Double-end pressed sealing structure of water turbine brake

Abstract

The utility model provides a water turbine brake double-end compression sealing structure, which relates to the field of sealing, and comprises a sliding unit of a brake and a sealing ring, the sealing ring is clamped on the outer surface of the sliding unit in a sliding manner, and the sealing ring is divided into an inner fixing part and an outer friction part. According to the double-end pressed sealing structure of the water turbine brake, when the upper end of the sliding unit is extruded by a pressure medium, the device is integrally extruded and deformed along the annular notch, so that the convex unit can be always kept in contact with the sliding surface, and meanwhile, the pressure medium enters the groove and extrudes the friction head; the friction head is bent along the bending groove and keeps making contact with the sliding face, double-layer sealing is formed in the medium extrusion direction, the friction head on the side without medium extrusion does not make contact with the friction face, and when a pressure medium is extruded from the lower end of the sliding unit, double-layer extrusion is formed on the lower side in the same way; the problem that in the prior art, a double-end-pressed sealing ring is prone to leakage is solved.

Description

Technical Field

[0001] This utility model relates to the field of sealing technology, specifically to a double-end pressure-sealed structure for a water turbine brake. Background Technology

[0002] The brake, also known as the air brake, is an important component of the mechanical braking system of a hydro-generator unit. The unit's braking system consists of the brake, oil and gas pipelines, and manual and automatic control devices.

[0003] All chambers of the brake are sealed with rubber O-rings. During brake use, issues such as jamming, oil leakage, and air leakage are often accompanied by aging and damage to the O-rings. O-rings, as circular rubber rings, are primarily composed of nitrile rubber or fluororubber. Widely used in hydraulic transmission systems, O-rings are common sealing components. Under pressure, the ring rotates continuously, causing some of the ring within the gap to wear down, while other parts enter the gap area. This wear gradually expands until the O-ring is completely worn, at which point the sealing capacity decreases, leading to leakage. Utility Model Content

[0004] To address the shortcomings of existing technologies, this utility model provides a double-end pressure-sealed structure for a water turbine brake, which solves the problem of reduced sealing capacity and leakage caused by O-ring seals mentioned in the background technology.

[0005] Technical solution

[0006] To achieve the above objectives, this utility model is implemented through the following technical solution: a double-end pressure-sealed structure for a water turbine brake, comprising a sliding unit of the brake and a sealing ring. The sealing ring is slidably engaged on the outer surface of the sliding unit. The sealing ring is divided into an inner fixing part and an outer friction part. Grooves are provided at the upper and lower ends of the connection between the inner fixing part and the outer friction part. The outer friction part includes a protruding unit that protrudes outward from the middle and a friction head that protrudes outward from both the upper and lower ends. An arc-shaped bending groove is provided between the friction head and the protruding unit.

[0007] Furthermore, the outer surface of the sliding unit is provided with a bearing groove, the inner fixing part is sleeved inside the bearing groove, and the bearing groove partially covers the groove.

[0008] Furthermore, the diameter of the bending groove is larger than the diameter of the groove.

[0009] Furthermore, the top of the friction head is arc-shaped, and the outermost protruding part of the friction head and the protruding unit are located on the same vertical plane.

[0010] Furthermore, the sealing ring is made of elastic polyurethane material.

[0011] Furthermore, the inner wall of the internal fixation part is provided with an annular notch, which is located at the center of the internal fixation part.

[0012] The beneficial effects of this utility model are as follows:

[0013] 1. The double-end pressure-sealed structure of this turbine brake, when the upper end of the sliding unit is squeezed by the pressure medium, firstly, the device is squeezed and deformed along the annular notch, so that the protruding unit can always keep in contact with the sliding surface. At the same time, the pressure medium enters the groove and squeezes the friction head, so that the friction head bends along the bending groove and keeps in contact with the sliding surface, forming a double-layer seal in the direction of medium squeezing. The friction head on the side without medium squeezing does not keep in contact with the friction surface. When the pressure medium squeezes from the lower end of the sliding unit, a double-layer squeezing is formed on the lower side in the same way, which solves the problem of easy leakage of the double-end pressure-sealed ring in the prior art.

[0014] 2. The water turbine brake has a double-end pressure-sealed structure. The diameter of the bending groove is larger than the diameter of the groove. This design allows the friction head to tilt along the bending groove. Both the bending groove and the groove are arc-shaped, which ensures that the friction head is subjected to uniform force during bending and will not break. Attached Figure Description

[0015] Figure 1 This is a schematic diagram of the structure of this utility model;

[0016] Figure 2 This is a half-sectional schematic diagram of the sealing ring of this utility model;

[0017] Figure 3 This is a schematic diagram of the cross-section of the sealing ring of this utility model.

