CN210106593U - High-pressure reciprocating sealing structure - Google Patents
High-pressure reciprocating sealing structure Download PDFInfo
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- CN210106593U CN210106593U CN201920419382.XU CN201920419382U CN210106593U CN 210106593 U CN210106593 U CN 210106593U CN 201920419382 U CN201920419382 U CN 201920419382U CN 210106593 U CN210106593 U CN 210106593U
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Abstract
The utility model discloses a high-pressure reciprocating sealing structure, which comprises a sealing ring, an X-shaped sealing ring and an O-shaped sealing ring; the sealing ring is in a bilateral symmetry structure, one side of the sealing ring, which is contacted with the matching surface of the oil cylinder, is provided with a middle groove, the other side of the sealing ring is provided with a sealing bottom, and the left side and the right side of the sealing bottom are provided with sealing grooves; the X-shaped sealing ring is arranged in the middle groove, and the O-shaped sealing ring is arranged in the sealing groove; the sealing rings are positioned on two sides of the middle groove and are provided with sealing lips, and the sealing lips are in contact with the matching surface of the oil cylinder through a platform structure to form a multi-labyrinth sealing structure; as the piston moves leftwards or rightwards, the sealing lip on the corresponding side plays a main sealing role, so that bidirectional sealing is realized. The utility model discloses a bilateral symmetry sealing ring effectively cuts off the flow of high-pressure fluid and gas with the cooperation design of X type sealing washer and O type sealing washer, realizes zero leakage, guarantees that seal structure has reliable sealing performance and lower frictional force, and fatigue life is high satisfying under high pressure, the high low temperature environment of limit.
Description
Technical Field
The utility model relates to a sealing member field especially relates to a high pressure reciprocating seal structure.
Background
Along with the increasing demands for light weight, miniaturization and low energy consumption of mechanical structures, hydraulic systems are developing towards high pressure and high precision. The sealing and friction performance of the hydraulic sealing element becomes the key for determining the system performance, and particularly for high-precision servo oil cylinders, aerospace and other hydraulic systems, the sealing has high reliability under high pressure and high speed, the leakage does not occur after continuous long-time working, the friction force is small, the system efficiency is improved, and the energy consumption is reduced. However, the hydraulic sealing system used at present can only perform one-way sealing under 35MPa low pressure, such as steckel, U-shaped sealing, Y-shaped sealing and the like, if the two-way sealing needs to be combined for use, the structure is complex, the size is large, and inclination and degeneration are easy to occur in the movement process, so that the friction force is large, for the hydraulic system with the pressure higher than 35MPa, the friction force is large in the conventional sealing combination structure at present, the heating in the working process is serious, fatigue failure is easy to occur, so that leakage is easy to occur, and even serious accidents are caused. The method has the advantages that the national soil of China is wide, the temperature difference of the climate in the south and north is large, the reliable sealing is carried out in the extreme low-temperature and high-temperature environments in different seasons, and the method is the key for improving the performance and the working efficiency of the hydraulic system in China.
With the rapid development of the intelligent automobile industry in China, automatic driving becomes the development trend in the future, the most key core technology in automatic driving is a brake-by-wire system, no matter high-speed driving or urban working conditions, the intervention of the brake system is needed at any time, braking is a key system related to driving safety, high reliability and high-speed response characteristics are required, the bottom hardware of the system is a hydraulic brake cylinder, high-pressure sealing of the brake cylinder becomes a key component with the development of the brake system towards miniaturization, low power and high pressure, and at present, the vehicle enterprises in China mainly rely on imports, and have a large gap with foreign products in the aspects of reliability, pressurization and pressure maintaining performance.
