pad wear increases, thus ensuring braking performance.
[0023] Other features and advantages of this invention will be set forth in the description which follows, and will be apparent in part from the description, or may be learned by practicing the invention. The objectives and other advantages of this invention are realized and obtained through the structures particularly pointed out in the description and the accompanying drawings.
[0024] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, preferred embodiments are described in detail below with reference to the accompanying drawings. Attached Figure Description
[0025] To more clearly illustrate the technical solutions in the specific embodiments or related technologies of this utility model, the drawings used in the description of the specific embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.
[0026] Figure 1 A perspective view of the brake cylinder provided in an embodiment of this disclosure;
[0027] Figure 2 A cross-sectional view of a brake cylinder provided in an embodiment of this disclosure;
[0028] Figure 3 A cross-sectional view of the preload adjustment mechanism provided in this embodiment.
[0029] In the picture:
[0030] 1. Cylinder block; 10. Oil inlet; 2. Cylinder bottom; 3. Piston rod; 30. Fixed piston; 31. Rod head lug; 4. Disc spring assembly; 5. Preload adjustment mechanism; 51. Screw; 52. Guide floating piston; 53. Thrust bearing; 54. Protective cover. Detailed Implementation
[0031] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.
[0032] In this document, when it is mentioned that a first component is located on a second component, this can mean that the first component can be directly formed on the second component, or that a third component can be inserted between the first and second components. Furthermore, in the accompanying drawings, the thickness of the components may be exaggerated or reduced for the purpose of effectively describing the technical content.
[0033] In this document, exemplary embodiments of the present disclosure will be described in more detail with reference to the accompanying drawings. As used herein, expressions such as “at least one of…” modify the entire list of elements when following a list of elements, rather than individual elements in the list. For example, the expression “at least one of a, b, and c” should be understood to include only a, only b, only c, both a and b, both a and c, both b and c, or all of a, b, and c.
[0034] The terminology used herein is for the purpose of describing specific exemplary configurations only and is not intended to be limiting. As used herein, the singular articles “a,” “an,” and “the” may also be intended to include plural forms unless otherwise clearly stated herein. The terms “comprising,” “including,” and “having” are inclusive and thus specify the presence of features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein should not be construed as requiring them to be performed in the specific order discussed or shown, unless specifically identified as such. Additional or alternative steps may be employed.
[0035] As used herein, the phrases “in one embodiment,” “according to one embodiment,” “in some embodiments,” etc., generally refer to the fact that a particular feature, structure, or characteristic following the phrase can be included in at least one embodiment of this disclosure. Therefore, a particular feature, structure, or characteristic can be included in more than one embodiment of this disclosure, such that these phrases do not necessarily refer to the same embodiment. As used herein, the terms “example,” “exemplary,” etc., are used to “serve as an example, instance, or illustration.” Any implementation, aspect, or design described herein as “example” or “exemplary” is not necessarily to be construed as preferred or superior to other implementations, aspects, or designs. Rather, the use of the terms “example,” “exemplary,” etc., is intended to present concepts in a specific manner.
[0036] Research has revealed that in the maritime field (ships, drilling platforms, etc.), the braking system of anchor winches and hoists is a core component ensuring the safe operation of the equipment. Traditional braking systems generally employ a structure design where spring force provides braking force, and hydraulic pressure is used to push a piston to release the brake. This type of system faces the following drawbacks:
[0037] 1. The contradiction between durability and the complexity of operating conditions: Ships are in a high salt spray and high humidity environment for a long time. The wear rate of brake pads is 2-3 times that of land equipment. In the existing thrust mode (that is, the braking force is provided by the thrust of the disc spring on the piston rod), the compression of the disc spring of the brake cylinder gradually decreases with wear, resulting in the loss of braking force. This cannot meet the "dual redundancy braking" specification requirements of the ABS classification society for lifting operations.
[0038] 2. The contradiction between maintenance costs and safety: Although the traditional traction mode brake cylinder can compensate for braking force by adjusting the disc spring mounting distance, its structure is only suitable for traction conditions. The lack of a similar adjustment mechanism in thrust mode leads to frequent disassembly of the cylinder and replacement of the disc spring during maintenance, which is time-consuming and labor-intensive.
