CN113028065B

CN113028065B - Sealing device

Info

Publication number: CN113028065B
Application number: CN202110307251.4A
Authority: CN
Inventors: 陆俊杰; 王天瑞; 张炜; 高德; 张学昌; 许少锋
Original assignee: Zhejiang University of Science and Technology ZUST
Current assignee: Zhejiang University of Science and Technology ZUST
Priority date: 2021-03-23
Filing date: 2021-03-23
Publication date: 2023-08-04
Anticipated expiration: 2041-03-23
Also published as: CN113028065A

Abstract

The invention discloses a sealing device, which comprises a movable ring component sleeved outside a rotating shaft and a stationary ring component fixed at the end part of a sealing cavity, wherein the stationary ring component comprises a stationary ring, a stationary ring seat and a reverse L-shaped pushing cylinder; one end of the static ring, which is away from the static sealing surface, is sealed and slidably matched in the first mounting groove, the tail part of the static ring abuts against the other end of the pressure plate, and the sealing surface of the static ring is attached to the sealing surface of the movable ring assembly. The sealing device disclosed by the invention has the advantages of simple structure and stable performance, and can be suitable for working conditions of high pressure and high rotating speed.

Description

Sealing device

Technical Field

The invention relates to the technical field of rotary shaft sealing, in particular to a sealing device.

Background

The supercritical carbon dioxide Brayton cycle power generation system is a revolutionary innovative technology, wherein turbine equipment belongs to core equipment of the system, and compared with a traditional power generation system, the supercritical carbon dioxide turbine equipment needs to solve the sealing problem of working media at high rotation speed, high pressure and high temperature, and the operation state of the turbine equipment is directly influenced by the sealing effect, so that the efficiency of the supercritical carbon dioxide Brayton cycle power generation is further determined. However, the traditional cylindrical labyrinth seal, contact mechanical seal and the like have the problems of serious end face abrasion, serious high-pressure high-temperature deformation, large leakage quantity, incapability of adapting to stable operation under high rotation speed and the like, and cannot be suitable for high-energy density supercritical carbon dioxide turbine equipment, and meanwhile, the sealing faces working conditions of more than 50000r/min, 20MPa and 500 ℃ and the sealing device and the sealing technology with extremely strong shaft end sealing capability of the supercritical carbon dioxide turbine equipment are not disclosed at present.

Disclosure of Invention

The technical problems to be solved by the invention are as follows: in order to overcome at least one technical defect in the prior art, the invention aims to provide a sealing device which is specially applied to shaft end equipment of supercritical carbon dioxide turbine equipment.

The technical scheme adopted by the invention is as follows: the sealing device comprises a movable ring assembly and a stationary ring assembly, wherein the movable ring assembly is sleeved outside a rotating shaft, the stationary ring assembly is fixed at the end part of a sealing cavity and comprises a stationary ring, a stationary ring seat and a reverse L-shaped pushing cylinder, a first mounting groove is formed in one end of the stationary ring seat, which is close to the movable ring assembly, the reverse L-shaped pushing cylinder comprises a sleeve and a pressure plate convexly arranged on the outer side wall of one end of the sleeve, the outer side wall of the sleeve is in sealing fit with the inner side of the stationary ring seat, and the pressure plate is in sliding fit with the bottom of the first mounting groove; the one end that quiet ring deviates from quiet sealed face is sealed and slidable cooperation is in first mounting groove, just the afterbody of quiet ring leans on with the other end of pressure disk, the sealed face of quiet ring is laminated with the sealed face of moving ring subassembly.

Compared with the prior art, the invention has the following advantages:

the static ring component of the sealing structure adopts the reverse L-shaped pushing cylinder to replace the traditional pushing ring, the pushing ring is blocked in the static ring seat due to the fact that the traditional pushing ring structure is easy to linearly expand or deform under high pressure, the pushing ring structure is unfavorable for flexible matching of the sealing ring under high pressure, the sealing ring of the pushing ring is easy to extrude, but the reverse L-shaped pushing cylinder of the sealing device of the novel design has strong bearing capacity, large deformation is prevented under high pressure, the sealing ring is pressed more uniformly, a pressure-holding phenomenon is not easy to exist, good axial following property is provided, and the sealing compensation ring can realize stable independent regulation and control capacity.