In addition, the automobile industry in China is rapidly developed, the requirement of people on the riding comfort of automobiles is continuously improved, and the vibration isolation of automobile suspensions draws more and more attention of people. The suspension is a key component for isolating road excitation in the automobile driving process, the traditional passive suspension can not be adjusted after damping and rigidity design is finished, the smoothness and the operation stability of the whole automobile can not be considered, the oil-gas suspension has excellent vibration damping performance, high energy density, nonlinear rigidity damping characteristics and the like, and becomes an advanced automobile suspension system at present, so that the smoothness, the operation stability and the driving safety of the whole automobile under different working conditions of smooth road, off-road, no-load, full-load and the like of the automobile are effectively improved, and the floating piston in the oil-gas suspension has obvious advantages particularly for heavy vehicles, military vehicles and the like, is used for sealing and isolating high-pressure oil and high-pressure gas in a suspension oil cylinder, is the most core component of the oil-gas suspension, and determines the performance, the service life and the reliability of the.
The sealing structure provided by the patent can be used for hydraulic and gas sealing of two sides of the floating piston within 80MPa, is reliable in sealing under the conditions of high speed, high pressure and extreme high and low temperature, has lower friction force and long fatigue life, and is suitable for piston sealing and rod sealing in structural form.
SUMMERY OF THE UTILITY MODEL
The utility model discloses the main technical problem who solves provides a high pressure reciprocating seal structure, can solve floating piston both sides hydraulic pressure and gas seal and seal up the reliability problem under high-speed, high pressure and the high low temperature environment of limit.
In order to solve the technical problem, the utility model discloses a technical scheme be: there is provided a high pressure reciprocating seal structure comprising: the sealing ring, the X-shaped sealing ring and the O-shaped sealing ring; the sealing ring is of a bilateral symmetry structure, a middle groove is arranged in the middle of one side of the sealing ring, which is in contact with the matching surface of the oil cylinder, a sealing bottom is arranged at the position, opposite to the middle groove, of the other side of the sealing ring, and sealing grooves are symmetrically formed in the left side and the right side of the sealing bottom; the X-shaped sealing ring is arranged in the middle groove, and the O-shaped sealing rings are symmetrically arranged in the sealing groove; the sealing rings are positioned on two sides of the middle groove and are provided with symmetrically distributed sealing lips, and the sealing lips are in contact with the matching surface of the oil cylinder in a platform structure to form a multi-path labyrinth sealing structure; the sealing lip on the corresponding side plays a main sealing role as the piston moves leftwards or rightwards, so that bidirectional sealing is realized.
In a preferred embodiment of the present invention, the X-shaped sealing ring has an arc-shaped groove on both the side facing the cylinder fitting surface and the other side facing the middle groove; two opposite sides of the middle grooves of the X-shaped sealing ring and the left side and the right side are both of a plane structure.
In a preferred embodiment of the present invention, the width of the sealing bottom is greater than the width of the middle groove; the distance from the top of the sealing groove to the middle of the lower edge of the sealing bottom is 2/3-1 times of the diameter of the O-shaped sealing ring.
In a preferred embodiment of the present invention, the bottom two sides of the sealing bottom extend toward the sealing groove.
In a preferred embodiment of the present invention, the extending edge of the sealing bottom and the outer side edge of the sealing groove are rounded structures.
In a preferred embodiment of the present invention, the sealing ring is made of teflon; the X-shaped sealing ring and the O-shaped sealing ring are made of fluororubber, hydrogenated nitrile rubber or polyurethane, and the Shore hardness of the X-shaped sealing ring and the Shore hardness of the O-shaped sealing ring are 70-90.
In a preferred embodiment of the present invention, the front portion is formed along the moving direction, and a lip front angle and a lip rear angle are formed between the seal lip and the cylinder fitting surface, wherein the lip front angle is greater than the lip rear angle.
In a preferred embodiment of the present invention, the lip front foot is 30 to 80 °, and the lip back angle is 5 to 30 °.
In a preferred embodiment of the present invention, the length of the platform structure is 1-10 mm.
In a preferred embodiment of the present invention, the left and right sides of the sealing ring are in non-contact engagement with the piston.
