CN214036367U

CN214036367U - Piston sealing element for reducing extrusion stress for hydraulic support oil cylinder

Info

Publication number: CN214036367U
Application number: CN202022731222.4U
Authority: CN
Inventors: 王文进
Original assignee: Weiwan Technology Co ltd
Current assignee: Weiwan Technology Co ltd
Priority date: 2020-11-23
Filing date: 2020-11-23
Publication date: 2021-08-24
Anticipated expiration: 2030-11-23

Abstract

The utility model discloses a hydraulic support hydro-cylinder is with piston seal spare that reduces extrusion stress, including the piston, be provided with the seal groove on the piston, be provided with double-acting sealing member in the seal groove, be provided with full retaining ring between double-acting sealing member and the seal groove, the both sides of full retaining ring are inconsistent with double-acting sealing member and seal groove respectively, reduce the pressure that receives on half retaining ring through full retaining ring to prevent that half retaining ring from being extruded.

Description

Piston sealing element for reducing extrusion stress for hydraulic support oil cylinder

Technical Field

The utility model belongs to the mechanical seal field, more specifically the utility model relates to a hydraulic support stand is anti piston sealing system that extrudes for hydro-cylinder that says so.

Background

The hydraulic support is used for supporting and controlling a top plate of a fully mechanized mining face and pushing and walking of working face equipment, can reliably and effectively support and control the top plate of the working face, isolates a goaf, prevents gangue from entering a stope face and propelling a scraper conveyor, and the upright posts and the jacks are used as executing elements in a hydraulic support system to realize the functions of lifting, descending, pushing, moving and the like of the whole hydraulic support. The hydraulic support realizes telescopic action through the upright post oil cylinder and mainly comprises a single telescopic part and a double telescopic part.

With the improvement of the fully mechanized mining technology level, the working resistance of the largest shield type two-column large mining height hydraulic support at present is 26000KN, the mining height is 8.8 m, and the cylinder diameter of the vertical column of the hydraulic support is 600 mm. In general: 1. the larger the cylinder diameter of the oil cylinder is, the larger the fit clearance of the joint surface of the piston and the cylinder body is, the larger the bearing pressure of the sealing element is, and the extrusion resistance of the sealing element is reduced; 2. when the double-telescopic oil cylinder is adopted, the cylinder diameter is reduced, so that the pressure borne by the piston is higher under the same working resistance; 3. uncontrollable working conditions often occur in the real fully-mechanized mining, and sometimes the pressure of ore pressure can quickly and instantly reach more than 120 MPa; 4. the coal face has an inclination angle, so that the upright post has unbalance loading, and the unilateral clearance of the piston is enlarged during unbalance loading.

The common seal on the column piston is a double-acting seal, as shown in fig. 4, which comprises a "male" sealing ring, an elastic ring and two half-collars, the sealing ring is positioned at the bottom of the sealing groove, the elastic ring is positioned above the sealing ring, and one part of the elastic ring extends out of the sealing groove, the part of the elastic ring extending out of the sealing groove is a trapezoidal convex ring, the two half retaining rings are respectively positioned on the steps at the two sides of the sealing ring, when the piston is arranged in the cylinder body, the trapezoidal convex ring on the elastic ring generates deformation and is abutted against the cylinder body, when the piston stretches on the cylinder body, the half retaining ring receives the pressure generated by the elastic ring, due to the problems in the fully mechanized mining, the transmission double-acting sealing element can not reduce the pressure on the half retaining ring, so that the pressure on the half retaining ring is overlarge, the half retaining ring is extruded under stress, so that the piston fails, and the service life of the hydraulic support is shortened.

SUMMERY OF THE UTILITY MODEL

The utility model provides a not enough to prior art, the utility model provides a hydraulic support hydro-cylinder is with piston seal spare that reduces extrusion stress reduces the pressure that half fender circle received, prevents that half fender circle from extruding.

In order to achieve the above purpose, the utility model provides a following technical scheme: the utility model provides a hydraulic support hydro-cylinder is with piston seal spare that reduces extrusion stress, includes the piston, is provided with the seal groove on the piston, is provided with double-acting seal spare in the seal groove, be provided with full retaining ring between double-acting seal spare and the seal groove, the both sides of full retaining ring are inconsistent with double-acting seal spare and seal groove respectively.

Furthermore, the cross-section of full retaining ring is the inverted right trapezoid, and the one side that just offsets with the seal groove is the inclined plane.

