Sealing end face structure of rotating machinery

Abstract

The present invention provides a sealing end face structure of a rotating mechanical device, comprising a stationary ring and a moving ring that can rotate relative to the stationary ring, wherein the low-pressure side of the stationary ring or the moving ring is the downstream side, and the high-pressure side of the stationary ring or the moving ring is the upstream side; the downstream side of the relative surface of the stationary ring or the moving ring has a plurality of reverse groove groups, the plurality of reverse groove groups are spaced apart in the radial direction, and each of the reverse groove groups includes a plurality of reverse spiral grooves distributed in the circumferential direction. After adopting a plurality of reverse groove groups, the pumping capacity of the fluid on the downstream side can be enhanced, and at the same time, the reverse spiral grooves in the reverse groove group can store fluid to reduce the friction and wear of the sealing end face, increase the service life of the seal, and ensure the effect of the mechanical seal.

Description

Technical Field

[0001] The invention relates to the field of mechanical seals, and in particular to a sealing end face structure of a rotating mechanical device. Background Art

[0002] Mechanical seal is an axial end face sealing device that achieves sealing by pre-tightening the dynamic and static ring end face sealing pair with elastic elements and pressing the medium pressure with the elastic element pressure, also known as end face seal. Through flow field calculation and theoretical design, the seal can form a stable fluid film with a thickness of micrometers between the dynamic ring rotating with the shaft and the relatively static static ring end face under specified working conditions, thereby limiting the leakage of the working medium and playing a role in reducing wear and lubricating the friction pair end face.

[0003] In engineering applications, many rotating machines require mechanical seals to meet high performance requirements such as long service life, wide range of applicable working conditions, stable working performance, low leakage or even zero leakage. Common dynamic and static pressure combined upstream pumping mechanical seals are designed with shallow grooves with pumping capacity on the sealing end face to prevent leakage of the sealed fluid. However, for current low-leakage mechanical seals, a stable fluid film is not formed during start-up and shutdown, and the contact wear of the sealing end face is large, which affects the effect of the mechanical seal. Summary of the invention

[0004] Based on this, it is necessary to provide a sealing end face structure of a rotating mechanical device that reduces wear and improves upstream pumping capacity in order to address the current problems of large seal end face wear and insufficient upstream pumping capacity.

[0005] The above purpose is achieved through the following technical solutions:

[0006] A sealing end face structure of a rotating mechanical device, comprising a stationary ring and a moving ring rotatable relative to the stationary ring, wherein the low-pressure side of the stationary ring or the moving ring is the downstream side, and the high-pressure side of the stationary ring or the moving ring is the upstream side;

[0007] The downstream side of the relative surface of the stationary ring or the dynamic ring has a plurality of reverse groove groups, the plurality of reverse groove groups are spaced apart in the radial direction, and each of the reverse groove groups includes a plurality of reverse spiral grooves distributed in the circumferential direction.

[0008] In one embodiment, the number of the reverse spiral grooves in each reverse groove group gradually decreases from the downstream side to the upstream side;

[0009] Alternatively, the number of the reverse spiral grooves in each reverse groove group is the same.

[0010] In one embodiment, the plurality of reverse groove groups include a main groove and a plurality of auxiliary grooves, and the plurality of auxiliary grooves are located between the main groove and the downstream side.

[0011] In one embodiment, the number of the reverse spiral grooves in the main groove is 6 to 48, and the angle between the tangent lines of two adjacent side walls of the reverse spiral groove in the main groove is in the range of 5° to 80°;

[0012] The number of the reverse spiral grooves in the secondary groove is 2 to 10 times the number of the reverse spiral grooves in the primary groove, and the angle between the tangent lines of two adjacent side walls of the reverse spiral grooves in the secondary groove is in the range of 5° to 80°.

[0013] In one embodiment, the surface where the dynamic ring contacts the static ring is a sealing ring surface, and the width of the reverse groove group in the radial direction is 1 / 3 to 3 / 4 of the radial width of the sealing ring surface;

[0014] And / or, the groove depth of the reverse spiral groove in the secondary groove is greater than the groove depth of the reverse spiral groove in the main groove, and the groove depth of the reverse spiral groove in each secondary groove increases step by step from the upstream side to the downstream side.

[0015] In one embodiment, the groove depth of the reverse spiral groove in the main groove is 5 μm to 100 μm, and the groove depth of the reverse spiral groove in the secondary groove is 1 μm to 50 μm deeper than the groove depth of the reverse spiral groove in the main groove.

[0016] In one embodiment, a first auxiliary dam area is formed between the main groove and the adjacent auxiliary groove, and the ratio of the radial width of the reverse spiral groove in the main groove to the radial width of the first auxiliary dam area is 0.2 to 5;

[0017] And / or, a second auxiliary dam area is formed between adjacent auxiliary grooves, and the ratio of the radial width of the reverse spiral groove in the auxiliary groove to the radial width of the second auxiliary dam area is 0.2-5.

[0018] In one embodiment, in the circumferential direction of the main groove, a main reverse sealing weir area is formed between adjacent reverse spiral grooves, and the ratio of the circumferential width of the reverse spiral groove in the main groove to the circumferential width of the main reverse sealing weir area is 0.2 to 5;

[0019] In the circumferential direction of the secondary groove, a secondary reverse sealing weir area is formed between adjacent reverse spiral grooves, and the ratio of the circumferential width of the reverse spiral groove in the secondary groove to the circumferential width of the secondary reverse sealing weir area is 1 / 10 to 1 / 2 of the ratio of the circumferential width of the reverse spiral groove in the main groove to the circumferential width of the main reverse sealing weir area.

[0020] In one embodiment, the plurality of sub-grooves include a first sub-groove and a second sub-groove, the second sub-groove is located on the downstream side, the first sub-groove is located between the main groove and the second sub-groove, the reverse spiral groove in the main groove is the main reverse spiral groove, the reverse spiral groove in the first sub-groove is the first sub-reverse spiral groove, the reverse spiral groove in the second sub-groove is the second sub-reverse spiral groove, a first sub-dam area is formed between the main groove and the adjacent sub-groove, a second sub-dam area is formed between the adjacent sub-grooves, the sub-reverse sealing weir area of ​​the first sub-groove is the first sub-reverse sealing weir area, and the sub-reverse sealing weir area of ​​the second sub-groove is the second sub-reverse sealing weir area;

[0021] The number of the main reverse spiral grooves is 6 to 48, the angle between the tangent lines of two adjacent side walls of the main reverse spiral groove is 5° to 80°; the ratio of the radial width of the main reverse spiral groove to the radial width of the first auxiliary dam area is 0.2 to 5; the ratio of the circumferential width of the main reverse spiral groove to the circumferential width of the main reverse sealing weir area is 0.2 to 5, and the groove depth of the main reverse spiral groove is 5 μm to 100 μm;

