CN114857273B - End face seal assembly - Google Patents

End face seal assembly Download PDF

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Publication number
CN114857273B
CN114857273B CN202210346368.8A CN202210346368A CN114857273B CN 114857273 B CN114857273 B CN 114857273B CN 202210346368 A CN202210346368 A CN 202210346368A CN 114857273 B CN114857273 B CN 114857273B
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China
Prior art keywords
face
pressure side
circumferential groove
radial
groove
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CN114857273A (en
Inventor
黄伟峰
高文彬
刘莹
李德才
李永健
郭飞
晋立丛
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Tsinghua University
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Tsinghua University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3268—Mounting of sealing rings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Sealing (AREA)

Abstract

The invention discloses an end face seal assembly, which comprises: a first seal ring formed with a first end face; a second seal ring which is provided with a second end face opposite to the first end face, and a seal gap extending from a high pressure side to a low pressure side is formed between the first end face and the second end face; wherein at least one of the first end face and the second end face is formed with a circumferential groove located between the high pressure side and the low pressure side to control potential locations of fluid phase change within the seal gap. According to the end face sealing assembly, pressure distribution in a sealing gap can be improved, potential positions of fluid phase change are controlled, a lubrication area is enlarged, abrasion can be effectively reduced even if phase change occurs, and the service life of the end face sealing assembly is remarkably prolonged.

Description

End face seal assembly
Technical Field
The invention relates to the technical field of mechanical sealing, in particular to an end face sealing assembly.
Background
Mechanical seal face structures are a fundamental key component in various rotary fluid machines. The mechanical seal is a device with less fluid leakage, which keeps the sealing rings to be jointed and relatively slide under the combined action of the end face fluid pressure vertical to the rotation axis, the action of the compensation element and the auxiliary seal. The common mechanical end face seal has relatively mature sealing end face and structural design for sealing a gas medium and a liquid medium. With the development of sealing technology and the extension of sealing application media, there are also deficiencies and gaps in the related designs for media applications where phase changes may occur on both sides of the seal due to pressure and temperature differences. Basically, the application scenario is that the medium is kept in a liquid state under a certain temperature and pressure in the sealed cavity, and is changed into a vapor phase under the condition outside the seal. Therefore, phase transformation usually occurs on the sealing end face, if the phase transformation is not controlled by adopting a targeted design, if the medium completely undergoes the phase transformation in the sealing gap, the sealing may not work effectively, and even failure or accident occurs. For this case, it is more common to have a contact mechanical end face seal, the end face of which is not provided with any groove-type, substantially flat end face. The mechanical seal utilizing the fluid dynamic pressure effect is often provided with dynamic pressure shallow grooves according to the rotation direction of the end face, such as spiral shallow grooves with the depth of several micrometers to tens of micrometers, and the advantages of friction and wear improvement and leakage rate control can be achieved. However, in the case where the rotation direction needs to be considered, the advantages of the dynamic pressure grooves are reduced even at a low speed, and the seal may fail in the case of a medium phase change. At the same time, the processing cost of the shallow grooves capable of providing dynamic pressure is often relatively high. The present application is directed to an end face seal assembly that addresses the above-described issues.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems existing in the prior art. Therefore, an object of the present invention is to provide an end face seal assembly, which can improve the pressure distribution in the seal gap, control the potential position of fluid phase transition, enlarge the lubrication area, and effectively reduce wear even if phase transition occurs, and significantly improve the service life of the end face seal assembly.
The end face seal assembly according to the present invention comprises: a first seal ring formed with a first end face; a second seal ring which is provided with a second end face opposite to the first end face, and a seal gap extending from a high pressure side to a low pressure side is formed between the first end face and the second end face; and at least one of the first end face and the second end face is provided with a circumferential groove, and the circumferential groove is positioned between the high pressure side and the low pressure side so as to control the position of fluid phase change in the sealing gap.