[0018] Among them, 1 is a sealing ring; 2 is a sliding unit; 11 is an inner fixing part; 12 is an outer friction part; 121 is a groove; 122 is a protruding unit; 123 is a friction head; 124 is a bending groove; 125 is an annular notch; and 201 is a bearing groove. Detailed Implementation

[0019] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0020] See Figures 1-3A double-end pressure-sealed structure for a water turbine brake includes a sliding unit 2 and a sealing ring 1. The sealing ring 1 is slidably engaged with the outer surface of the sliding unit 2. The sealing ring 1 is divided into an inner fixing part 11 and an outer friction part 12. Grooves 121 are provided at the upper and lower ends of the connection between the inner fixing part 11 and the outer friction part 12. The outer friction part 12 includes a protruding unit 122 that protrudes outward from the middle, and a friction head 123 that protrudes outward from both the upper and lower ends. An arc-shaped bending groove 124 is provided between the friction head 123 and the protruding unit 122.

[0021] The outer surface of the sliding unit 2 is provided with a bearing groove 201, and the inner fixing part 11 is sleeved inside the bearing groove 201. The bearing groove 201 partially covers the groove 121. This arrangement allows the extrusion medium hydraulic oil or compressed air to enter the groove 121, causing the friction head 123 to tilt and fit the friction head 123 on this side with the sliding surface.

[0022] The diameter of the bending groove 124 is larger than the diameter of the groove 121. This design allows the friction head 123 to tilt along the bending groove 124. Furthermore, both the bending groove 124 and the groove 121 are arc-shaped, which ensures that the friction head 123 is subjected to uniform force during bending and will not break.

[0023] The top of the friction head 123 is arc-shaped, and the outermost protruding part of the friction head 123 and the protruding unit 122 are located on the same vertical plane. This arrangement ensures that after wear, the friction head 123 and the protruding unit 122 can be deformed by external pressure to maintain their contact with the sliding surface.

[0024] The sealing ring 1 is made of elastic polyurethane material. The outstanding characteristics of thermoplastic polyurethane rubber are excellent wear resistance, high hardness, high strength, good elasticity, low temperature resistance, and good oil resistance, which can be adapted to the working conditions of the sealing ring 1.

[0025] The inner wall of the inner fixing part 11 is provided with an annular notch 125, which is located at the center of the inner fixing part 11. This arrangement allows for the overall compression deformation of the device.

[0026] In use, when the upper end of the sliding unit 2 is squeezed by the pressure medium, the device is first deformed along the annular notch 125, so that the protruding unit 122 can always keep in contact with the sliding surface. At the same time, the pressure medium enters the groove 121 and squeezes the friction head 123, so that the friction head 123 bends along the bending groove 124 and keeps in contact with the sliding surface, forming a double seal in the direction of medium compression. The friction head 123 on the side without medium compression does not keep in contact with the friction surface. When the pressure medium squeezes from the lower end of the sliding unit 2, a double compression is formed on the lower side in the same way, which solves the problem that the double-end pressure sealing ring 1 is prone to twisting and damage in the prior art.

[0027] It should be noted that in this paper, relational terms such as first and second are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations.

[0028] The above description is only a preferred embodiment of the present utility model, but the protection scope of the present utility model is not limited thereto. Any equivalent substitutions or changes made by those skilled in the art within the technical scope disclosed in the present utility model, based on the technical solution and the inventive concept of the present utility model, should be included within the protection scope of the present utility model.

Claims

1. A double-end pressure-sealed structure for a water turbine brake, comprising a sliding unit (2) of the brake and a sealing ring (1), characterized in that: The sealing ring (1) is slidably engaged on the outer surface of the sliding unit (2). The sealing ring (1) is divided into an inner fixing part (11) and an outer friction part (12). The inner fixing part (11) and the outer friction part (12) are provided with grooves (121) at the upper and lower ends of the connection. The outer friction part (12) includes a protruding unit (122) that protrudes outward from the middle, and a friction head (123) that protrudes outward from the upper and lower ends. An arc-shaped bending groove (124) is provided between the friction head (123) and the protruding unit (122).

2. The double-end pressure-sealed structure for a water turbine brake according to claim 1, characterized in that: The outer surface of the sliding unit (2) is provided with a bearing groove (201), and the inner fixing part (11) is sleeved inside the bearing groove (201), with the bearing groove (201) partially covering the groove (121).

3. The double-end pressure-sealed structure for a water turbine brake according to claim 1, characterized in that: The diameter of the bending groove (124) is larger than the diameter of the groove (121).

4. The double-end pressure-sealed structure for a water turbine brake according to claim 1, characterized in that: The top of the friction head (123) is arc-shaped, and the outermost protruding part of the friction head (123) is located on the same vertical plane as the protruding unit (122).

5. The double-end pressure-sealed structure for a water turbine brake according to claim 1, characterized in that: The sealing ring (1) is made of elastic polyurethane material.

6. The double-end pressure-sealed structure for a water turbine brake according to claim 1, characterized in that: The inner wall of the internal fixation part (11) is provided with an annular notch (125), and the annular notch (125) is located at the center of the internal fixation part (11).

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