Further, the movable ring assembly comprises a movable ring and a movable ring seat, the movable ring seat is sealed and sleeved outside the rotating shaft, a second installation groove which is annular and axially opened is formed in the outer portion of the movable ring seat, the movable ring is assembled in the second installation groove, the inner side wall of the movable ring is in sealing fit with one side wall of the second installation groove, and a gap is reserved between the outer side wall of the movable ring and the other side wall of the second installation groove. In the structure, the inner side of the movable ring is in interference fit with the movable ring seat, and a gap is reserved between the outer side of the movable ring and the movable ring seat, so that the movable ring is prevented from extrusion deformation between the excessive linear expansion and the matching surface of the movable ring seat under high speed, high pressure and high temperature, and the sealing performance is prevented from being influenced.

As an improvement, the movable ring seat is also provided with a positioning component for axially limiting the end face of the movable ring. The positioning assembly drives the movable ring to play a certain limiting role except when the movable ring is installed, and can also effectively prevent the movable ring from excessively large linear expansion under high speed, high pressure and high temperature, so that the stable operation of the sealing rotary ring under high rotation speed is ensured.

Preferably, the positioning assembly comprises a positioning sleeve, the positioning sleeve is sleeved at one end of the movable ring seat close to the stationary ring, and a micro-gap of 0.03-0.05mm is reserved between the end part of the positioning sleeve and the end face of the movable ring.

And when the adjusting bolts are arranged in the threaded holes, the distance between the positioning sleeve and the end face of the movable ring is adjusted by screwing the adjusting bolts. The distance between the positioning sleeve and the end face of the movable ring seat is realized by screwing the adjusting bolt, so that the accurate adjustment of the distance between the end face of the positioning sleeve and the end face of the movable ring is realized, and the linear expansion of the movable ring under high temperature and high pressure is accurately and effectively controlled.

The movable ring is made of silicon carbide, and the sealing end face of the movable ring is provided with a diamond coating; the static ring is made of hard alloy, and a composite type multiple pattern structure is arranged on the sealing end face of the static ring.

Still preferably, the composite type multi-element pattern structure comprises a plurality of spiral micro grooves and a plurality of triangular micro holes, wherein the plurality of spiral micro grooves are arranged on the outer ring of the end face of the movable ring in the radial direction and are uniformly distributed along the circumferential direction of the movable ring; and the triangular micropores are uniformly distributed on the inner ring of the radial direction of the end surface of the movable ring.

Still improve, all be equipped with annular metal cladding circle between telescopic lateral wall and the inside wall of quiet ring seat and between moving ring seat and the rotation axis lateral wall, metal cladding circle include the plate spring that the cross section is the V type, just the outside cladding of plate spring has the rubber seal layer. The metal cladding ring in the improved structure not only plays a role in sealing, but also can play a role in better axial following performance, and the sealing performance is ensured to be more stable.

Still further, the spiral supporting ring is arranged between one end of the movable ring, which is away from the movable sealing surface, and the bottom of the second mounting groove and between the pressure plate and one end of the static ring, which is away from the static sealing surface. The spiral supporting ring in the structure plays a role in balancing axial force besides a sealing effect, and the two sealing rings are mainly subjected to high pressure because high pressure enters from the upper end, so that the sealing ring with the structure can resist the high pressure.

And the side wall of the first mounting groove is provided with at least one limiting column extending along the axial direction, and the side walls of the pressure plate and the static ring are respectively provided with a limiting groove matched with the limiting column. The limiting column in the structure is provided with the limiting groove, so that the static ring assembly can not rotate relative to the static ring seat under the action of friction torque force of the dynamic ring, and the sealing stability is ensured.

Drawings

Fig. 1 is a schematic view of a semi-sectional structure of a sealing device of the present invention.

