Mechanical seal end face structure and high speed pump

Abstract

The utility model relates to mechanical seal technical field provides a kind of mechanical seal end surface structure and high-speed pump, mechanical seal end surface structure includes static ring, moving ring and sealing assembly, moving ring and static ring are oppositely arranged with interval, static ring and moving ring jointly limit out-flowing gap, and flowing gap is used for fluid flow;Sealing assembly is located at least one of static ring and moving ring, sealing assembly includes flow guide groove and multiple spiral grooves, multiple spiral grooves are located at the outer diameter side of sealing assembly, and it is interval setting along the circumference of sealing assembly;The bottom wall of each spiral groove is provided with at least one flow guide groove.The utility model provides mechanical seal end surface structure, to improve the defect that fluid viscosity heat production in existing spiral groove or vortex is easily produced in spiral groove, fluid flow form is optimized by the design of flow guide groove, sealing failure caused by local high temperature is improved, and the reliability and service life of sealing system under high-speed, high viscosity working condition are improved.

Description

Technical Field

[0001] This utility model relates to the field of mechanical seal technology, and in particular to a mechanical seal end face structure and a high-speed pump. Background Technology

[0002] Mechanical seals are critical components in high-speed pump systems used in aerospace and other fields to prevent high-pressure fluid leakage along the shaft. During operation, fluid within the sealing cavity enters the micro-gap at the end face under the shear force and pressure differential of the rotating ring. Through dynamic and static pressure effects, a fluid lubrication film is formed, enabling non-contact operation of the friction pair and achieving zero-wear sealing. Existing technologies generally employ a hydrodynamic structure with micron-level shallow grooves (such as spiral grooves) on the end face to establish the lubrication film. However, under high-speed conditions, the shallow groove structure easily leads to severe viscous heat generation in the fluid within the gap due to intense shearing. High-viscosity fluids are more prone to vaporization phase changes, which can disrupt the stability of the fluid film and even cause seal instability and failure.

[0003] To address this, existing technologies attempt to increase the depth of the spiral groove. However, increasing the depth of the spiral groove will create eddies in the middle of the groove, exacerbating energy dissipation and temperature rise. These risks of viscous heat generation and vaporization severely restrict the reliable application of mechanical seals under high-speed, high-parameter extreme conditions. Utility Model Content

[0004] The first aspect of this utility model provides a mechanical seal end face structure to improve the defects of the prior art, such as the viscous heat generation of fluid in the spiral groove or the easy generation of eddies in the spiral groove. The design of the guide groove optimizes the fluid flow pattern, improves the sealing failure caused by local high temperature, and enhances the reliability and service life of the sealing system under high speed and high viscosity conditions.

[0005] The second aspect of this utility model provides a high-speed pump.

[0006] The mechanical seal end face structure provided by this utility model includes:

[0007] Static ring;

[0008] A moving ring is disposed opposite to the stationary ring at a distance, and the stationary ring and the moving ring together restrict a flow gap for fluid flow;

[0009] A sealing assembly, disposed in at least one of the stationary ring and the rotating ring, the sealing assembly comprising:

[0010] Multiple spiral grooves are provided on the outer diameter side of the sealing assembly and are spaced apart circumferentially along the sealing assembly;

[0011] Each spiral groove has at least one guide groove on its bottom wall.

[0012] According to the mechanical seal end face structure provided by this utility model, the depth of the spiral groove is a, where the value of a ranges from 5μm to 30μm.

[0013] According to the mechanical seal end face structure provided by this utility model, the depth of the guide groove is b, wherein the value of b ranges from 50μm to 1000μm.

[0014] According to the mechanical seal end face structure provided by this utility model, the ratio of the width of the guide groove to the width of the spiral groove is c, where the value of c ranges from 2 / 5 to 3 / 4.

[0015] According to the mechanical seal end face structure provided by this utility model, the helix angle of the guide groove is the same as the helix angle of the helix groove.

[0016] According to the mechanical seal end face structure provided by this utility model, the sealing assembly further includes:

[0017] An annular groove is provided on the inner diameter side of the sealing assembly. The depth of the annular groove is greater than or equal to the depth of the guide groove, and the annular groove is connected to the guide groove.

[0018] According to the mechanical seal end face structure provided by this utility model, the width of the annular groove is d, where the value of d ranges from 2mm to 5mm.