[0022] The number of the first secondary reverse spiral grooves is 2 to 4 times the number of the main reverse spiral grooves, and the angle range of the corresponding tangents of two adjacent side walls of the first secondary reverse spiral groove is 5° to 80°; the ratio of the radial width of the first secondary reverse spiral groove to the radial width of the second secondary dam area is 0.2 to 5; the ratio of the circumferential width of the first secondary reverse spiral groove to the circumferential width of the first secondary reverse sealing dam area is 0.2 to 5, and the groove depth of the first secondary reverse spiral groove is 1 μm to 50 μm deeper than the groove depth of the main reverse spiral groove;

[0023] The number of the second secondary reverse spiral grooves is 5 to 10 times the number of the main reverse spiral grooves, and the angle range of the corresponding tangents of two adjacent side walls of the second secondary reverse spiral groove is 5° to 80°; the ratio of the radial width of the second secondary reverse spiral groove to the radial width of the second secondary dam area is 0.2 to 5; the ratio of the circumferential width of the second secondary reverse spiral groove to the circumferential width of the second secondary reverse sealing dam area is 0.2 to 5, and the groove depth of the second secondary reverse spiral groove is 1μm to 50μm deeper than the groove depth of the first secondary reverse spiral groove.

[0024] In one embodiment, at least one of the main reverse spiral grooves corresponds to several of the first secondary reverse spiral grooves and several of the second secondary reverse spiral grooves;

[0025] The number of the first secondary reverse spiral grooves and the number of the second secondary reverse spiral grooves vary with the number of the main reverse spiral grooves.

[0026] In one embodiment, the upstream side of the relative surface of the stationary ring or the dynamic ring also has at least one forward groove group, and the forward groove group includes a plurality of forward spiral grooves distributed along the circumferential direction, and the rotation direction of the forward spiral groove is opposite to that of the reverse spiral groove.

[0027] In one embodiment, the sum of the areas of the reverse spiral grooves in the secondary grooves is greater than the sum of the areas of the reverse spiral grooves in the primary grooves, and the sum of the areas of the reverse spiral grooves in the secondary grooves gradually increases from the upstream side to the downstream side;

[0028] And / or, the width of the forward groove group in the radial direction is 1 / 5 to 1 / 2 of the radial width of the sealing ring surface.

[0029] In one of the embodiments, in the forward groove group, the number of the forward spiral grooves is 6 to 48, the angle between the tangents corresponding to two adjacent side walls of the forward spiral groove is in the range of 5° to 80°, and the groove depth of the forward spiral groove is 5 μm to 100 μm.

[0030] In one embodiment, a main dam area is formed between the reverse groove group and the forward groove group, and the ratio of the radial width of the forward spiral groove to the radial width of the main dam area is 0.2 to 5;

[0031] In the circumferential direction of the positive groove group, a positive sealing weir area is formed between adjacent positive spiral grooves, and the ratio of the circumferential width of the positive spiral groove to the circumferential width of the positive sealing weir area is 0.2-5.

[0032] In one embodiment, the groove wall connecting line of each of the reverse spiral grooves in the reverse groove group is a logarithmic spiral line, an Archimedean spiral line or a circular arc line;

[0033] And / or, a line connecting the groove walls of each of the forward spiral grooves in the forward groove group is a logarithmic spiral, an Archimedean spiral or a circular arc.

[0034] After adopting the above technical solution, the present invention has at least the following technical effects:

[0035] The sealing end face structure of the rotary mechanical equipment of the present invention is such that when the fluid in the sealing end face structure flows clockwise or counterclockwise in the circumferential direction of the sealing ring along the rotation direction of the moving ring, the fluid enters the reverse spiral groove of the reverse groove group, and flows from the downstream side to the middle of the moving ring or the static ring under the guiding effect of the groove wall of the reverse spiral groove, so as to offset the influence of the pressure difference between the inner and outer diameters of the sealing end face structure. When the upstream pumping capacity of the reverse groove group and the pressure difference between the inner and outer diameters reach a balance, an annular boundary line between the sealing medium and the atmosphere will be formed in the reverse spiral groove area, thereby achieving zero leakage of the sealing medium. After adopting multiple reverse groove groups, the area of ​​the fluid film on the sealing end face part can be increased. The current problem of large wear on the sealing end face is effectively solved. The sealing end face structure of the present invention reduces the friction and wear of the sealing end face through multiple reverse spiral grooves, improves the lubrication performance, and ensures the service life of the seal. At the same time, it improves the pumping capacity of the downstream side and ensures the effect of the mechanical seal. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 It is a front view of the dynamic ring in the sealing end face structure of the first embodiment of the present invention;

[0037] Figure 2 for Figure 1 A partial cross-sectional view at AA shown;

[0038] Figure 3 for Figure 1 A partial enlarged view of point B shown;

[0039] Figure 4 It is a front view of a dynamic ring in a sealing end face structure according to a second embodiment of the present invention;

[0040] Figure 5 It is a front view of the dynamic ring in the sealing end face structure of the third embodiment of the present invention.

[0041] in:

[0042] 100-dynamic ring;

[0043] 110-reverse slot group;

[0044] 111-reverse spiral groove;

[0045] 112-main slot;

[0046] 113-sub-slot; 1131-first sub-slot; 1132-second sub-slot;

[0047] 114- auxiliary dam area; 1141- first auxiliary dam area; 1142- second auxiliary dam area;

[0048] 115-main reverse seal weir area;

[0049] 116 - secondary reverse sealing weir area; 1161 - first secondary reverse sealing weir area; 1162 - second secondary reverse sealing weir area;

[0050] 120-forward slot group;

[0051] 121-positive spiral groove;

[0052] 122-main dam area;

[0053] 123-Positive seal weir area. DETAILED DESCRIPTION

[0054] In order to make the purpose, technical solution and advantages of the present invention more clearly understood, the sealing end face structure of the rotary mechanical equipment of the present invention is further described in detail below through embodiments and in combination with the accompanying drawings. It should be understood that the specific embodiments described here are only used to explain the present invention and are not used to limit the present invention.

[0055] The serial numbers of the components herein, such as "first", "second", etc., are only used to distinguish the objects described and do not have any order or technical meaning. The "connection" and "coupling" mentioned in this application, unless otherwise specified, include direct and indirect connections (couplings). In the description of the present invention, it should be understood that the orientation or positional relationship indicated by the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", etc. are based on the orientation or positional relationship shown in the accompanying drawings, which is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present invention.