FIG. 2 is a schematic illustration of a semi-sectional configuration of a stationary ring assembly according to the present invention.

FIG. 3 is a schematic view of the semi-sectional structure of the moving ring assembly of the present invention.

Fig. 4 is a cross-sectional view of a metal wrap ring in accordance with the present invention.

Fig. 5 is a schematic diagram of the end face grooving pattern of the stationary ring in the present invention.

Fig. 6 is an enlarged schematic view of the structure at X in fig. 5.

FIG. 7 is a graph showing the variation of friction coefficient when three different patterns are formed on the stationary ring.

FIG. 8 is a graph of temperature rise for a friction test with three different shaped patterns on a stationary ring.

FIG. 9 is a graph of friction coefficients for a pairing test of a stationary ring with a moving ring in three patterns without grooving, with only spiral grooves, and with both spiral grooves and triangular holes.

FIG. 10 is a graph showing the temperature rise of a pairing test of a stationary ring with a moving ring in three patterns without slotting, with only a spiral slot, and with both a spiral slot and a triangular hole.

Wherein the figures show: 01-moving ring assembly, 02-stationary ring assembly;

1-stationary ring, 2-stationary ring seat, 2.1-first mounting groove, 2.2-spring hole, 2.3-clamping groove, 3-L-shaped pushing cylinder, 3.1-sleeve, 3.2-pressure plate, 4-moving ring, 5-moving ring seat, 5.1-second mounting groove, 6-positioning sleeve, 6.1-threaded hole, 7-spiral micro groove, 8-triangular micropore, 9-metal cladding ring, 9.1-plate spring, 10-spiral supporting ring, 11-limit column, 12-limit groove, 13-small spring, 14-jump ring, 15-connecting bolt, 16-rubber supporting ring.

Description of the embodiments

The invention is further described below with reference to the drawings and the detailed description.

In the description of the present invention, it should be noted that the positional or positional relationship indicated by the terms such as "outer", "end", "outer side wall", "bottom", "tail", etc. are based on the positional or positional relationship shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or element in question must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention. In addition, in the description of the present invention, the terms "first" and "second" are used for convenience of description, convenience of distinction, and are not particularly meant. The end of the sealing ring facing away from the sealing friction surface is called the tail.

In the description of the present invention, it should be noted that, unless explicitly stated and limited otherwise, the term "connected" should be interpreted broadly, and for example, it may be a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.

As shown in fig. 1, the invention provides a sealing device, which comprises a movable ring assembly 01 and a static ring assembly 02, wherein the movable ring assembly 01 is sleeved outside a rotating shaft during installation, the static ring assembly 02 is also sleeved outside the rotating shaft and is fixedly installed at the end part of a sealing cavity, the sealing end surface of the movable ring assembly 01 is attached to the sealing end surface of the static ring assembly 02, when the rotating shaft rotates, the movable ring assembly 01 synchronously rotates along with the rotating shaft, the static ring assembly 02 is static, at the moment, the sealing surface of the movable ring assembly 01 and the sealing surface of the static ring assembly 02 relatively rotate, and a medium can enter a friction surface micro-gap between the movable ring assembly 01 and the static ring assembly 02 to form a layer of fluid film, so that a dynamic sealing effect is realized.

In this embodiment, specifically, the stationary ring assembly 02 includes a stationary ring 1, a stationary ring seat 2, and a reverse L-shaped pushing cylinder 3, where a first mounting groove 2.1 is provided at one end of the stationary ring seat 2 near the stationary ring assembly 01, the reverse L-shaped pushing cylinder 3 includes a sleeve 3.1 and a pressure plate 3.2 protruding on an outer side wall of one end of the sleeve 3.1, the outer side wall of the sleeve 3.1 is in sealing fit with an inner side of the stationary ring seat 2, and the pressure plate 3.2 is in sliding fit with a bottom of the first mounting groove 2.1; one end of the static ring 1, which is away from the static sealing surface, is sealed and slidably matched in the first mounting groove 2.1, the tail part of the static ring 1 abuts against the other end of the pressure plate 3.2, and the sealing surface of the static ring 1 is attached to the sealing surface of the movable ring assembly 01.