The utility model has the advantages that: the utility model relates to a high-pressure reciprocating sealing structure, which can meet the function of left and right bidirectional sealing through the matching design of a left and right symmetrical sealing ring, an X-shaped sealing ring and an O-shaped sealing ring, can effectively cut off the flow of high-pressure oil and gas, and realizes zero leakage; through the design of the sealing bottom and the O-shaped sealing ring, enough resilience force and reliable sealing performance are provided for the sealing ring, the sealing structure is guaranteed to have reliable sealing performance and lower friction force under the condition of meeting the requirements of high-pressure and extreme high-low temperature environments, and the fatigue life is long.
Drawings
Fig. 1 is a schematic perspective view of a preferred embodiment 1 of a high-pressure reciprocating sealing structure according to the present invention;
fig. 2 is a schematic perspective view of a preferred embodiment 2 of a high-pressure reciprocating sealing structure according to the present invention;
fig. 3 is a schematic perspective view of a preferred embodiment 3 of a high-pressure reciprocating sealing structure of the present invention;
FIG. 4 is a deformation and stress cloud plot of the high pressure reciprocating seal structure of example 1;
FIG. 5 is a strain cloud of the high pressure reciprocating seal structure of example 1;
the parts in the drawings are numbered as follows: 1. the sealing device comprises a sealing ring, 2. an X-shaped sealing ring, 3. an O-shaped sealing ring, 4. an oil cylinder matching surface, 5. a middle groove, 6. a sealing bottom, 7. a sealing groove and 8. a sealing lip.
Detailed Description
The following detailed description of the preferred embodiments of the present invention will be provided in conjunction with the accompanying drawings, so as to enable those skilled in the art to more easily understand the advantages and features of the present invention, and thereby define the scope of the invention more clearly and clearly.
Referring to fig. 1-5, an embodiment of the present invention includes:
example 1
The utility model discloses a high pressure reciprocating seal structure, include:
the sealing ring 1 is made of a polytetrafluoroethylene composite material added with related additives, and has an ultralow friction coefficient. The sealing ring 1 is of a bilateral symmetry structure, a middle groove 5 is arranged in the middle of one side of the sealing ring, which is in contact with the oil cylinder matching surface 4, a sealing bottom 6 is arranged at the position, opposite to the middle groove 5, of the other side of the sealing ring, and sealing grooves 7 are symmetrically formed in the left side and the right side of the sealing bottom 6; the X-shaped sealing ring 2 is arranged in the middle groove 5, and the O-shaped sealing ring 3 is symmetrically arranged in the sealing groove 7; the sealing rings 1 are positioned on two sides of the middle groove 5 and are provided with symmetrically distributed sealing lips 8, and the sealing lips 8 are in contact with the oil cylinder matching surface 4 in a platform structure with the length of 1-10 mm to form a multi-path labyrinth sealing structure; the sealing lip on the corresponding side plays a main sealing role as the piston moves leftwards or rightwards, so that bidirectional sealing is realized.
Specifically, the extending edge of the sealing bottom 6 and the outer side edge of the sealing groove 7 are both in a rounded structure. Through the structural design of the fillet, the stress concentration caused by the contact of the fillet and the O-shaped sealing ring 3 in the movement process can be avoided, and the O-shaped sealing ring 3 is scratched.
The X-shaped sealing ring 2 is provided with arc-shaped grooves on one side facing the oil cylinder matching surface 4 and on the other side facing the middle groove 5, and the two sides of the X-shaped sealing ring 2 opposite to the middle grooves 5 on the left side and the right side are both of a planar structure. Specifically, the contact area and the sliding friction can be reduced by the structural design of the arc-shaped groove, when the outside sealing oil pressure is high, the outside oil pressure extrudes the outside of the X-shaped sealing ring in the movement process, so that the sealing contact pressure is increased, the sealing performance of the X-shaped sealing ring is improved along with the increase of the outside pressure, and the X-shaped sealing ring has a self-reinforcing sealing characteristic; the design of the plane structure can prevent stress concentration and fatigue failure, improve the reliability of the X-shaped sealing ring structure and improve enough pressing force.