[0056] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being "above", "above" or "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below", "below" or "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0057] See also Figure 1 , Figure 4 and Figure 5An embodiment of the present invention provides a sealing end face structure of a rotating mechanical device. The sealing end face structure can seal the shaft ends of various types of rotating mechanical devices to avoid fluid leakage and ensure the normal operation of the rotating mechanical devices. Optionally, the rotating mechanical devices include but are not limited to compressors, expanders, pumps, reactor agitators, etc. The sealing end face structure of the present invention can reduce the friction and wear of the sealing end face, increase the service life of the seal, and at the same time, improve the pumping capacity of the upstream side to ensure the effect of the mechanical seal.

[0058] See also Figures 1 to 3 In the first embodiment of the present invention, the sealing end face structure includes a stationary ring and a moving ring 100 that can rotate relative to the stationary ring. The low-pressure side of the stationary ring or the moving ring 100 is the downstream side, and the high-pressure side of the stationary ring or the moving ring 100 is the upstream side. In other words, the inner side of the moving ring 100 can be the upstream side or the downstream side. In this embodiment, the outer diameter side of the moving ring 100 is the high-pressure sealed fluid. At this time, the inner side of the stationary ring and the moving ring 100 is the low-pressure side, that is, the downstream side, and the outer side of the stationary ring and the moving ring 100 is the high-pressure side, which is recorded as the upstream side. Usually, the fluid on the upstream side will flow to the downstream side under the action of pressure. Of course, in other embodiments of the present invention, if the inner side of the moving ring 100 is the high-pressure sealed fluid, the inner side of the moving ring 100 is the upstream side.

[0059] The downstream side of the relative surface of the stationary ring or the dynamic ring 100 has a plurality of reverse groove groups 110, which are spaced apart in the radial direction, and each reverse groove group 110 includes a plurality of reverse spiral grooves 111 distributed in the circumferential direction. The upstream side of the relative surface of the stationary ring or the dynamic ring 100 also has at least one positive groove group 120, which includes a plurality of positive spiral grooves 121 distributed in the circumferential direction, and the rotation direction of the positive spiral groove 121 is opposite to that of the reverse spiral groove 111. Moreover, the positive groove group 120 and the reverse groove group 110 are located on the same surface.

[0060] In this embodiment, the number of the forward groove group 120 can be one. Of course, in other embodiments of the present invention, the number of the forward groove group 120 can also be multiple, distributed at intervals in the radial direction. That is to say, the forward groove group 120 and the multiple reverse groove groups 110 can be located on the surface of the stationary ring facing the movable ring 100, or on the surface of the movable ring 100 facing the stationary ring. In the present invention, only the example that the forward groove group 120 and the multiple reverse groove groups 110 are both arranged on the movable ring 100 is used for explanation. Figure 1As shown, its specific working principle is described in detail below. Of course, in other embodiments of the present invention, the forward groove group 120 and the multiple reverse groove groups 110 are all arranged on the static ring, and their working principles are substantially the same as the principles in the above-mentioned embodiments. It should be noted that the forward direction of the forward groove group 120 means that when the fluid flows from the upstream side to the downstream side and the moving ring 100 rotates in the clockwise direction, the forward spiral groove 121 in the forward groove group 120 can guide the fluid flow. Similarly, the reverse direction of the reverse groove group 110 means that when the fluid flows from the upstream side to the downstream side and the moving ring 100 rotates in the clockwise direction, the reverse spiral groove 111 in the reverse groove group 110 can hinder the fluid flow. In addition, the reverse spiral groove 111 and the forward spiral groove 121 are spiral grooves, which are part of the spiral.

[0061] Both the moving ring 100 and the stationary ring are annular structures. The surface where the moving ring 100 contacts the stationary ring is the sealing ring surface, which is the minimum width dimension of the moving ring 100 and the stationary ring in the radial direction. For example, if the radial dimension of the moving ring 100 is small, the radial dimension of the sealing ring surface is equal to the radial dimension of the surface of the moving ring 100 facing the stationary ring; if the radial dimension of the stationary ring is small, the radial dimension of the sealing ring surface is equal to the radial dimension of the surface of the stationary ring facing the moving ring 100.

[0062] The principle of sealing is: in a stationary state, the dynamic ring 100 and the static ring maintain a close fit under the elastic force of the elastic parts of the rotating mechanical equipment to prevent fluid leakage. When the dynamic ring 100 moves with the rotating mechanical equipment, without considering the influence of the groove type of the forward spiral groove 121 and the reverse spiral groove 111, the fluid at the sealing ring surface flows clockwise or counterclockwise in the circumferential direction of the sealing ring surface along the rotation direction of the dynamic ring 100. Under the influence of the pressure difference between the inside and outside of the sealing ring surface, the fluid on the upstream side will enter the forward spiral groove 121, and the groove wall of the forward spiral groove 121 will guide the fluid, so that the fluid flows to the middle of the sealing ring surface. In addition, the fluid film thickness suddenly decreases at the groove root of the reverse spiral groove 111, that is, from the upstream side to the middle of the sealing ring surface, forming a fluid high-pressure area in the middle of the sealing ring surface. The fluid flowing circumferentially on the downstream side enters the reverse spiral groove 111, and flows from the downstream side to the middle of the sealing ring surface under the guidance of the groove wall of the reverse spiral groove 111, so as to offset the influence of the pressure difference between the inner and outer diameters of the sealing ring surface. In addition, the fluid film thickness suddenly decreases at the groove root of the reverse spiral groove 111, that is, from the downstream side to the middle of the sealing ring surface, forming a fluid high-pressure area in the middle of the sealing ring surface. Under the dual action of the forward spiral groove 121 and the reverse spiral groove 111, the main dam area 122 forms a stable fluid film high-pressure area, thereby preventing the leakage of the fluid on the upstream side to the downstream side.

[0063] When the upstream pumping capacity of the reverse spiral groove 111 and the pressure difference between the inner and outer diameters reach a balance, an annular dividing line between the sealing medium and the atmosphere will be formed in the reverse spiral groove 111 area, thereby achieving zero leakage of the sealing medium. When the working conditions change and a positive leakage occurs from the upstream side to the downstream side, it indicates that the above-mentioned annular dividing line is offset to the downstream side, and the upstream pumping capacity of the reverse spiral groove 111 is enhanced, pushing the annular dividing line to offset to the upstream side, and re-achieving the balance of zero leakage. Similarly, when the working conditions change and a reverse leakage occurs from the downstream side to the upstream side, it indicates that the above-mentioned annular dividing line is offset to the upstream side, and the upstream pumping capacity of the reverse spiral groove 111 is weakened, pushing the annular dividing line to offset to the downstream side, and re-achieving the balance of zero leakage. Therefore, the sealing end face structure combining the forward spiral groove 121 and the reverse spiral groove 111 can achieve zero leakage of the sealing fluid under a wide range of working conditions, and the seal has self-adjustment ability when the working conditions change, and has stable zero leakage sealing performance.