The end face sealing assembly has the advantages that after fluid flows into the sealing gap from the high-pressure side to the low-pressure side, the pressure in the sealing gap is gradually reduced along the radial direction, and as the circumferential groove is formed in at least one of the first end face and the second end face, the pressure of the fluid stops reducing after the fluid flows into the circumferential groove, so that the pressure of the fluid is stabilized in a range, the end face sealing assembly has the capability of controlling the pressure of the fluid in the sealing gap to be higher than the saturated vapor pressure of the fluid, the potential position of phase change is controlled, the lubrication area is enlarged, the abrasion is effectively reduced, and the service life of the end face sealing assembly is remarkably prolonged.
According to some embodiments of the invention, at least one of the first end face and the second end face is provided with a radial groove extending from the high pressure side to the low pressure side.
According to some embodiments of the invention, the radial groove is configured in a plurality, and the plurality of radial grooves are arranged at intervals in a circumferential direction of the first end face and/or the second end face.
According to some embodiments of the invention, the radial slot comprises: a plurality of first radial grooves configured adjacent to the high pressure side, the plurality of first radial grooves being arranged at intervals in a circumferential direction; and second radial grooves configured in a plurality adjacent to the low pressure side, the plurality of second radial grooves being circumferentially spaced apart, the first radial grooves being circumferentially staggered with the second radial grooves.
According to some embodiments of the invention, a sidewall of the circumferential groove adjacent the low pressure side communicates with an end of each of the first radial grooves adjacent the high pressure side.
According to some embodiments of the invention, the circumferential groove comprises a plurality of circumferentially spaced apart connection segments, each of the connection segments being in communication with one or more first radial grooves.
According to some embodiments of the invention, the circumferential groove is configured in a plurality and comprises: a first circumferential groove disposed adjacent the high pressure side and in communication with each of the first radial grooves; and a second circumferential groove disposed adjacent to the low pressure side and communicating with each of the second radial grooves.
According to some embodiments of the invention, the inner wall surfaces of the circumferential groove and the radial groove are configured as flat surfaces or curved surfaces.
According to some embodiments of the invention, the circumferential groove has a depth d1, the radial groove has a depth d2, and: d1 is more than or equal to 0.05mm and less than or equal to 2mm, d2 is more than or equal to 0.05mm and less than or equal to 2mm.
According to some embodiments of the invention, the circumferential groove has a width D1, the radial groove has a width D2, and: d1 is more than or equal to 0.1mm and less than or equal to 2mm, D2 is more than or equal to 0.1mm and less than or equal to 2mm.
According to some embodiments of the invention, the circumferential groove is configured as a plurality of wave segments, fold segments or curves that are circumferentially continuous.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:
FIG. 1 is a schematic illustration of the configuration of an end face seal assembly according to one embodiment of the present invention;
FIG. 2 is a schematic illustration of an end face seal assembly according to another embodiment of the present invention;
FIG. 3 is a schematic illustration of an end face seal assembly according to another embodiment of the present invention;
FIG. 4 is a schematic illustration of the configuration of an end face seal assembly according to another embodiment of the present invention;
FIG. 5 is a schematic plan view of a circumferential groove and a radial groove of one embodiment of the present invention;
FIG. 6 is a schematic plan view of a circumferential groove and a radial groove of another embodiment of the present invention;
FIG. 7 is a schematic plan view of a circumferential groove and a radial groove of another embodiment of the present invention;
FIG. 8 is a schematic plan view of a circumferential groove and a radial groove of another embodiment of the present invention;
FIG. 9 is a schematic plan view of a circumferential groove and a radial groove of another embodiment of the present invention;
FIG. 10 is a schematic representation of the end face partial deformation results of an end face seal assembly according to one embodiment of the present invention.
Reference numerals:
1: a shaft; 2: a housing; 3: a first seal ring; 4: a second seal ring; 5: a first radial slot; 6: a first circumferential groove; 7: a second radial slot; 8: a second circumferential groove.
Detailed Description
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may communicate with each other; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature. An end face seal assembly according to an embodiment of the present invention is described below with reference to fig. 1-10.