In addition, the sealing structure adopts static ring compensation, namely, a corresponding compensation element is arranged at the tail part of the static ring 1, after the sealing surface is worn, the static ring 1 is always clung to the sealing end surface of the movable ring assembly 01 after being acted by the compensation force of the compensation element, so that the stability of sealing performance is ensured. Specifically, the compensating element in this structure includes a plurality of cylindrical small springs 13, is equipped with a plurality of spring holes 2.2 along circumference at first mounting groove 2.1 bottom, and the one end of a plurality of small springs 13 is joined in marriage and is adorned in spring hole 2.2, and the other end is leaned against pressure disk 3.2 terminal surface, and the elastic force of a plurality of small springs 13 is through the afterbody of pressure disk 3.2 indirect effect in quiet ring 1.

In yet another aspect, to facilitate field installation of the seal, the stationary ring assembly 02 may be preassembled into a complete assembly prior to shipment, rather than as a plurality of discrete components; specifically, an annular clamping groove 2.3 is formed in the inner side wall of the opening end of the first mounting groove 2.1, a corresponding clamping spring 14 is assembled in the clamping groove 2.3, the outer end of the clamping spring 14 in the radial direction is matched in the clamping groove 2.3, and the inner end of the clamping spring is outwards protruded from the side wall of the first mounting groove 2.1. Correspondingly, the outer end part of the static ring 1 is provided with a limiting boss 1.1, during installation, a plurality of small springs 13 are firstly arranged in a spring hole 2.2 and then are arranged in a reverse L-shaped pushing cylinder 3, so that the small springs 13 are propped against the end surface of the pressure plate 3.2 near one end of the sleeve 3.1, then the static ring 1 is arranged in the first installation groove 2.1, the outer end surface of the static ring 1 is subjected to pressure test, at the moment, the small springs 13 are in a pre-pressing state, the clamping springs 14 are clamped in the clamping grooves 2.3, the external force is released, the small springs 13 reversely reset, and the limiting boss 1.1 of the static ring 1 is driven to prop against the end surface of the clamping springs 14, so that a complete assembly is formed, and all parts cannot be separated in a non-use state. More specifically, in order to prevent the stationary ring 1 and the pressure plate 3.2 from rotating circumferentially under the friction force driving action of the movable ring assembly 01, at least one limiting column 11 extending along the axial direction is arranged on the side wall of the first mounting groove 2.1, and limiting grooves 12 matched with the limiting columns 11 are formed in the side walls of the pressure plate 3.2 and the stationary ring 1, so that an anti-rotation effect is effectively achieved. Preferably, four limit posts 11 are arranged on the side wall of the first mounting groove 2.1, and specifically, the limit posts 11 can be directly integrally formed on the side wall of the first mounting groove 2.1, so that the processing difficulty is high and the cost is high; therefore, in this embodiment, the corresponding limiting pins are riveted at the bottom of the outer side of the first installation groove 2.1, that is, a post-matching mode is adopted, so that the processing difficulty is reduced.

In addition, the moving ring assembly 01 comprises a moving ring 4 and a moving ring seat 5, the moving ring seat 5 is hermetically sleeved outside the rotating shaft, a second installation groove 5.1 which is annular and axially opened is formed in the outer portion of the moving ring seat 5, the moving ring 4 is assembled in the second installation groove 5.1, the inner side wall of the moving ring 4 is hermetically matched with one side wall of the second installation groove 5.1, and a gap is reserved between the outer side wall of the moving ring 4 and the other side wall of the second installation groove 5.1.