[0064] The sealing end face structure of the present invention forms multiple annular sealing areas on the sealing ring surface through the forward groove group 120 and the multiple reverse groove groups 110. When the sealing end face structure stops working, zero leakage can be effectively achieved in the sealed static state under the elastic force of the elastic parts of the rotating mechanical equipment. In addition, through the cooperation of the forward groove group 120 and the multiple reverse groove groups 110, the pumping capacity of the upstream side fluid can be enhanced. At the same time, the reverse spiral groove 111 in the reverse groove group 110 can store fluid. It effectively solves the current problems of large wear of the sealing end face and insufficient upstream pumping capacity. The sealing end face structure of the present invention reduces the friction and wear of the sealing end face through the multiple reverse spiral grooves 111, increases the service life of the seal, and at the same time, increases the pumping capacity of the upstream side to ensure the effect of the mechanical seal.

[0065] Optionally, each forward spiral groove 121 in the forward groove group 120 is symmetrical and evenly distributed with the center of the rotating ring 100 as the center to ensure the sealing effect. Correspondingly, each reverse spiral groove 111 in the reverse groove group 110 is symmetrical with the center of the rotating ring 100 as the center to ensure the sealing effect. Further, each reverse spiral groove 111 can be evenly distributed or unevenly distributed.

[0066] In one embodiment, the number of reverse spiral grooves 111 in each reverse groove group 110 gradually decreases from the downstream side to the upstream side. That is, the number of reverse spiral grooves 111 in the reverse groove group 110 on the downstream side is greater than the number of reverse spiral grooves 111 in the reverse groove group 110 away from the downstream side. That is, the reverse spiral grooves 111 in each reverse groove group 110 are arranged in a structure similar to a herringbone from the upstream side to the downstream side. This can improve the upstream pumping capacity of the fluid. At the same time, the reverse spiral grooves 111 arranged in a herringbone shape can play a role in accommodating impurity abrasive particles, reducing friction and lubrication, and reducing the impact of thermal deformation on sealing performance. Of course, in other embodiments of the present invention, the number of reverse spiral grooves 111 in each reverse groove group 110 is the same. This can also improve the upstream pumping capacity of the fluid and play a role in accommodating impurity abrasive particles, reducing friction and lubrication.

[0067] In one embodiment, the multiple reverse groove groups 110 include a main groove 112 and multiple auxiliary grooves 113, and the multiple auxiliary grooves 113 are located between the main groove 112 and the downstream side. The main groove 112 and the multiple auxiliary grooves 113 cooperate to improve the upstream pumping capacity of the fluid, and play a role in accommodating impurities and abrasive particles, reducing friction and lubrication. At the same time, the multiple auxiliary grooves 113 can gradually enhance the pumping capacity of the downstream side fluid, so that the annular boundary line between the fluid film and the atmosphere can be controlled within a range closer to the downstream side, while ensuring the stability of the fluid film, so that the fluid film covers a wider range on the sealing ring surface, further enhancing the lubrication effect of the fluid film, and improving the working stability and service life of the mechanical seal. In this embodiment, the plurality of sub-grooves 113 include a first sub-groove 1131 and a second sub-groove 1132, the second sub-groove 1132 is located at the downstream side, the first sub-groove 1131 is located between the main groove 112 and the second sub-groove 1132, the reverse spiral groove 111 in the main groove 112 is the main reverse spiral groove, the reverse spiral groove 111 in the first sub-groove 1131 is the first reverse spiral groove, and the reverse spiral groove 111 in the second sub-groove 1132 is the second reverse spiral groove. Of course, in other embodiments of the present invention, the number of sub-grooves 113 can be more, that is, the plurality of sub-grooves 113 also include a third sub-groove, a fourth sub-groove, and so on.

[0068] In one embodiment, the number of the reverse spiral grooves 111 in the main groove 112 is 6 to 48. The angle between the tangent lines of two adjacent side walls of the reverse spiral grooves 111 in the main groove 112 is 5° to 80°. In this embodiment, the number of the main reverse spiral grooves 111 is 6 to 48. Preferably, the number of the reverse spiral grooves 111 in the main groove 112 is 12 to 24. Figure 3 As shown, the angle between the tangent lines of the two adjacent side walls of the main reverse spiral groove is α2, and the angle α2 between the tangent lines of the two adjacent side walls of the main reverse spiral groove is in the range of 5° to 80°. Preferably, the angle α2 between the tangent lines of the two adjacent side walls of the reverse spiral groove 111 in the main groove 112 is in the range of 15° to 30°.

[0069] In one embodiment, the number of the reverse spiral grooves 111 in the secondary groove 113 is 2 to 10 times the number of the reverse spiral grooves 111 in the main groove 112. The angle between the tangent lines of two adjacent side walls of the reverse spiral grooves 111 in the secondary groove 113 is 5° to 80°. In this embodiment, the number of the first secondary reverse spiral grooves is 2 to 4 times the number of the main reverse spiral grooves. Figure 3 As shown, the corresponding tangent of two adjacent side walls of the first secondary reverse spiral groove is α3, and the included angle α3 of the corresponding tangent of two adjacent side walls of the first secondary reverse spiral groove is in the range of 5° to 80°. Preferably, the included angle α3 of the corresponding tangent of two adjacent side walls of the first secondary reverse spiral groove is in the range of 15° to 30°. Figure 3 As shown, the corresponding tangent of two adjacent side walls of the first secondary reverse spiral groove is α4, and the number of the second secondary reverse spiral grooves is 5 to 10 times the number of the main reverse spiral grooves. The included angle α4 of the corresponding tangent of two adjacent side walls of the second secondary reverse spiral groove ranges from 5° to 80°. Preferably, the included angle α4 of the corresponding tangent of two adjacent side walls of the second secondary reverse spiral groove ranges from 15° to 30°.

[0070] In one embodiment, the width of the reverse groove group 110 in the radial direction is 1 / 3 to 3 / 4 of the radial width of the sealing ring surface. In this way, a certain number of reverse groove groups 110 can be ensured, thereby ensuring the pumping capacity of the downstream side fluid, while also ensuring the stability of the fluid film and improving the mechanical sealing effect.