The O-shaped sealing ring 3, the O-shaped sealing ring 3 and the X-shaped sealing ring 2 are made of fluororubber or hydrogenated nitrile rubber added with related additives, and the Shore hardness of the O-shaped sealing ring 3 and the X-shaped sealing ring 2 is 70-90. The O-shaped sealing ring 3 is assembled in a sealing groove 7 at the bottom of the sealing ring 1, and the initial interference of assembly is 10-30%. After initial assembly, the O-shaped sealing ring 3 deforms, the sealing lip 8 on the sealing ring 1 is pressed on the oil cylinder matching surface 4, certain abrasion occurs at the top of the sealing lip after long-time work, and the O-shaped sealing ring can compensate the abrasion loss. In addition, the O-shaped sealing ring can provide enough pressing force to keep reliable sealing under high oil pressure or air pressure, and the phenomenon that the sealing deflects during the movement of the piston to cause the increase of friction force is prevented. Through finite element simulation analysis, the maximum stress of the assembled sealing ring is 39MPa, the maximum stress occurs in the top area of the sealing lip, the structural stress is distributed reasonably, and no obvious stress concentration exists.
Under high pressure operating mode, 3 hardness of O type sealing washer are great, can provide sufficient holding power, and pressure is great between seal lip and the hydro-cylinder fitting surface 4, and the seal lip top design of sealing ring 1 is platform structure, and the length of designing platform structure according to sealing pressure's difference is 1~ 10mm, avoids area of contact too little to produce stress concentration, produces excessive wearing and tearing with the fitting surface contact.
In addition, the left side and the right side of the sealing ring 1 are in non-contact fit with the piston. Under extreme high, low temperature environment, because different materials thermal expansion coefficient is different, both sides clearance can prevent to take place the extrusion under extreme high temperature between the structure, influences sealed effect, avoids producing stress concentration and destruction simultaneously.
The utility model discloses a theory of operation does:
the sealing ring 1 and the oil cylinder matching surface 4 have 6 seals, are symmetrical left and right, and are expressed as follows by taking the left side as an example:
when the piston moves leftwards, the oil cylinder is relatively static, in order to prevent leakage of a left side sealing medium, the left side sealing has a main sealing function, three sealing lips are arranged on the left side of the middle groove 5 respectively, the specified moving direction is the front part, the sealing lips and the oil cylinder matching surface form a front lip angle and a rear lip angle, wherein the front lip angle (30-80 degrees) is larger than the rear lip angle (5-30 degrees), so that residual oil or gas can be effectively cut off to flow, and zero leakage is realized.
When the piston moves right, the hydro-cylinder is static relatively, for preventing that right side sealing medium from revealing, the right side is sealed and is played main sealing function, respectively has three seal lips at 5 right sides of middle recess, prescribes that to be anterior along the direction of motion, seal lip with form lip anterior angle and lip relief angle between the hydro-cylinder fitting surface, wherein, lip anterior angle (30 ~ 80 °) is greater than lip relief angle (5 ~ 30 °), can effectively cut off remaining fluid or gas flow, realize zero leakage.
The utility model discloses a two way seal's function is realized to symmetrical structure's sealing ring design.
In addition, a small gap is formed between the piston and the matching surface, a certain gap length is formed in the axial direction, so that the pressure transmitted to a sealing position in the oil cylinder is reduced, the piston and the matching surface are supported through a guide belt, the guide belt is made of low-friction polytetrafluoroethylene composite materials and provides radial supporting force, the piston and the sealing ring are kept to have good coaxiality, and the roughness requirement of the sealing matching surface is lower than Ra 0.5 micrometer.
The utility model discloses a seal structure, through finite element simulation analysis, normal operating temperature is under 100 ℃, and assembly back X type sealing washer and O type sealing washer are met an emergency cloud picture, and the biggest strain is 0.28, takes place in O type sealing washer central area and X type sealing washer bottom, and the sealing washer project organization is met an emergency at reasonable within range by the utmost, can effectively avoid fatigue failure.