For medium application which can generate phase change on two sides of the seal due to different pressure and temperature, contact type mechanical end face seal is more common, the end face of the seal is not provided with any groove type, basically a flat end face, and the seal end face is more worn and has shorter service life. Some non-contact end face sealing end faces are designed with shallow grooves locally, the mechanical seal utilizing the fluid dynamic pressure effect is often provided with the dynamic pressure shallow grooves according to the rotation direction of the end faces, most of traditional dynamic pressure grooves have directionality, the advantages of the dynamic pressure grooves can be reduced under the condition that the rotation direction needs to be compatible or the rotation direction needs to be low, the sealing is likely to be invalid under the condition that the medium changes phase, and meanwhile, the processing cost for manufacturing the shallow grooves is often higher. The present application is directed to designing an end face seal assembly to address the above-described technical problems to a certain extent.
An end face seal assembly according to an embodiment of the present invention is described below with reference to fig. 1-10.
According to the end face seal assembly of the present invention, referring to fig. 1, the end face seal assembly includes a first seal ring 3 and a second seal ring 4, the first seal ring 3 is formed with a first end face, the second seal ring 4 is formed with a second end face facing the first end face, and a seal gap extending from a high pressure side H to a low pressure side L is formed between the first end face and the second end face; wherein at least one of the first end surface and the second end surface is provided with a circumferential groove, and the circumferential groove is positioned between the high pressure side H and the low pressure side L to control the position of fluid phase change in the sealing gap.
It is known to those skilled in the art that for a fluid flowing within a seal gap there will be a decrease in along-line pressure in the direction of flow, the extent of the pressure decrease being inversely proportional to the dimension of the seal gap, the greater the dimension of the seal gap, the lesser the extent of the pressure decrease. In the end face sealing assembly provided by the invention, the circumferential groove is formed on at least one of the first end face and the second end face, the circumferential groove can be configured as an annular groove surrounding the rotation center of the first sealing ring 3 or the rotation center of the second sealing ring 4, fluid flows into the sealing gap from the high pressure side H to the low pressure side L, the pressure in the gap also decreases along the radial direction, after the fluid flows into the circumferential groove, the fluid flow path is widened, the pressure loss of the sealing end face is greatly reduced, namely, the pressure of the fluid stops decreasing after flowing into the circumferential groove, and the pressure of the fluid is stabilized above the saturated vapor pressure of the fluid. Therefore, according to the design of different media and working conditions, the phase change between the inner radius of the circumferential groove and the outer radius of the end faces opposite to the first sealing ring 3 and the second sealing ring 4 can be avoided as much as possible, the potential position of the phase change is controlled, and the vaporization position is limited in a limited area.
According to some embodiments of the present invention, when the end face seal assembly is used for a rotary machine seal, the rotary machine further comprises a shaft 1 and a housing 2, the bottom of the housing 2 is perforated, the shaft 1 of the rotary machine passes through the hole, the housing 2 is fixedly connected with a first seal ring 3, the first seal ring 3 is formed with a first end face, a second seal ring 4 is connected with the shaft 1 and can rotate around the shaft 1, the second seal ring 4 is formed with a second end face, and the first end face of the first seal ring 3 is in face fit with the second end face of the second seal ring 4. It should be noted that, the operation states of the first seal ring 3 and the second seal ring 4 are not particularly limited, and the second seal ring may be fixedly connected to the housing 2, the first seal ring 3 rotates around the shaft 1, a high pressure area is formed outside the first seal ring 3 and the second seal ring 4 in the housing 2, a low pressure area is formed between the shaft body and the first seal ring 3 and the second seal ring 4, and a medium in the high pressure area in the housing 2 may enter the low pressure area through a seal gap so as to lubricate and improve the bearing capacity between the first seal ring 3 and the second seal ring 4 when the first seal ring 3 and the second seal ring 4 rotate relatively.
According to some embodiments of the present invention, the number and positions of the circumferential grooves are not particularly limited, and the circumferential grooves may be formed only on the first seal ring 3, or only on the second seal ring 4, or on both the first seal ring 3 and the second seal ring 4.
According to some embodiments of the invention, at least one of the first end face and the second end face is provided with a radial groove extending in the high pressure side to the low pressure side. In particular, the radial grooves may be provided only on the first end face, or only on the second end face, or both the first end face and the second end face. Therefore, the pressure of the fluid stops to be reduced after flowing into the circumferential groove, the radial groove can further stabilize the pressure of the fluid in a wider range, phase change caused by the fact that the pressure of the fluid is reduced to the saturated vapor pressure of the liquid is avoided, the pressure reduction of the fluid in the sealing gap is further controlled, meanwhile, the actual end face specific pressure of the sealing is reduced, and the bearing capacity of the sealing is further improved.