[0071] In one embodiment, the groove depth of the reverse spiral groove 111 in the auxiliary groove 113 is greater than the groove depth of the reverse spiral groove 111 in the main groove 112, and the groove depth of the reverse spiral groove 111 in each auxiliary groove 113 increases step by step from the upstream side to the downstream side. In other words, the groove depth of the reverse spiral groove 111 close to the upstream side is deeper than the groove depth of the reverse spiral groove 111 far from the upstream side. In this way, the pumping capacity of the fluid on the downstream side can be gradually enhanced, so that the annular boundary line between the fluid film and the atmosphere can be controlled within a range closer to the downstream side, while ensuring the stability of the fluid film, so that the fluid film covers a wider range on the sealing ring surface, further strengthening the lubrication effect of the fluid film, and effectively improving the working stability and service life of the mechanical seal.

[0072] Optionally, the groove depth of the reverse spiral groove 111 in the main groove 112 is 5μm to 100μm, and the groove depth of the reverse spiral groove 111 in the sub-groove 113 is 1μm to 50μm deeper than the groove depth of the reverse spiral groove 111 in the main groove 112. In this embodiment, the groove depth of the main reverse spiral groove is h2, the groove depth of the first sub-reverse spiral groove is h3, and the groove depth of the second sub-reverse spiral groove is h4. Preferably, the groove depth h2 of the main reverse spiral groove is 10μm to 20μm. The groove depth h3 of the first sub-reverse spiral groove is 1μm to 50μm deeper than the groove depth h2 of the main reverse spiral groove. Preferably, the groove depth h3 of the first sub-reverse spiral groove is 5μm to 10μm deeper than the groove depth h2 of the main reverse spiral groove, that is, h3=h2+5μm to 10μm. The groove depth h4 of the second reverse spiral groove is 1 μm to 50 μm deeper than the groove depth h3 of the first reverse spiral groove. Preferably, the groove depth h4 of the second reverse spiral groove is 5 μm to 10 μm deeper than the groove depth h3 of the first reverse spiral groove, that is, h4=h3+5 μm to 10 μm.

[0073] In one embodiment, a first auxiliary dam area 1141 is formed between the main groove 112 and the adjacent auxiliary groove 113. The ratio of the radial width of the reverse spiral groove 111 in the main groove 112 to the radial width of the first auxiliary dam area 1141 is 0.2 to 5. It can be understood that the ratio of the radial dimension of the groove to the radial dimension of the dam area is recorded as the radial groove-dam ratio. In other words, the ratio of the radial width of the main reverse spiral groove to the radial width of the first auxiliary dam area 1141 is w g2 / w d2 Preferably, the ratio of the radial width of the main reverse spiral groove to the radial width of the first auxiliary dam area 1141 is w g2 / w d2 It is 2 to 3.

[0074] In one embodiment, a second auxiliary dam area 1142 is formed between adjacent auxiliary grooves 113, and the ratio of the radial width of the reverse spiral groove 111 in the auxiliary groove 113 to the radial width of the second auxiliary dam area 1142 is 0.2-5. In this embodiment, the ratio of the radial width of the first auxiliary reverse spiral groove to the radial width of the second auxiliary dam area 1142 is w g3 / w d3 Preferably, the ratio of the radial width of the first secondary reverse spiral groove to the radial width of the second secondary dam area 1142 is w g3 / w d3 The ratio of the radial width of the second secondary reverse spiral groove to the radial width of the second secondary dam area 1142 is w g4 / w d3 Preferably, the ratio of the radial width of the second secondary reverse spiral groove to the radial width of the second secondary dam area 1142 is w g4 / w d3 It is 2 to 3.

[0075] In one embodiment, in the circumferential direction of the main groove 112, a main reverse sealing weir area 115 is formed between adjacent reverse spiral grooves 111, and the ratio of the circumferential width of the reverse spiral groove 111 in the main groove 112 to the circumferential width of the main reverse sealing weir area 115 is l g2 / l d2 In the circumferential direction of the secondary groove 113, a secondary reverse sealing weir area 116 is formed between adjacent reverse spiral grooves 111, and the ratio of the circumferential width of the reverse spiral groove 111 in the secondary groove 113 to the circumferential width of the secondary reverse sealing weir area 116 is 1 / 10 to 1 / 2 of the ratio of the circumferential width of the reverse spiral groove 111 in the main groove 112 to the circumferential width of the main reverse sealing weir area 115.

[0076] It can be understood that the ratio of the circumferential dimension of the above-mentioned groove to the circumferential dimension of the weir area is recorded as the circumferential groove weir ratio. That is to say, the range of the circumferential groove weir ratio of the main reverse spiral groove is 0.2~5. The circumferential groove weir ratio of the reverse spiral groove 111 in the secondary groove 113 is 1 / 10~1 / 2 of the circumferential groove weir ratio of the main reverse spiral groove. In this embodiment, the range of the circumferential groove weir ratio of the main reverse spiral groove is 0.2~5. Preferably, the range of the circumferential groove weir ratio of the reverse spiral groove 111 in the main groove 112 is 1~2. In this embodiment, the secondary reverse sealing weir area 116 of the first secondary groove 1131 is the first secondary reverse sealing weir area 1161, and the secondary reverse sealing weir area 116 of the second secondary groove 1132 is the second secondary reverse sealing weir area 1162. The ratio of the circumferential width of the first secondary reverse spiral groove to the circumferential width of the first secondary reverse sealing weir area 1161 is l g3 / l d3 The ratio of the circumferential width of the second reverse spiral groove to the circumferential width of the second reverse sealing weir area 1162 is l g4 / l d4 It is 0.2~5.

[0077] See also Figures 1 to 3 , at least one main reverse spiral groove corresponds to several first secondary reverse spiral grooves and several second secondary reverse spiral grooves, dividing the multiple reverse groove groups 110 into several groove groups along the circumferential direction. Moreover, there are large intervals between adjacent groove groups. In other words, the size of the sealing weir area between adjacent groove groups gradually increases from the upstream side to the downstream side. In this way, the reverse spiral grooves 111 in each groove group can be distributed in a herringbone shape, so that the pumping capacity of the fluid on the downstream side is gradually enhanced, so that the annular boundary line between the fluid film and the atmosphere can be controlled within a range closer to the downstream side, while ensuring the stability of the fluid film, so that the fluid film covers a wider range on the sealing ring surface, further enhancing the lubrication effect of the fluid film, and improving the working stability and service life of the mechanical seal. In this embodiment, if Figure 1As shown, each main reverse spiral groove corresponds to three first secondary reverse spiral grooves and five second secondary reverse spiral grooves.