Example 2
The difference from embodiment 1 is that the width of the sealing bottom 6 is greater than the width of the intermediate trench 5; the distance from the top of the sealing groove 5 to the middle of the lower edge of the sealing bottom 6 is 2/3-1 times of the diameter of the O-shaped sealing ring 3. Through the structural design of the sealing bottom 6 on the sealing ring 1, good rear support can be provided for the O-shaped sealing ring 3 in the dynamic sealing process, and the service life of the O-shaped sealing ring 3 is prolonged; the two side sealing grooves 7 can provide larger supporting force for the first sealing, and the sealing performance is improved. The two sides of the bottom of the sealing bottom 6 extend towards the sealing groove 7.
Example 3
The difference with embodiment 2 is that 4 seals are arranged on the sealing ring 1 and the oil cylinder matching surface 4, 2 seals are arranged on one side, after the sealing fluid passes through the second section of sealing gap, an obvious throttling effect is generated, the sealing pressure is rapidly reduced, the low-pressure fluid is sealed by the X-shaped sealing ring, and the sealing performance is good. The embodiment has the advantages of simple structure, low processing cost, high structural strength and lower risk of fatigue failure in long-time work.
The utility model discloses following beneficial effect has:
1. the sealing ring can effectively reduce the oil hydraulic pressure and the leakage amount through multi-stage labyrinth sealing, and the front lip angle is far greater than the rear lip angle, so that the pressure gradient near the front lip angle is greater than that of the rear lip angle, the oil reverse pumping effect in the reciprocating motion process is facilitated, and the sealing performance is improved; the clearance between the platform outside the sealing ring and the sealing surface is 0.001-0.1 mm, the phenomenon that the X-shaped sealing ring is extruded into the clearance of the sealing ring to be damaged at high speed or high pressure due to overlarge clearance, the friction force and the thermal stress are increased due to the overlarge clearance, meanwhile, only the sealing lip is in contact with the matching surface, the contact area is small, the increase of the contact friction force due to deflection in the motion process like a Stent seal is avoided, the friction force is greatly reduced while the sealing is reliable, and the dynamic response characteristic of the system can be obviously improved for the application of a servo valve, an oil-gas suspension and the like;
2. the pressure is greatly reduced after part of oil or gas passing through the sealing ring reaches the X-shaped sealing ring, the X-shaped sealing ring has self-enhanced sealing performance, the flow of the oil or gas can be effectively cut off, and zero leakage is realized; the X-shaped sealing ring has small contact area with the matching surface, so that the friction force in the movement process is effectively reduced, the structure is stable in the movement process, deflection cannot occur, the structural design is reasonable through structural thermal simulation analysis, the stress strain is lower under the assembly condition, and the fatigue reliability is good;
3. the sealing ring is supported by the two O-shaped rings at the bottom, the structure is stable, the O-shaped rings are always positioned in the grooves in the movement process by designing the oval grooves which are adaptive to the pre-compression deformation of the O-shaped rings, so that stable supporting force is provided, the O-shaped sealing rings are separated by the middle structure of the oval grooves at the bottom of the sealing ring, the O-shaped rings are prevented from being extruded mutually, and the service life of the O-shaped rings is prolonged;
4. the utility model has the advantages that the PTFE sealing ring and the X-shaped sealing ring are mutually matched to carry out multi-sealing to the high-pressure medium, the structure is compact, the axial length of the combined sealing is effectively shortened, the sealing performance and the reliability of the system are improved, and the friction force is reduced;
5. the sealing bottom can provide good rear support for the O-shaped ring in the dynamic sealing process, the service life of the O-shaped ring is prolonged, the O-shaped ring supporting grooves on the two sides can provide larger supporting force for the first sealing, and the sealing performance is improved; and the single-channel sealing structure is designed, so that the sealing structure has good sealing performance, simple structure, low processing cost and high reliability.