[0019] According to the mechanical seal end face structure provided by this utility model, the inner diameter side of the annular groove is a sealing dam area, and the width of the sealing dam area is e, wherein the value of e ranges from 1mm to 3mm.

[0020] According to the mechanical seal end face structure provided by this utility model, the depth of the annular groove is f, where the value of f ranges from 50μm to 1000μm.

[0021] The high-speed pump provided by this utility model includes the mechanical seal end face structure described in any of the preceding claims.

[0022] In the mechanical seal end face structure provided by this utility model embodiment, when the fluid flows through the spiral groove, it is easy to form a vortex in the middle of the groove. The fluid in the vortex area is circulated and heated, resulting in an aggravated local temperature rise. The addition of the guide groove can form a stepped structure with the spiral groove, thereby guiding the fluid to flow in a direction and undergoing abrupt changes, interrupting the vortex formation path, effectively suppressing the formation of vortex in the middle of the spiral groove, reducing the heat loss due to fluid viscosity, and thus effectively reducing the temperature rise of the sealing end face.

[0023] Compared to the eddy current problem caused by increasing the depth of the spiral groove in the prior art, this invention maintains the dynamic pressure effect while optimizing the fluid flow pattern through the design of the guide groove, improving the local temperature rise acceleration in the eddy current zone, and enhancing the reliability and service life of the sealing system under high-speed and high-viscosity conditions. For high-speed pump systems in aerospace and other fields, it can effectively improve the temperature rise and stability problems of traditional sealing structures under extreme conditions. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0025] Figure 1 This is an exploded structural diagram of the mechanical seal end face structure provided in this embodiment of the utility model.

[0026] Figure 2 This is a front view of the dynamic ring provided in an embodiment of this utility model.

[0027] Figure 3 This is a cross-sectional structural diagram of the moving ring provided in an embodiment of this utility model.

[0028] Figure label:

[0029] 100: stationary ring; 200: moving ring; 300: fluid; 400: sealing assembly; 410: spiral groove; 420: guide groove; 430: annular groove; 440: sealing weir area; 450: sealing dam area. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0031] In the description of the embodiments of this application, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this application based on the specific circumstances.

[0032] In the embodiments of this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0033] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the embodiments of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0034] Figure 1 This is an exploded structural diagram of the mechanical seal end face structure provided in this embodiment of the utility model; Figure 2 This is a front view of the dynamic ring provided in an embodiment of this utility model.

[0035] See Figure 1 and Figure 2The first aspect of this utility model provides a mechanical seal end face structure, which includes a sealing pair composed of a stationary ring 100 and a rotating ring 200. The stationary ring 100 and the rotating ring 200 are disposed opposite each other at a distance to form a flow gap for the flow of fluid 300. A sealing assembly 400 is disposed on at least one of the stationary ring 100 and the rotating ring 200. That is, the sealing assembly 400 can be disposed on the stationary ring 100, the rotating ring 200, or both. The specific structures of the rotating ring 200 and the stationary ring 100 can be found in the prior art, and will not be described in detail here.

[0036] The sealing assembly 400 includes multiple spiral grooves 410 and flow guide grooves 420. The spiral grooves 410 are disposed on the outer diameter side of the sealing assembly 400 (the inner diameter side and outer diameter side refer to the side closer to the center of the stationary ring 100 and the moving ring 200 along the radial direction of the stationary ring 100 and the moving ring 200, which is the inner diameter side, and the side farther from the center of the stationary ring 100 and the moving ring 200 is the outer diameter side; according to the flow direction of the fluid 300, the outer diameter side can also be called the upstream side, and the inner diameter side can also be called the downstream side). The multiple spiral grooves 410 are evenly spaced along the circumference of the moving ring 200, and the non-groove areas on both sides of the spiral grooves 410 constitute the sealing weir area 440. The bottom wall of each spiral groove 410 is provided with at least one flow guide groove 420, that is, in some optional embodiments, the bottom wall of each spiral groove 410 can also be provided with two or more flow guide grooves 420.

[0037] In one optional embodiment, the guide groove 420 is positioned in the middle of the spiral groove 410 to interrupt the vortex path. In another optional embodiment, when the circumferential groove width of the spiral groove 410 is large, two guide grooves 420 can be provided within a single spiral groove 410 to further refine the fluid 300 guiding path.