[0078] In one embodiment, the sum of the areas of the reverse spiral grooves 111 in the auxiliary grooves 113 is greater than the sum of the areas of the reverse spiral grooves 111 in the main grooves 112, and the sum of the areas of the reverse spiral grooves 111 in the auxiliary grooves 113 gradually increases from the upstream side to the downstream side. In other words, the sum of the areas of the first auxiliary reverse spiral grooves in the first auxiliary grooves 1131 is less than the sum of the areas of the second auxiliary reverse spiral grooves in the second auxiliary grooves 1132. In addition, the width of the forward groove group 120 in the radial direction is 1 / 5 to 1 / 2 of the width of the sealing ring surface.

[0079] In one embodiment, in the forward groove group 120, the number of the forward spiral grooves 121 is 6 to 48. Preferably, the number of the forward spiral grooves 121 is 12 to 24. The angle between the tangent lines of two adjacent side walls of the forward spiral groove 121 is in the range of 5° to 80°. Preferably, Figure 1 As shown, the tangent lines corresponding to the two adjacent side walls of the forward spiral groove 121 are α1, and the angle range α1 of the tangent lines corresponding to the two adjacent side walls of the forward spiral groove 121 is 15° to 30°. The groove depth of the forward spiral groove 121 is 5μm to 100μm. Figure 2 As shown, the groove depth of the forward spiral groove 121 is h1. Preferably, the groove depth h1 of the forward spiral groove 121 is 10 μm to 20 μm.

[0080] In one embodiment, a main dam area 122 is formed between the reverse groove group 110 and the forward groove group 120. The main dam area 122 is the main structure that separates the forward groove group 120 from the reverse groove group 110, and also plays an important role in sealing the sealing end face structure. The ratio of the radial width of the forward spiral groove 121 to the radial width of the main dam area 122 is w g1 / w d1 In other words, the radial groove-dam ratio of the forward spiral groove 121, i.e., w g1 / w d1 is 0.2 to 5. Preferably, the radial groove-dam ratio of the spiral groove, i.e., w g1 / w d1 It is 2 to 3.

[0081] It can be understood that the sealing ring surface realizes static sealing through the dam area, and both the main dam area 122 and the auxiliary dam area 114 can play a sealing role. When the dynamic ring 100 stops running, the main dam area 122 and the auxiliary dam area 114 can still prevent fluid leakage. Furthermore, in the circumferential direction of the forward groove group 120, a positive sealing weir area 123 is formed between adjacent forward spiral grooves 121. The ratio of the circumferential width of the forward spiral groove 121 to the circumferential width of the positive sealing weir area 123 is 0.2 to 5. Preferably, the circumferential groove weir ratio of the forward spiral groove 121, that is, lg1 / l d1 It is 1 to 2.

[0082] In this embodiment, the plurality of sub-grooves 113 include a first sub-groove 1131 and a second sub-groove 1132, the second sub-groove 1132 is located on the downstream side, the first sub-groove 1131 is located between the main groove 112 and the first sub-groove 1131, the reverse spiral groove 111 in the main groove 112 is the main reverse spiral groove, the reverse spiral groove 111 in the first sub-groove 1131 is the first sub-reverse spiral groove, the reverse spiral groove 111 in the second sub-groove 1132 is the second sub-reverse spiral groove, the sub-reverse sealing weir area 116 of the first sub-groove 1131 is the first sub-reverse sealing weir area 1161, and the sub-reverse sealing weir area 116 of the second sub-groove 1132 is the second sub-reverse sealing weir area 1162.

[0083] The number of main reverse spiral grooves is 6 to 48, and the angle range of the corresponding tangents of two adjacent side walls of the main reverse spiral groove is 5° to 80°; the ratio of the radial width of the main reverse spiral groove to the radial width of the first auxiliary dam area 1141 is 0.2 to 5; the ratio of the circumferential width of the main reverse spiral groove to the circumferential width of the main reverse sealing dam area 115 is 0.2 to 5, and the groove depth of the main reverse spiral groove is 5μm to 100μm.

[0084] The number of the first secondary reverse spiral grooves is 2 to 4 times the number of the main reverse spiral grooves, and the angle range of the corresponding tangents of the two adjacent side walls of the first secondary reverse spiral groove is 5° to 80°; the ratio of the radial width of the first secondary reverse spiral groove to the radial width of the second secondary dam area 1142 is 0.2 to 5; the ratio of the circumferential width of the first secondary reverse spiral groove to the circumferential width of the first secondary reverse sealing dam area 1161 is 0.2 to 5, and the groove depth of the first secondary reverse spiral groove is 5μm to 10μm deeper than the groove depth of the main reverse spiral groove.

[0085] The number of the second secondary reverse spiral grooves is 5 to 10 times the number of the main reverse spiral grooves, and the angle range of the corresponding tangents of the two adjacent side walls of the second secondary reverse spiral groove is 5° to 80°; the ratio of the radial width of the second secondary reverse spiral groove to the radial width of the second secondary dam area 1142 is 0.2 to 5; the ratio of the circumferential width of the second secondary reverse spiral groove to the circumferential width of the second secondary reverse sealing dam area 1162 is 0.2 to 5, and the groove depth of the second secondary reverse spiral groove is 5μm to 10μm deeper than the groove depth of the first secondary reverse spiral groove.

[0086] When the dynamic ring 100 rotates with the rotating shaft of the rotating mechanical equipment, on the upstream side, under the dual influence of the pressure difference between the inner and outer diameters of the sealing ring surface and the flow guiding effect of the groove wall of the forward spiral groove 121, the fluid on the upstream side flows radially from the upstream side to the middle of the main dam area 122 of the sealing ring along the forward spiral groove 121, and the fluid film thickness decreases at the groove root of the forward spiral groove 121 close to the main dam area 122, and the squeezing effect of the fluid forms a fluid high pressure area in the main dam area 122. On the downstream side, the fluid flowing along the circumferential direction enters the reverse spiral groove 111, and flows from the downstream side to the main dam area 122 in the middle under the flow guiding effect of the groove wall of the reverse spiral groove 111 to offset the influence of the pressure difference between the inner and outer diameters of the sealing ring, and the fluid film thickness decreases at the groove root of the main reverse spiral groove close to the main dam area 122, and the squeezing effect of the fluid forms a fluid high pressure area in the main dam area 122. Under the dual effect of the forward and reverse spiral grooves 111, the main dam area 122 forms a stable fluid film high pressure area, which prevents the leakage of the fluid to the downstream side. When the upstream pumping capacity of the reverse spiral groove 111 and the pressure difference between the inner and outer diameters reach a balance, an annular dividing line between the sealing medium and the atmosphere will be formed in the reverse spiral groove 111 area, thereby achieving zero leakage of the sealing medium. When the working conditions change and a positive leakage occurs from the upstream side to the downstream side, it indicates that the dividing line is offset to the downstream side, and the upstream pumping capacity of the reverse spiral groove 111 is enhanced, pushing the dividing line to the upstream side, and re-achieving a balance of zero leakage; similarly, when the working conditions change and a reverse leakage occurs from the downstream side to the upstream side, it indicates that the dividing line is offset to the upstream side, and the upstream pumping capacity of the reverse spiral groove 111 is weakened, pushing the dividing line to the downstream side, and re-achieving a balance of zero leakage.