The movable ring seat 5 is also provided with a positioning component which is used for axially limiting the end face of the movable ring 4. Specifically, the positioning assembly comprises a positioning sleeve 6, the positioning sleeve 6 is sleeved at one end of the movable ring seat 5 close to the stationary ring 1, a micro gap is reserved between the end part of the positioning sleeve 6 and the end face of the movable ring 4, and the specific gap is 0.03-0.05mm. Specifically, a plurality of connecting bolts 15 are arranged on the axial outer end face of the positioning sleeve 6, and the end parts of the connecting bolts 15 are connected to the movable ring seat 5.

In the moving ring assembly 01 with the structure, the moving ring 4 is in interference fit with the moving ring seat 5, specifically, a flexible rubber support ring 16 is arranged between the inner side wall of the moving ring 4 and the inner side wall of the second mounting groove 5.1 of the moving ring seat 5, so that swing under high rotating speed and large amplitude is prevented, and a perfluoro rubber O-shaped ring is specifically adopted, so that the sealing performance can be ensured at high temperature. One end of the movable ring seat 5 is sleeved with a positioning sleeve 6, the positioning sleeve 6 is fixed through a connecting bolt 15, and specifically, after a micro gap of 0.03-0.05mm is reserved between the end part of the positioning sleeve 6 and the end face of the movable ring 4, the excessive linear expansion of the movable ring 4 is prevented under the working condition of high temperature, high speed and high pressure, and the stable operation of the movable ring 4 at high rotation speed is ensured, so that the sealing performance of a sealing surface is ensured.

The axial outer end face of the positioning sleeve 6 is also provided with a plurality of threaded holes 6.1, when the adjusting bolts are arranged in the threaded holes 6.1, the distance between the positioning sleeve 6 and the end face of the movable ring seat 5 is realized by screwing the adjusting bolts, so that the end face of the positioning sleeve 6 is realized

Accurate adjustment of the distance from the end face of the movable ring 4 accurately and effectively controls linear expansion of the movable ring 4 at high temperature and high pressure.

Annular metal cladding rings 9 are arranged between the outer side wall of the sleeve 3.1 and the inner side wall of the stationary ring seat 2 and between the movable ring seat 5 and the outer side wall of the rotating shaft, the metal cladding rings 9 comprise plate springs 9.1 with V-shaped cross sections, and rubber sealing layers 9.2 are coated outside the plate springs 9.1. In the structure, two metal cladding rings 9 are sealed, and the combined sealing ring with the plate spring 9.1 belongs to the second stage of static sealing, so that the pressure is reduced, and simultaneously, the two places slide axially and rotate, so that the combined sealing ring with the plate spring 9.1 can compensate the axial following property.

In this embodiment, a spiral supporting ring 10 is disposed between one end of the moving ring 4 facing away from the moving sealing surface and the bottom of the second mounting groove 5.1, and between the pressure plate 3.2 and one end of the stationary ring 1 facing away from the stationary sealing surface. In this structure, two spiral supporting rings 10 are arranged, which have the function of balancing axial force besides the sealing function, and the sealing rings can resist high pressure because high pressure enters from the upper end, and the two sealing rings are mainly at the high pressure bearing position.

In this embodiment, the moving ring 4 is made of silicon carbide, and a diamond coating is disposed on the sealing end surface of the moving ring 4; the static ring 1 is made of hard alloy, and a composite type multiple pattern structure is arranged on the sealing end face of the static ring 1. As can be seen from fig. 1, the friction surface of the stationary ring 1 is a narrow surface, the friction surface of the moving ring 4 is a wide surface, and due to the high hardness of the silicon carbide material and good wear resistance, the pit is prevented from being ground on the end surface of the moving ring 4 in the structure, so that the moving ring 4 is made of the silicon carbide material, and a layer of diamond coating is added on the grinding surface, so that the wear resistance and the lubrication performance of the moving ring are further enhanced. Because the static ring 1 is required to be provided with a pattern structure, a hard alloy material with better processing property is selected, and because the silicon carbide material has good wear resistance and high strength, but is fragile, obvious in dust particles and poor in processing property under high-energy density melting.