In the description of the present invention, it should be noted that the terms "upper", "lower", "left", "right", "inner", "outer", etc. indicate the position or positional relationship based on the position or positional relationship shown in the drawings, or the position or positional relationship that the products of the present invention are usually placed when used, and are only for convenience of description and simplification of the description, but do not indicate or imply that the device or element to which the term refers must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. A high pressure reciprocating seal structure, comprising: the sealing ring, the X-shaped sealing ring and the O-shaped sealing ring; the sealing ring is of a bilateral symmetry structure, a middle groove is arranged in the middle of one side of the sealing ring, which is in contact with the matching surface of the oil cylinder, a sealing bottom is arranged at the position, opposite to the middle groove, of the other side of the sealing ring, and sealing grooves are symmetrically formed in the left side and the right side of the sealing bottom; the X-shaped sealing ring is arranged in the middle groove, and the O-shaped sealing rings are symmetrically arranged in the sealing groove; the sealing rings are positioned on two sides of the middle groove and are provided with symmetrically distributed sealing lips, and the sealing lips are in contact with the matching surface of the oil cylinder in a platform structure to form a multi-path labyrinth sealing structure; the sealing lip on the corresponding side plays a main sealing role as the piston moves leftwards or rightwards, so that bidirectional sealing is realized.
2. The high-pressure reciprocating sealing structure according to claim 1, wherein one side of the X-shaped sealing ring facing the oil cylinder matching surface and the other side facing the middle groove are both provided with circular arc-shaped grooves; two opposite sides of the middle grooves of the X-shaped sealing ring and the left side and the right side are both of a plane structure.
3. The high pressure reciprocating seal structure of claim 1, wherein the seal bottom has a width greater than a width of the intermediate groove; the distance from the top of the sealing groove to the middle of the lower edge of the sealing bottom is 2/3-1 times of the diameter of the O-shaped sealing ring.
4. The high pressure reciprocating seal structure of claim 3, wherein both sides of the bottom of the seal bottom extend in the direction of the seal groove.
5. The high pressure reciprocating seal structure of claim 4, wherein the extending edge of the seal bottom and the outer side edge of the seal groove are rounded off.
6. A high pressure reciprocating seal structure according to any of claims 1-3, wherein the seal ring is polytetrafluoroethylene; the X-shaped sealing ring and the O-shaped sealing ring are made of fluororubber, hydrogenated nitrile rubber or polyurethane, and the Shore hardness of the X-shaped sealing ring and the Shore hardness of the O-shaped sealing ring are 70-90.
7. The high pressure reciprocating seal structure of claim 1, wherein the forward portion is along the direction of motion, and a lip front angle and a lip rear angle are formed between the seal lip and the cylinder mating surface, wherein the lip front angle is greater than the lip rear angle.
8. The high pressure reciprocating seal structure of claim 7, wherein the lip front angle is 30-80 ° and the lip rear angle is 5-30 °.
9. The high pressure reciprocating seal structure of claim 1, wherein the platform structure has a length of 1-10 mm.
10. The high pressure reciprocating seal structure of claim 1, wherein the left and right sides of the seal ring are in non-contact engagement with the piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920419382.XU CN210106593U (en) | 2019-03-29 | 2019-03-29 | High-pressure reciprocating sealing structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920419382.XU CN210106593U (en) | 2019-03-29 | 2019-03-29 | High-pressure reciprocating sealing structure |
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| Publication Number | Publication Date |
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| CN210106593U true CN210106593U (en) | 2020-02-21 |
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| CN201920419382.XU Expired - Fee Related CN210106593U (en) | 2019-03-29 | 2019-03-29 | High-pressure reciprocating sealing structure |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110005816A (en) * | 2019-03-29 | 2019-07-12 | 清华大学 | A kind of high pressure reciprocation sealing structure |
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2019
- 2019-03-29 CN CN201920419382.XU patent/CN210106593U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110005816A (en) * | 2019-03-29 | 2019-07-12 | 清华大学 | A kind of high pressure reciprocation sealing structure |
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