[0087] In one embodiment, the groove wall connection line of each reverse spiral groove 111 in the reverse groove group 110 is a logarithmic spiral, an Archimedean spiral or a circular arc. In one embodiment, the groove wall connection line of each forward spiral groove 121 in the forward groove group 120 is a logarithmic spiral, an Archimedean spiral or a circular arc.

[0088] See also Figure 4 In the second embodiment of the present invention, the sealing end face structure includes a stationary ring and a stationary ring that can rotate relative to the stationary ring. The low-pressure side of the stationary ring or the dynamic ring 100 is the downstream side, and the high-pressure side of the stationary ring or the dynamic ring 100 is the upstream side. The downstream side of the relative surface of the stationary ring or the dynamic ring 100 has a plurality of reverse groove groups 110, and the plurality of reverse groove groups 110 are spaced apart in the radial direction, and each reverse groove group 110 includes a plurality of reverse spiral grooves 111 distributed along the circumferential direction.

[0089] That is to say, compared with the first embodiment, the second embodiment cancels the forward groove group 120. At the same time, the radial width of each reverse groove group 110 is correspondingly increased. At this time, the space between the reverse groove group 110 near the upstream side and the upstream side forms the main dam area 122. This can greatly enhance the pumping capacity downstream of the mechanical seal and is applicable to occasions with a relatively high pressure difference between the upstream and downstream. It should be noted that in the second embodiment, the working principle of the reverse groove group 110 is the same as that of the reverse groove group 110 in the forward groove group 120 in the first embodiment.

[0090] See Figure 5 , in the third embodiment, the number of the first secondary reverse spiral grooves and the number of the second secondary reverse spiral grooves change with the number of the main reverse spiral grooves. That is to say, when the number of the main reverse spiral grooves increases, the number of the first secondary reverse spiral grooves and the number of the second secondary reverse spiral grooves also increase.

[0091] For example, in the first embodiment, as Figure 1 shown, each main reverse spiral groove corresponds to three first secondary reverse spiral grooves and five second secondary reverse spiral grooves. In this embodiment, as Figure 5 shown, the number of the main reverse spiral grooves increases to twice the original number, and the number of the secondary reverse spiral grooves 111 increases accordingly, so that the upstream pumping capacity on the downstream side is further enhanced, the coverage range of the fluid film on the seal end face during stable operation of the seal is increased, and the lubrication performance of the mechanical seal is effectively improved.

[0092] In one embodiment, the forward spiral groove 121 and the reverse spiral groove 111 are formed by laser processing, electrochemical corrosion or electrical discharge machining. This facilitates the formation of the grooves. Moreover, a contact profilometer or a non-contact optical profilometer is used to detect the machining accuracy to ensure the sealing effect of the seal end face structure.

[0093] The seal end face structure of the present invention has several annular seal dam areas, which can effectively achieve zero leakage in the static state of the seal under the action of the elastic element when the seal stops working. Moreover, in some occasions where rotating machinery needs to be started and stopped repeatedly, the reverse spiral grooves 111 in a shape similar to a product character can store a certain amount of sealing medium, which can effectively reduce the friction and wear of the seal end face during the start-stop process and improve the service life of the seal. Under the combined action of the forward and reverse spiral grooves 111, the main dam area 122 of the seal ring face forms a stable fluid high-pressure area, which hinders the flow of the fluid to the downstream side under the influence of the pressure difference between the inner and outer diameters, thereby achieving zero leakage of the seal, and moreover, the sealing performance is more stable, meeting the working requirements of zero leakage and stable performance of many rotating machinery.

[0094] It can be understood that the stability of the sealing end face structure of the present invention in the high-pressure fluid area and the self-adjusting ability of the flow field between the sealing ring faces enable the sealing end face structure to always maintain zero leakage under a wide range of working conditions, and is suitable for occasions where the working conditions of rotating machinery change continuously. On the basis of achieving zero leakage, the reverse spiral grooves 111 in the shape of a similar product character make the pumping ability of the fluid from the main dam area 122 to the downstream side gradually increase, the fluid film covers a wider range on the sealing ring face, and effectively reduces the friction and wear conditions of the downstream sealing end face.

[0095] An embodiment of the present invention further provides a rotating machinery, including a rotating shaft and the sealing end face structure in the above embodiment, and the sealing end face structure is arranged on the rotating shaft. The sealing performance of the fluid is ensured through the sealing end face structure, and the reliable operation of the rotating machinery is ensured.

[0096] The technical features of the above embodiments can be combined arbitrarily. For the sake of concise description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope recorded in this specification.

[0097] The above embodiments only express several implementation manners of the present invention, and the description is relatively specific and detailed, but it cannot be understood as a limitation on the scope of the invention patent of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present invention, several deformations and improvements can still be made, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the invention patent of the present invention shall be subject to the appended claims.

Claims

1. A sealing end face structure of a rotating mechanical device, characterized in that: It comprises a stationary ring and a moving ring which can rotate relative to the stationary ring, wherein the low-pressure side of the stationary ring or the moving ring is the downstream side, and the high-pressure side of the stationary ring or the moving ring is the upstream side; The downstream side of the relative surface of the stationary ring or the dynamic ring has a plurality of reverse groove groups, the plurality of reverse groove groups are spaced apart in the radial direction, and each of the reverse groove groups includes a plurality of reverse spiral grooves distributed in the circumferential direction; the upstream side of the relative surface of the stationary ring or the dynamic ring also has at least one positive groove group, the positive groove group includes a plurality of positive spiral grooves distributed in the circumferential direction, and the rotation direction of the positive spiral groove is opposite to that of the reverse spiral groove; From the downstream side to the upstream side, the number of the reverse spiral grooves in each reverse groove group gradually decreases; Wherein, the plurality of reverse groove groups include a main groove and a plurality of sub-grooves, the plurality of sub-grooves are located between the main groove and the downstream side, a first sub-dam area is formed between the main groove and the adjacent sub-grooves, a second sub-dam area is formed between the adjacent sub-grooves, a main reverse sealing weir area is formed between the adjacent reverse spiral grooves in the circumferential direction of the main groove, a sub-reverse sealing weir area is formed between the adjacent reverse spiral grooves in the circumferential direction of the sub-groove, the plurality of sub-grooves include a first sub-groove and a second sub-groove, the second sub-groove is located on the downstream side, the first sub-groove is located between the main groove and the second sub-groove, the reverse spiral groove in the main groove is the main reverse spiral groove, the reverse spiral groove in the first sub-groove is the first sub-reverse spiral groove, the reverse spiral groove in the second sub-groove is the second sub-reverse spiral groove, and at least one main reverse spiral groove corresponds to several of the first sub-reverse spiral grooves and several of the second sub-reverse spiral grooves; The sum of the areas of the reverse spiral grooves in the secondary grooves is greater than the sum of the areas of the reverse spiral grooves in the main grooves, and the sum of the areas of the reverse spiral grooves in each secondary groove increases gradually from the upstream side to the downstream side, the groove depths of the reverse spiral grooves in the secondary grooves are greater than the groove depths of the reverse spiral grooves in the main grooves, and the groove depths of the reverse spiral grooves in each secondary groove increase step by step from the upstream side to the downstream side; A main dam area is formed between the reverse groove group and the forward groove group, and a forward sealing dam area is formed between adjacent forward spiral grooves in the circumferential direction of the forward groove group.