[0039] Therefore, the aforementioned deficiencies are technical problems that urgently need to be solved in this field.
[0040] The defects in the above solutions and the reasons for their occurrence are the results of the inventors' practice and careful research. Therefore, the discovery process of the above problems and the solutions proposed in this disclosure should be considered as the inventors' contributions to this disclosure.
[0041] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.
[0042] The following detailed description, with reference to the accompanying drawings, describes some embodiments of the present invention. Unless otherwise specified, the following embodiments and features can be combined with each other.
[0043] like Figures 1 to 3 As shown, at least one embodiment provides a brake cylinder with adjustable preload in thrust mode, comprising: a cylinder body 1, the cylinder body 1 being made of duplex stainless steel; a cylinder bottom 2 and a piston rod 3 respectively provided at both ends; the piston rod 3 being slidably disposed within the cylinder body 1, with one end protruding from the cylinder body 1. The piston rod 3 has a rod head lug 31 for cooperating with the winch brake arm, and the rod head lug 31 is adapted to drive the brake pads to move synchronously when moving horizontally.
[0044] Reference Appendix Figure 2 A disc spring assembly 4 is disposed inside the cylinder body 1. The disc spring assembly 4 is sleeved on the outer wall of the piston rod 3, and its two ends abut against the fixed piston 30 and the guide floating piston 52, respectively. The disc spring assembly 4 includes multiple mating disc springs, the compression deformation of a single disc spring ranging from 1 to 2.14 mm, and the total compression deformation of the disc spring assembly 4 ranging from 88 to 188 mm. The disc spring assembly 4 pushes the fixed piston 30 towards the rod head lug 31 to provide braking thrust. When installing the brake cylinder and the winch brake arm, the hydraulic line supplies hydraulic oil to the oil inlet 10. The hydraulic oil pushes the fixed piston 30, causing the piston rod 3 to move as a whole towards the cylinder bottom 2, until the rod head lug 31 is fixed to the winch brake arm. When the hydraulic oil in the cylinder body 1 is discharged, the disc spring assembly 4 pushes the fixed piston 30 towards the rod head lug 31 to provide braking thrust to the winch brake arm.
[0045] Reference Appendix Figure 3The preload adjustment mechanism 5, installed on the side of the cylinder bottom 2, includes: a screw 51 threadedly connected to the cylinder bottom 2; when the screw 51 rotates circumferentially relative to the cylinder bottom 2, the screw 51 moves synchronously relative to the cylinder bottom 2 in the axial direction. The screw 51 is a hollow structure, and its inner diameter is larger than the diameter of the piston rod 3, which is suitable for insertion into the screw 51. The outer wall of the screw 51 is provided with a trapezoidal thread, and the trapezoidal thread is located inside the protective cover 54. The trapezoidal thread facilitates the rotation of the screw 51 and reduces rotational resistance. When the screw 51 rotates relative to the cylinder bottom 2, the screw 51 moves towards the piston rod 3, thereby pushing the guide floating piston 52 to move horizontally synchronously to compress the disc spring assembly 4, thereby adjusting the compression of the disc spring assembly 4. The disc spring assembly 4 compresses the fixed piston 30 and the piston rod 3 to move towards the rod head ear 31, further improving the braking force of the brake pads. A guide floating piston 52 is sleeved on the outer wall of the piston rod 3 and abuts against the disc spring assembly 4. A thrust bearing 53 abuts against the guide floating piston 52 and the screw 51 on both sides. The thrust bearing 53 is used to reduce the axial friction force when the screw 51 rotates, ensuring the linear movement of the guide floating piston 52. The screw 51 drives the guide floating piston 52 and the thrust bearing 53 to move axially along the piston rod 3 by rotation, thereby adjusting the compression of the disc spring assembly 4 and achieving dynamic compensation of the preload. Through the cooperation of the screw 51 and the guide floating piston 52, the disc spring assembly 4 can be continuously adjusted within the compression range of 88-188mm, allowing the braking force to dynamically compensate for the wear of the brake pads, thus ensuring braking performance.
[0046] Continue to refer to the appendix Figure 3 The preload adjustment mechanism 5 also includes a protective cover 54, which is sealed to the cylinder body 1 and filled with anti-corrosion lubricating grease. The outer end of the screw 51 protrudes from the protective cover 54. The protective cover 54 provides corrosion and dust protection, thereby extending the service life of the equipment.