Further, a gap is arranged between the double-acting sealing element and the sealing groove.

Furthermore, the upper surface of the trapezoid boss is in a wave shape, and at least one wave trough and two wave crests are arranged on the upper surface of the wave shape.

Furthermore, a plurality of friction bulges are arranged on the side surface of the half check ring, which is abutted against the elastic ring and the sealing ring.

Compared with the prior art, the beneficial effects of the utility model are that: one side through between two effect sealing member and seal groove sets up full retaining ring, can share the pressure that receives on the board retaining ring through full retaining ring to reduce the extrusion stress on half retaining ring, thereby prevent that half retaining ring from being extruded.

Drawings

FIG. 1 is a schematic structural view of an anti-extrusion piston seal system of the present invention;

FIG. 2 is an enlarged view of portion A of FIG. 1;

FIG. 3 is an enlarged view of portion B of FIG. 2;

fig. 4 is a schematic diagram of a double acting seal of the prior art.

Reference numerals: 1. a piston; 2. a cylinder body; 3. a support groove; 4. a support ring; 5. a void; 6. a full retainer ring; 7. an inclined surface; 8. wave crest; 9. a trough of a wave; 10. a seal ring; 11. an elastic ring; 12. a half retaining ring; 13. a trapezoidal convex ring; 14. and (4) rubbing the protrusions.

Detailed Description

In the description of the present invention, it should be noted that, for the orientation words, such as the terms "center", "lateral (X)", "longitudinal (Y)", "vertical (Z)", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., the orientation and the positional relationship are indicated based on the orientation or the positional relationship shown in the drawings, and the description is only for convenience of describing the present invention and simplifying the description, but not for indicating or implying that the device or the element referred to must have a specific orientation, be constructed and operated in a specific orientation, and should not be construed as limiting the specific protection scope of the present invention.

Furthermore, if the terms "first" and "second" are used for descriptive purposes only, they are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features. Thus, the definition of "a first" or "a second" feature may explicitly or implicitly include one or more of the features, and "a plurality" or "a plurality" in the description of the invention means two or more unless a specific definition is explicitly provided.

The present invention is further explained with reference to fig. 1 to 4.

The utility model provides a hydraulic support stand is anti extrusion piston sealing system for hydro-cylinder, includes piston 1, be provided with the seal groove on the piston 1, be provided with two effect sealing members in the seal groove, be provided with a plurality of support grooves 3 on the piston 1, be provided with support ring 4 on the support groove 3, the external diameter of support ring 4 is greater than the diameter of piston 1.

As shown in fig. 1, before the piston 1 is matched with the cylinder 2, the support ring 4 is installed in the support groove 3, the double-acting sealing element is installed in the sealing groove, and then the piston 1 is installed on the cylinder 2, during installation, the outer surface of the support ring 4 is in contact with the cylinder 2, so that a gap is formed between the outer circular surface of the piston 1 and the cylinder 2, namely, the support ring 4 replaces the sliding friction of the piston 1 on the cylinder 2, and meanwhile, the gap between the piston 1 and the cylinder 2 is kept unchanged, the gap is prevented from being expanded, so that when a large load is borne on the piston 1, two half check rings 12 on the double-acting sealing element are prevented from being squeezed into the gap due to high pressure, and the service life of the hydraulic support is prolonged.

As shown in fig. 1, preferably, the number of the support grooves 3 is four, and two support grooves 3 are disposed on two sides of the double-acting sealing member, so that the gap between the two sides of the double-acting sealing member is uniform, which is beneficial to the operation of the piston 1.

As shown in fig. 3, preferably, a plurality of friction protrusions 14 are disposed on a side of the half retainer 12 that is in contact with the elastic ring 11 and the sealing ring 10, and when the half retainer 12 is subjected to pressure from the elastic ring 11 and the sealing ring 10, the friction protrusions 14 are embedded into the elastic ring 11 and the sealing ring 10 due to elasticity of the elastic ring 11 and the sealing ring 10, so that friction force between the half retainer 12 and the elastic ring 11 and the sealing ring 10 is increased, and the half retainer 12 is prevented from being extruded due to the force.

Preferably, the outer diameter of the support ring 4 is smaller than the outer diameter of the trapezoidal convex ring 13, so that when the piston 1 is installed in the cylinder 2, the elastic ring 11 is deformed, and the trapezoidal convex ring 13 has enough pressure to cling to the cylinder 2 through the deformation of the elastic ring 11, thereby performing a sealing function.