Specifically, the composite type multiple pattern structure comprises a plurality of spiral micro grooves 7 and a plurality of triangular micro holes 8, wherein the plurality of spiral grooves 7 are arranged on the outer ring of the end surface of the movable ring 4 in the radial direction and are spirally distributed along the circumferential direction of the movable ring 4; the triangular micropores 8 are uniformly distributed on the inner ring of the end surface of the movable ring 4 in the radial direction. As shown in fig. 5, more specifically, in the present embodiment, the outermost end of the spiral groove is open, and the spiral direction is opposite to the rotation direction of the seal ring, and the curved arrow direction in the figure is the rotation direction.

In addition, the orientation position of the triangular micro-holes 8 is also required, specifically, along the spiral direction of the spiral micro-groove 7, each triangular micro-hole converges along the spiral direction from both ends of any one side, reaching a sharp angle position of the triangular micro-hole corresponding to the side, and the side of the triangular micro-hole is parallel to the radial direction of the sealing ring radiating from the center of the circle in the radial direction, which is specifically set, hereinafter, specifically developed.

The following is test data in combination with a related simulation run test, specifically illustrating the selection basis of the slot shape on the friction pair:

FIG. 6 is a friction test at 250 r/min cruise conditions for 3 different textures of triangles, ellipses and classical helical grooves. As can be seen from fig. 6: the friction coefficient of the group 2-B1 (triangle) forms regular fluctuation with time, the fluctuation with time of the friction coefficient of the group 0.0597,2-B2 (ellipse) is more complex, the fluctuation amplitude is smaller than that of the group 2-B1, because the ellipse is smoother than the figure edge of the triangle, but the average friction coefficient of the group 2-B2 is 0.1290; the friction coefficient of groups 2-B3 (classical helical grooves) fluctuates smoothly and regularly with time, and has the lowest amplitude and average friction coefficient of 0.0810. The difference in coefficient of friction exhibited by the texture in fig. 6 can be summarized as the following 3 causes: (1) because the oval micropore boundaries are smoother, when fluid enters the oval micropores, more fluid is soaked in the pores, so that the film thickness is increased; meanwhile, negative pressure is easy to form in the running process to suck liquid medium, so that the dynamic pressure effect of elliptical textures is insufficient, and the running state of the friction pair cannot be improved; (2) the triangular micropore has a tip area, has a stronger convergent wedge effect, has extremely strong directivity, and improves the lubrication state of the friction pair micro-gap fluid; on the other hand, the triangular texture has larger speed difference between the inner diameter and the outer diameter, so that the friction coefficient of the group 2-B2 slightly fluctuates; (3) the classical spiral groove texture belongs to micro grooves, has the characteristics of large area and small density, is quite opposite to the characteristics of small area and large density of triangular and elliptic micropores, has a longer continuous fluid domain wall surface, can instantly convert fluid kinetic energy into pressure potential energy, forms an obvious Rayleigh step effect, counteracts partial vortex formed by fluid backflow, improves the fluctuation of a friction pair in the running process, and has a vibration suppression effect.

From the above test results, it is inferred that: (1) for microporous texture (triangles and ellipses), its shape is a key factor affecting the mechanical seal friction performance; (2) the micro-groove texture (classical spiral groove) is mainly embodied in dynamics, so that the running stability can be improved.

Fig. 7 shows the temperature change of the friction pair during operation. Comparing the temperature change trend of triangle, ellipse and classical spiral groove, the temperature rises of group 2-B1, group 2-B2 and group 2-B3 are found to be 4.1 ℃, 12.3 ℃ and 15.3 ℃ respectively. In the initial stage of the test, the rising amplitude of the surface temperatures of the three groups of test pieces is basically similar, and as the test is carried out, the surface temperatures of the 2-B1 groups of test pieces tend to be balanced at the earliest, and the highest temperature is only 27.7 ℃; the surface temperature rise rates of the groups 2-B2 and 2-B3 are reduced, but the temperature is still slowly increased, so that the friction heat generation amount of the test pieces of the groups 2-B2 and 2-B3 in unit time is higher, and further the temperature dynamic balance is delayed.