The bearing force includes two parts, namely, integral of pressure distribution of fluid in the gap and contact force when solid contacts, and the specific pressure of the end face refers to the ratio of the solid contact force to the sealing bearing force. The radial grooves can stabilize the fluid pressure in a wider range, so that the reduction of the fluid pressure is avoided to a certain extent, and the integral area of the pressure distribution of the fluid in the sealing gap is increased, which is equivalent to the increase of the sealing bearing capacity, namely the reduction of the end face specific pressure.
The person skilled in the art knows that when the end face seal assembly is used for rotating mechanical seal, the start-stop stage speed is lower, the end face seal assembly is simultaneously provided with a circumferential groove and a radial groove, under the condition of no rotation, the end face specific pressure can be small and also has a certain bearing capacity, so that the end face can be protected at the seal start-stop stage through arranging the radial groove, friction is avoided, and the end face seal assembly is suitable for various low, medium and high rotating speeds while effectively controlling the leakage rate through parameterized design. Meanwhile, due to the symmetrical design of the circumferential groove and the radial groove, the end face sealing assembly can be suitable for various rotation directions and is not limited by a single rotation direction any more.
In some embodiments, the radial groove is configured as a connecting groove extending radially along the first seal ring 3 or the second seal ring 4, the direction of extension of the radial groove passing through the center of rotation of the first seal ring 3 or the second seal ring 4.
According to some embodiments of the present invention, the positions of the radial groove and the circumferential groove on the seal ring are not particularly limited, for example, referring to fig. 1, the radial groove and the circumferential groove may each be provided on the second seal ring 4; referring to fig. 2, both radial grooves and circumferential grooves may be provided on the first seal ring 3; referring to fig. 3, radial grooves are provided on the second seal ring 4, and circumferential grooves are provided on the first seal ring 3; referring to fig. 4, radial grooves are provided on the first seal ring 3 and circumferential grooves are provided on the second seal ring 4, which can be selected according to actual needs by those skilled in the art.
According to some embodiments of the invention, referring to fig. 5-9, the radial groove may be configured in plurality, and the plurality of radial grooves are spaced apart in a circumferential direction of the first end face and/or the second end face. Specifically, a plurality of radial grooves may be disposed only on the first end surface, or a plurality of radial grooves may be disposed only on the second end surface, and preferably, a plurality of radial grooves are disposed uniformly on the first end surface and the second end surface, and by disposing the radial grooves on the end surfaces, it is possible to maintain the pressure above the liquid saturation vapor pressure when the fluid flows through the radial grooves on the first end surface or the second end surface, and thereby control the region in the sealed gap where the phase change of the medium occurs.
According to some embodiments of the present invention, referring to fig. 5-9, the radial slots may further include a first radial slot 5 and a second radial slot 7, wherein the first radial slot 5 is configured as a plurality of first radial slots 5 spaced apart in a circumferential direction adjacent to the high pressure side H; the second radial grooves 7 are configured in plural adjacent to the low pressure side L, the plural second radial grooves 7 are arranged at intervals in the circumferential direction, and the first radial grooves 5 are staggered in the circumferential direction with the second radial grooves 7. Specifically, a plurality of first radial grooves 5 are arranged on the high pressure side H, a plurality of second radial grooves 7 are arranged on the low pressure side L, the second radial grooves 7 are opposite to gaps formed by two adjacent first radial grooves 5 to form comb-tooth type radial grooves, under the combined action of pressure and temperature in the end face gaps, referring to fig. 10, the radial grooves can generate periodic deformation on the end face, namely end face waviness deformation, in the rotating process, fluid flows through the gaps with waviness, dynamic pressure effect of corresponding degree is generated in the gaps, and bearing capacity of sealing is effectively improved so as to adapt to severe working conditions such as high temperature, high pressure and high speed.