As shown in fig. 1, a gap 5 is provided between one side of the double-acting sealing element and the sealing groove, and the other side of the double-acting sealing element is in contact with the sealing groove, so that when the piston 1 operates to apply pressure to the half check ring 12, the half check ring 12 can be extruded out through the gap 5 to obtain a certain buffer, and the half check ring 12 is prevented from being extruded into the gap 5 between the piston 1 and the cylinder 2 after being applied with instantaneous high pressure.

As shown in fig. 1, a full retainer ring 6 is disposed between the double-acting sealing element and the sealing groove, and two sides of the full retainer ring 6 respectively contact with the double-acting sealing element and the sealing groove, and the full retainer ring 6 can share pressure applied to the half retainer ring 12, so as to prevent the half retainer ring 12 from being extruded under high pressure, and at the same time, the full retainer ring 6 extends from the bottom of the sealing groove to the opening of the sealing groove, so that the full retainer ring 6 has a large pressure-bearing capacity, and the full retainer ring 6 is prevented from being extruded under high pressure.

As shown in fig. 1, the cross section of the full retainer ring 6 in the preferred embodiment is in a shape of an inverted right trapezoid, and one side of the full retainer ring 6 that is in contact with the seal groove is an inclined surface 7, so that when the full retainer ring 6 is subjected to pressure, the force applied to the full retainer ring is transferred to the bottom of the seal groove, and the half retainer ring 12 and the full retainer ring 6 are further prevented from being extruded.

As shown in fig. 2, in the preferred embodiment, the upper surface of the trapezoidal boss is wavy, at least one wave trough 9 and two wave crests 8 are arranged on the wavy upper surface, when the piston 1 is mounted on the cylinder body 2, only the wave crest 8 is abutted against the cylinder body 2, and a cavity is formed between the wave trough 9 and the wide body, so that the contact area between the elastic ring 11 and the cylinder body 2 is reduced, the friction loss of the elastic body during the operation of the piston 1 is reduced, and the service life of the elastic body is prolonged.

As shown in fig. 1, the preferred support ring 4 of this embodiment is made of phenolic resin, which has high temperature resistance and improves the service life of the support ring 4.

As shown in fig. 1, the preferred sealing ring of this embodiment is nitrile rubber, which has better elasticity, and is beneficial to continuously providing elastic compensation for the half check ring 12 when the piston 1 is running, so as to prevent the half check ring 12 from being extruded.

As shown in fig. 1, the elastic ring 11 of the present embodiment is preferably made of polyurethane, which has better wear resistance and improves the service life of the elastic ring 11.

As shown in fig. 1, the half retainer ring 12 and the retainer ring of the present embodiment are preferably made of polyoxymethylene, which has strong pressure resistance and is not easily deformed after being pressed, so as to further prevent the half retainer ring 12 or the full retainer ring 6 from being extruded under pressure.

It is above only the utility model discloses a preferred embodiment, the utility model discloses a scope of protection does not only confine above-mentioned embodiment, the all belongs to the utility model discloses a technical scheme under the thinking all belongs to the utility model discloses a scope of protection. It should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.

Claims

1. The utility model provides a hydraulic support hydro-cylinder is with piston seal spare that reduces extrusion stress, includes the piston, is provided with the seal groove on the piston, is provided with two effect seal spare in the seal groove, its characterized in that: and a full check ring is arranged between the double-acting sealing element and the sealing groove, and two sides of the full check ring are respectively abutted to the double-acting sealing element and the sealing groove.

2. The hydraulic mount cylinder extrusion stress reducing piston seal of claim 1, further comprising: the cross-section of the full check ring is in an inverted right trapezoid shape, and one side of the full check ring, which is abutted to the sealing groove, is an inclined surface.

3. The hydraulic mount cylinder extrusion stress reducing piston seal of claim 2, further comprising: and a gap is arranged between the double-acting sealing element and the sealing groove.

4. The hydraulic mount cylinder extrusion stress reducing piston seal of claim 3, further comprising: the upper surface of the trapezoid boss is in a wave shape, and at least one wave trough and two wave crests are arranged on the upper surface of the wave shape.

5. The hydraulic mount cylinder extrusion stress reducing piston seal of claim 4, further comprising: and a plurality of friction bulges are arranged on the side surfaces of the half check rings, which are abutted against the elastic ring and the sealing ring.