Therefore, the real-time change condition of the surface temperature of the friction pair can be known: the change of the texture of the surface of the friction pair can influence the friction heat generating rate and the dynamic balance state of the surface of the friction pair, and the triangular texture can effectively control the temperature rise of the friction pair and improve the heat of the surface of the friction pair.

Additionally, for 3-C1: and 3-C2 under the condition that no pattern is arranged on the dynamic ring and the static ring: the static ring 1 is provided with a classical spiral groove, and the dynamic ring 4 is a smooth surface; 3-C3: the static ring 1 is provided with classical spiral grooves and triangular small holes, and the dynamic ring 4 is a smooth surface, and three friction pairs are subjected to test analysis.

FIG. 8 shows the real-time variation of the friction coefficient of groups 3-C1, 3-C2 and 3-C3 with time of operation. The average coefficient of friction of the 3-C1 group was 0.123,3-C2 group, the average coefficient of friction of the 0.129,3-C3 group was 0.052. From the three groups of average friction coefficients, the friction coefficient of 3-C3 is reduced by 59.69 percent compared with that of 3-C2. The friction performance of the 3-C3 group is better than that of the 3-C2 group and the 3-C1 group. Therefore, when the triangular texture is formed on the hard alloy (WC for short), the friction pair is matched with a classical spiral groove, and matched with SSiC, the friction coefficient reaches the minimum of all test objects, the friction coefficient is reduced by 12.90% compared with the friction coefficient of the test objects in the group 2-B1, the friction coefficient is reduced by 59.69% compared with the friction coefficient of the test objects in the group 2-B2, and the friction coefficient is reduced by 35.80% compared with the friction coefficient of the test objects in the group 2-B3. However, the friction coefficient of the 3-C2 group is extremely undesirable, and it can be demonstrated that the provision of the helical groove in the WC-SSiC pairing does not improve the surface friction performance. Therefore, the surface of the friction pair is simultaneously provided with the classical spiral groove and the triangle, a 'synergistic effect' exists between the classical spiral groove and the triangle, and the double-texture composite configuration of the micropore and the micro groove 'supplies' part of pressure peak value to the cavitation part, so that the 'dynamic pressure effect' of the classical spiral groove and the 'antifriction and lubrication' effect of the triangle are improved.

FIG. 9 shows the trend of temperature change for groups 3-C1, 3-C2 and 3-C3; the test structure finds: the temperature rise of 3-C1 is 9.9 ℃, the temperature rise of 3-C2 is 11.1 ℃, and the temperature rise of 3-C3 is 3.8 ℃, thereby showing that the double-texture composite configuration of 3-C3 has positive effect on reducing the surface temperature rise of the friction pair. The double-texture composite structure formed by combining the triangular and classical spiral grooves enables the micro grooves and the micropores to generate a synergistic effect, and the high heat conduction and low expansion characteristics of the silicon carbide ceramic material are combined, so that the temperature rise of 3-C3 is minimized.

From test data, the surface of the friction pair is simultaneously provided with a classical spiral groove and a triangular micropore, a synergistic effect exists between the classical spiral groove and the triangular micropore, and the double-texture composite configuration of the micropore and the micro groove enables partial pressure peak value to be supplied to a cavitation part, so that the dynamic pressure effect of the classical spiral groove and the antifriction and lubrication effect of the triangle are improved.

The foregoing description of the preferred embodiments of the present invention is provided for illustration and is not to be construed as limiting the claims. The present invention is not limited to the above embodiments, and the specific structure thereof is allowed to be changed, and all changes made within the scope of the invention as independently claimed are within the scope of the invention.