According to some embodiments of the invention, the radial grooves and the circumferential grooves may be non-communicating or communicating, and with reference to fig. 1 and 5, the side wall of the circumferential groove adjacent to the low pressure side L communicates with one end of each first radial groove 5 adjacent to the high pressure side H. Specifically, the first end face of the first seal ring 3 and the second end face of the second seal ring 4 are opposite, the first seal ring 3 is a rotating ring, the second seal ring 4 is a stationary ring, the former can rotate relative to the latter, the outer side of the end face is the high pressure side, i.e. the upstream H, and the inner side of the end face is the low pressure side, i.e. the downstream L. Under the influence of the given pressure, the fluid flows from the upstream H to the downstream L in the direction of the arrow G, with a consequent reduction of the pressure in the sealing gap. A first radial groove 5, a second radial groove 7 and a circumferential groove are provided at a first end face of the rotating ring. The pressure between the end faces from the circumferential groove to the end of the radial groove can be maintained at a certain level, thereby limiting the occurrence of phase changes. In addition, a planar annulus, i.e., the annulus between R1 and R3, is located outside of the circumferential groove, and acts as a throttle and park seal, which may be referred to as a seal dam. The inner radii of the first end face and the second end face, where the first seal ring 3 and the second seal ring 4 are opposite to each other, are R0, the outer radii of the first end face and the second end face, where the first seal ring 3 and the second seal ring 4 are opposite to each other, where R1 is the outer radius of the first end face and the second end face, where the second seal ring 4 are opposite to each other, R2 is the inner radius of the circumferential groove, R3 is the outer radius of the circumferential groove, R4 is the inner radius of the first radial groove 5, R5 is the outer radius of the second radial groove 7, and Rb is the equilibrium radius.
According to some embodiments of the invention, the circumferential groove may be continuous or discontinuous. For example, referring to fig. 6, the circumferential groove may include a plurality of connection segments arranged at intervals in the circumferential direction, each connection segment communicating with one or more first radial grooves 5.
According to some embodiments of the invention, referring to fig. 5, the circumferential groove may be further configured in a plurality and include: a first circumferential groove 6 and a second circumferential groove 8, wherein the first circumferential groove 6 is provided adjacent to the high pressure side H and communicates with each first radial groove 5, and the second circumferential groove 8 is provided adjacent to the low pressure side and communicates with each second radial groove 7.
According to some embodiments of the present invention, referring to fig. 5 and 6, the inner wall surfaces of the circumferential groove and the radial groove may be configured to be planar, and referring to fig. 7 and 8, the inner wall surfaces of the circumferential groove and the radial groove may be further configured to be curved.
According to some embodiments of the invention, referring to fig. 3, the depth d1 of the circumferential groove may be constant or may be varied. Alternatively, the circumferential groove may be the same depth in the entire circumferential direction, in which case the depth d1 of the circumferential groove is constant; the depth of the circumferential groove in the circumferential direction may also vary periodically, e.g. every 60 degrees, the circumferential groove having a variation of waviness, the depth d1 of the circumferential groove satisfying 0.05 mm.ltoreq.d1.ltoreq.2mm according to some embodiments of the present invention. Therefore, compared with the shallow grooves, the circumferential grooves adopt deep grooves, the deep grooves are more in processing modes, more in processing modes and more in available processing modes, the requirements of the deep grooves on precision are relatively tolerant, and the production cost can be reduced to a certain extent.
According to some embodiments of the invention, referring to fig. 4, the depth d2 of the radial groove may be constant or may be varied. Alternatively, the bottom surface of the radial groove may be planar, in which case the depth d2 of the radial groove is constant; the bottom surface of the radial groove may also be beveled, where the depth of the radial groove varies, and according to some embodiments of the invention, the depth d2 of the radial groove satisfies 0.05mm 2. Therefore, the radial grooves adopt deep grooves, compared with the shallow grooves, the deep grooves are processed in a relatively large number of ways, the applicable process means are relatively large in number, the requirements of the deep grooves on the precision are relatively tolerant, and the production cost can be reduced to a certain extent.
According to some embodiments of the invention, referring to fig. 5, the width D1 of the circumferential groove may be constant or may be varied. Alternatively, the width of the circumferential groove is uniform over the entire circumference, or the bottom to the notch of the circumferential groove is of a closed type or an open type, in which case the width of the circumferential groove in the radial direction is varied, and according to some embodiments of the present invention, the width D1 of the circumferential groove satisfies 0.1 mm.ltoreq.D1.ltoreq.2 mm.