2. The sealing end surface structure according to claim 1, characterized in that: The number of the reverse spiral grooves in the main groove is 6 to 48, and the angle between the tangent lines of two adjacent side walls of the reverse spiral groove in the main groove is in the range of 5° to 80°; The number of the reverse spiral grooves in the secondary groove is 2 to 10 times the number of the reverse spiral grooves in the primary groove, and the angle between the tangent lines of two adjacent side walls of the reverse spiral grooves in the secondary groove is in the range of 5° to 80°.

3. The sealing end surface structure according to claim 1, characterized in that: The surface where the dynamic ring contacts the static ring is a sealing ring surface, and the width of the reverse groove group along the radial direction is 1 / 3 to 3 / 4 of the radial width of the sealing ring surface.

4. The sealing end surface structure according to claim 3, characterized in that: The groove depth of the reverse spiral groove in the main groove is 5 μm to 100 μm, and the groove depth of the reverse spiral groove in the sub-groove is 1 μm to 50 μm deeper than the groove depth of the reverse spiral groove in the main groove.

5. The sealing end surface structure according to claim 1, characterized in that: The ratio of the radial width of the reverse spiral groove in the main groove to the radial width of the first auxiliary dam area is 0.2 to 5; And / or, the ratio of the radial width of the reverse spiral groove in the auxiliary groove to the radial width of the second auxiliary dam area is 0.2-5.

6. The sealing end surface structure according to claim 1, characterized in that: The ratio of the circumferential width of the reverse spiral groove in the main groove to the circumferential width of the main reverse sealing weir area is 0.2 to 5; The ratio of the circumferential width of the reverse spiral groove in the secondary groove to the circumferential width of the secondary reverse seal weir area is 1 / 10 to 1 / 2 of the ratio of the circumferential width of the reverse spiral groove in the main groove to the circumferential width of the primary reverse seal weir area.

7. The sealing end surface structure according to any one of claims 1 to 6, characterized in that: A first auxiliary dam area is formed between the main groove and the adjacent auxiliary groove, a second auxiliary dam area is formed between the adjacent auxiliary grooves, the auxiliary reverse sealing dam area of ​​the first auxiliary groove is the first auxiliary reverse sealing dam area, and the auxiliary reverse sealing dam area of ​​the second auxiliary groove is the second auxiliary reverse sealing dam area; The number of the main reverse spiral grooves is 6 to 48, the angle between the tangent lines of two adjacent side walls of the main reverse spiral groove is 5° to 80°; the ratio of the radial width of the main reverse spiral groove to the radial width of the first auxiliary dam area is 0.2 to 5; the ratio of the circumferential width of the main reverse spiral groove to the circumferential width of the main reverse sealing weir area is 0.2 to 5, and the groove depth of the main reverse spiral groove is 5 μm to 100 μm; The number of the first secondary reverse spiral grooves is 2 to 4 times the number of the main reverse spiral grooves, and the angle range of the corresponding tangents of two adjacent side walls of the first secondary reverse spiral groove is 5° to 80°; the ratio of the radial width of the first secondary reverse spiral groove to the radial width of the second secondary dam area is 0.2 to 5; the ratio of the circumferential width of the first secondary reverse spiral groove to the circumferential width of the first secondary reverse sealing dam area is 0.2 to 5, and the groove depth of the first secondary reverse spiral groove is 1 μm to 50 μm deeper than the groove depth of the main reverse spiral groove; The number of the second secondary reverse spiral grooves is 5 to 10 times the number of the main reverse spiral grooves, and the angle range of the corresponding tangents of two adjacent side walls of the second secondary reverse spiral groove is 5° to 80°; the ratio of the radial width of the second secondary reverse spiral groove to the radial width of the second secondary dam area is 0.2 to 5; the ratio of the circumferential width of the second secondary reverse spiral groove to the circumferential width of the second secondary reverse sealing dam area is 0.2 to 5, and the groove depth of the second secondary reverse spiral groove is 1μm to 50μm deeper than the groove depth of the first secondary reverse spiral groove.

8. The sealing end surface structure according to claim 7, characterized in that: The number of the first secondary reverse spiral grooves and the number of the second secondary reverse spiral grooves vary with the number of the main reverse spiral grooves.

9. The sealing end surface structure according to any one of claims 1 to 6, characterized in that: The surface where the dynamic ring contacts the static ring is a sealing ring surface, and the width of the positive groove group in the radial direction is 1 / 5 to 1 / 2 of the radial width of the sealing ring surface.

10. The sealing end surface structure according to any one of claims 1 to 6, characterized in that: In the forward groove group, the number of the forward spiral grooves is 6 to 48, the angle between the tangents corresponding to two adjacent side walls of the forward spiral groove is in the range of 5° to 80°, and the groove depth of the forward spiral groove is 5 μm to 100 μm.

11. The sealing end surface structure according to any one of claims 1 to 6, characterized in that: The ratio of the radial width of the forward spiral groove to the radial width of the main dam area is 0.2 to 5; The ratio of the circumferential width of the positive spiral groove to the circumferential width of the positive sealing weir area is 0.2-5.

12. The sealing end surface structure according to any one of claims 1 to 6, characterized in that: The groove wall connection line of each of the reverse spiral grooves in the reverse groove group is a logarithmic spiral line, an Archimedean spiral line or a circular arc line; And / or, a line connecting the groove walls of each of the forward spiral grooves in the forward groove group is a logarithmic spiral, an Archimedean spiral or a circular arc.

Images