[0047] Reference Appendix Figure 2 A fixed piston 30 is sleeved and fixed on the outer wall of the piston rod 3 away from the cylinder body 1, and one end of the disc spring assembly 4 abuts against the fixed piston 30. An oil inlet 10 is provided on the outer wall of the cylinder body 1, and the oil inlet 10 is located between the end of the cylinder body 1 and the fixed piston 30. The oil inlet 10 is connected to an external hydraulic pipeline.
[0048] The working principle is as follows:
[0049] If brake pad wear leads to a decrease in braking force, please refer to the appendix. Figure 3The screw 51 rotates circumferentially and moves axially during rotation. The screw 51 pushes the thrust bearing 53 and the guide floating piston 52 to move synchronously to the left. The guide floating piston 52 compresses the disc spring assembly 4 to adjust the compression of the disc spring assembly 4. The disc spring assembly 4 pushes the fixed piston 30 to move towards the rod head ear 31 to increase the braking thrust. Figure 3 In the diagram, F3 represents the rotation direction of screw 51, F1 represents the movement direction of guide floating piston 52, and F2 represents the thrust direction of piston rod 3.
[0050] In the description of the embodiments of this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.
[0051] In the description of this utility model, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence unless expressly indicated herein. Therefore, without departing from the teachings of the exemplary embodiments, the first element, component, region, layer, or segment discussed above may be referred to as the second element, component, region, layer, or segment.
[0052] Based on the above-described preferred embodiments of this utility model, and through the foregoing description, those skilled in the art can make various changes and modifications without departing from the technical concept of this utility model. The technical scope of this utility model is not limited to the contents of the specification, but must be determined according to the scope of the claims.
Claims
1. A brake cylinder with adjustable preload in thrust mode, characterized in that, include: The cylinder body (1) has a cylinder bottom (2) and a piston rod (3) at its two ends respectively; Disc spring assembly (4), located inside cylinder (1), is used to provide braking thrust; The preload adjustment mechanism (5), installed on the side of the cylinder bottom (2), includes: The screw (51) is threadedly connected to the cylinder bottom (2); A guide floating piston (52) is sleeved on the outer wall of the piston rod (3) and abuts against one end of the disc spring assembly (4); The screw (51) drives the guide floating piston (52) to move axially along the piston rod (3) by rotation, so as to adjust the compression of the disc spring assembly (4).
2. The brake cylinder as described in claim 1, characterized in that, The screw (51) is a hollow structure with an inner diameter larger than that of the piston rod (3). The piston rod (3) is adapted to reciprocate within the hollow structure.
3. The brake cylinder as described in claim 1, characterized in that, The preload adjustment mechanism (5) also includes a thrust bearing (53), which abuts against the guide floating piston (52) and the screw (51) on both sides respectively.
4. The brake cylinder as described in claim 1, characterized in that, The preload adjustment mechanism (5) also includes a protective cover (54), which is sealed to the cylinder (1), and is filled with anti-corrosion lubricating grease. The outer end of the screw (51) protrudes from the protective cover (54).
5. The brake cylinder as described in claim 1, characterized in that, A fixed piston (30) is fitted on the outer wall of the piston rod (3) away from the cylinder (1), and the other end of the disc spring assembly (4) abuts against the fixed piston (30).
6. The brake cylinder as described in claim 5, characterized in that, The piston rod (3) is provided with a rod head lug (31) for cooperating with the winch brake arm.
7. The brake cylinder as described in claim 1, characterized in that, The disc spring assembly (4) includes multiple mating disc springs, with the compression deformation of a single disc spring ranging from 1 to 2.14 mm, and the total compression deformation of the disc spring assembly (4) ranging from 88 to 188 mm.
8. The brake cylinder as described in claim 5, characterized in that, The cylinder body (1) has an oil inlet (10) on its outer wall. The oil inlet (10) is located between the end of the cylinder body (1) and the fixed piston (30). The oil inlet (10) is connected to an external hydraulic pipeline.
9. The brake cylinder as described in claim 4, characterized in that, The outer wall of the screw (51) is provided with a trapezoidal thread, and the trapezoidal thread is located inside the protective cover (54).