Claims

1. A sealing device comprising a moving ring assembly (01) for being sleeved outside a rotating shaft and a stationary ring assembly (02) fixed at the end of a sealing cavity, characterized in that: the static ring assembly (02) comprises a static ring (1), a static ring seat (2) and a reverse L-shaped pushing cylinder (3), a first mounting groove (2.1) is formed in one end of the static ring seat (2) close to the dynamic ring assembly (01), the reverse L-shaped pushing cylinder (3) comprises a sleeve (3.1) and a pressure plate (3.2) convexly arranged on the outer side wall of one end of the sleeve (3.1), the outer side wall of the sleeve (3.1) is in sealing fit with the inner side of the static ring seat (2), and the pressure plate (3.2) is in sliding fit with the bottom of the first mounting groove (2.1); one end of the static ring (1) deviating from the static sealing surface is sealed and slidably matched in the first mounting groove (2.1), the tail part of the static ring (1) abuts against the other end of the pressure plate (3.2), and the sealing surface of the static ring (1) is attached to the sealing surface of the movable ring assembly (01);

the movable ring assembly (01) comprises a movable ring (4) and a movable ring seat (5), the movable ring seat (5) is hermetically sleeved outside the rotating shaft, a second installation groove (5.1) which is annular and axially opened is formed in the outer part of the movable ring seat (5), the movable ring (4) is assembled in the second installation groove (5.1), the inner side wall of the movable ring (4) is hermetically matched with one side wall of the second installation groove (5.1), and a gap is reserved between the outer side wall of the movable ring (4) and the other side wall of the second installation groove (5.1); the movable ring (4) is made of silicon carbide, and a diamond coating is arranged on the sealing end surface of the movable ring (4); the static ring (1) is made of hard alloy, and a composite multi-element pattern structure is arranged on the sealing end surface of the static ring (1); the composite type multielement pattern structure comprises a plurality of spiral micro grooves (7) and a plurality of triangular micro holes (8), wherein the plurality of spiral micro grooves (7) are arranged on the outer ring of the end face of the stationary ring (1) in the radial direction and are uniformly distributed along the circumferential direction of the stationary ring (1); the triangular micropores (8) are uniformly distributed on the inner ring of the end surface radial direction of the stationary ring (1);

the outermost end of the spiral micro groove (7) is open, the spiral direction is opposite to the rotation direction of the static ring (1), a plurality of triangular micro holes (8) are converged along the spiral direction of the spiral micro groove (7) from two ends of one side, one sharp angle position of the triangular micro hole (8) corresponding to the side is reached, and the side of the triangular micro hole (8) is parallel to the radial direction of the static ring (1) radiating from the center of a circle along the radial direction.

2. The sealing device of claim 1, wherein: and the movable ring seat (5) is also provided with a positioning assembly for axially limiting the end face of the movable ring (4).

3. The sealing device of claim 2, wherein: the positioning assembly comprises a positioning sleeve (6), the positioning sleeve (6) is sleeved at one end of the movable ring seat (5) close to the stationary ring (1), and a micro-gap of 0.03-0.05mm is reserved between the end part of the positioning sleeve (6) and the end face of the movable ring (4).

4. A sealing device according to claim 3, wherein: and a plurality of threaded holes (6.1) are further formed in the axial outer end face of the positioning sleeve (6), and when an adjusting bolt is arranged in the threaded holes (6.1), the adjusting bolt is screwed to adjust the distance between the positioning sleeve (6) and the end face of the movable ring (4).

5. The sealing device of claim 1, wherein: annular metal cladding rings (9) are arranged between the outer side wall of the sleeve (3.1) and the inner side wall of the static ring seat (2) and between the movable ring seat (5) and the outer side wall of the rotating shaft, the metal cladding rings (9) comprise plate springs (9.1) with V-shaped cross sections, and rubber sealing layers (9.2) are coated outside the plate springs (9.1).

6. The sealing device of claim 5, wherein: spiral supporting rings (10) are arranged between one end of the movable ring (4) deviating from the movable sealing surface and the bottom of the second mounting groove (5.1) and between the pressure plate (3.2) and one end of the static ring (1) deviating from the static sealing surface.

7. The sealing device according to any one of claims 1 to 6, wherein: the side wall of the first mounting groove (2.1) is provided with at least one limiting column (11) extending along the axial direction, and the side walls of the pressure plate (3.2) and the stationary ring (1) are respectively provided with a limiting groove (12) matched with the limiting column (11).