According to some embodiments of the invention, referring to fig. 5, the width D2 of the radial slot may be constant or may be varied. Alternatively, the width of the bottom of the radial groove to the width of the notch may be uniform, or the bottom of the radial groove to the notch may be of a closed type or an open type, in which case the width of the radial groove varies. According to some embodiments of the invention, the width D2 of the radial slot satisfies 0.1 mm.ltoreq.D1.ltoreq.2 mm.
According to some embodiments of the present invention, the shape and configuration of the circumferential groove are not particularly limited, and may be a plurality of wave segments, fold segments or curves that are continuous in the circumferential direction to accommodate different conditions. As shown in fig. 7 and 8, the first circumferential groove may be configured in a wavy shape, and the second circumferential groove may be configured in a wavy shape, and depending on the sizes of the first seal ring 3 and the second seal ring 4, and the kinds of different mediums and the distribution of the high pressure side and the low pressure side, wavy circumferential grooves protruding toward the radially outer portion may be provided, or wavy circumferential grooves protruding toward the inner portion may be provided. The circumferential groove is in a wavy shape, so that the range of fluid pressure maintained by the circumferential groove is larger, the circumferential groove has the effect achieved by a certain radial groove, and the range of fluid pressure change controlled by the circumferential groove is enlarged. In the machining process, the efficiency of machining the wavy circumferential groove is high compared with the machining of the annular circumferential groove and the radial groove at the same time.
In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.

Claims (8)

1. An end face seal assembly, comprising:
a first seal ring formed with a first end face;
a second seal ring which is provided with a second end face opposite to the first end face, and a seal gap extending from a high pressure side to a low pressure side is formed between the first end face and the second end face; wherein the method comprises the steps of
At least one of the first end surface and the second end surface is provided with a circumferential groove, and the circumferential groove is positioned between a high pressure side and a low pressure side so as to control the position of fluid phase change in the sealing gap;
at least one of the first end surface and the second end surface is provided with a radial groove extending from the high pressure side to the low pressure side;
the radial grooves are configured in a plurality, and the plurality of radial grooves are arranged at intervals in the circumferential direction of the first end face and/or the second end face;
the radial slot includes:
a plurality of first radial grooves configured adjacent to the high pressure side, the plurality of first radial grooves being arranged at intervals in a circumferential direction;
and second radial grooves configured in a plurality adjacent to the low pressure side, the plurality of second radial grooves being circumferentially spaced apart, the first radial grooves being circumferentially staggered with the second radial grooves.
2. The face seal assembly of claim 1 wherein a sidewall of said circumferential groove adjacent the low pressure side communicates with an end of each of said first radial grooves adjacent the high pressure side.
3. The face seal assembly of claim 1 wherein said circumferential groove comprises a plurality of circumferentially spaced apart connection segments, each of said connection segments communicating with one or more first radial grooves.
4. The face seal assembly of claim 1 wherein said circumferential groove is configured in a plurality and comprises:
a first circumferential groove disposed adjacent the high pressure side and in communication with each of the first radial grooves;
and a second circumferential groove disposed adjacent to the low pressure side and communicating with each of the second radial grooves.
5. The face seal assembly of claim 1 wherein the inner wall surfaces of the circumferential groove and the radial groove are configured as flat or curved surfaces.
6. The face seal assembly of claim 1, wherein the circumferential groove has a depth d1 and the radial groove has a depth d2, and wherein: d1 is more than or equal to 0.05mm and less than or equal to 2mm, d2 is more than or equal to 0.05mm and less than or equal to 2mm.
7. The face seal assembly of claim 1, wherein the circumferential groove has a width D1 and the radial groove has a width D2, and wherein: d1 is more than or equal to 0.1mm and less than or equal to 2mm, D2 is more than or equal to 0.1mm and less than or equal to 2mm.
8. The face seal assembly of any one of claims 1-7, wherein the circumferential groove is configured as a plurality of circumferentially continuous wave segments, fold segments, or curves.
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