[0038] The sealing principle of the mechanical seal end face structure: Taking a high-speed pump as an example, the fluid 300 in the sealing cavity of the high-speed pump enters the flow gap under the combined effect of the high-speed rotation of the rotating ring 200 and the pressure difference between the inner and outer diameters. The fluid in the spiral groove 410 generates a dynamic pressure effect, ensuring that the friction pair of the rotating ring 200 and the stationary ring 100 operates in non-contact. When the fluid 300 flows through the spiral groove 410, it is easy to form a vortex in the middle of the channel. The fluid in the vortex area is circulated and heated, resulting in an aggravated local temperature rise. The addition of the guide groove 420 can form a stepped structure with the spiral groove 410, which can guide the fluid 300 to flow in a direction and undergo abrupt changes, interrupting the vortex formation path and reducing the heat loss due to fluid viscosity.

[0039] See Figure 1 and Figure 2It is understood that in the mechanical seal end face structure provided by this utility model embodiment, the stepped structure from the spiral groove 410 to the guide groove 420 is formed by the design of the guide groove 420, which effectively suppresses the formation of vortices in the middle of the spiral groove 410, reduces the heat dissipation due to the viscosity of the fluid 300, and thus effectively reduces the temperature rise of the sealing end face. Compared with the vortex problem caused by increasing the groove depth of the spiral groove 410 in the prior art, this utility model optimizes the flow pattern of the fluid 300 by designing the guide groove 420 while maintaining the dynamic pressure effect, improves the formation of the vortex zone in the middle of the spiral groove channel, and enhances the reliability and service life of the sealing system under high-speed and high-viscosity conditions; for high-speed pump systems in aerospace and other fields, it can effectively improve the temperature rise and stability problems of traditional sealing components 400 under extreme conditions.

[0040] Figure 3 This is a cross-sectional structural diagram of the moving ring provided in an embodiment of this utility model.

[0041] See Figure 3 In an optional embodiment of this utility model, the depth of the spiral groove 410 is 'a', where the value of 'a' ranges from 5μm to 30μm. For example, 'a' can be 5μm, 10μm, 15μm, 25μm, or 30μm. The selection of the depth range of the spiral groove 410 is based on the balance requirement between the hydrodynamic effect of the fluid 300 and eddy current suppression: when the depth of the spiral groove 410 is less than 5 micrometers, the hydrodynamic effect of the fluid may be poor, making it difficult to form a stable lubricating film; when the depth exceeds 30 micrometers, the fluid 300 is prone to forming a large area of ​​eddy currents in the middle of the channel, which exacerbates energy dissipation and temperature rise.

[0042] In practical implementation, the depth of the spiral groove 410 can be flexibly adjusted from 5 micrometers to 30 micrometers depending on the actual working conditions. For example, at a rotation speed of 5000 rpm, the depth of the spiral groove 410 can be selected as 15 micrometers; while at a high-speed working speed of 25000 rpm, the depth can be increased to 25 micrometers to reduce the end face temperature. The depth of the guide groove 420 is always greater than the depth of the spiral groove 410 (e.g., a 30-micrometer spiral groove 410 paired with a 900-micrometer guide groove 420) to ensure that the eddies are effectively broken.

[0043] See Figure 3It is understood that in the mechanical seal end face structure provided by this utility model embodiment, by setting a guide groove 420 in the spiral groove 410, the limitation of the spiral groove 410 depth on the eddy current problem can be broken, so that the upper limit of the spiral groove 410 depth can be increased from 10μm commonly used in the prior art to 30μm. Under the synergistic effect of the guide groove 420, the spiral groove 410 in this range retains sufficient dynamic pressure effect to maintain liquid film stability, and improves the eddy current problem that is easily caused by traditional groove structures (such as exceeding 10 micrometers). At the same time, the increase in depth reduces the shear strength of the fluid 300, further suppresses viscous heat generation, and improves the sealing instability problem caused by temperature rise under high parameter conditions.

[0044] In an optional embodiment of this utility model, the helix angle of the spiral groove 410 ranges from 12° to 28°, the circumferential groove width of the spiral groove 410 ranges from 5mm to 20mm, the ratio of the radial width of the spiral groove 410 to the total width of the sealing end face ranges from 0.3 to 0.7, and the number of spiral grooves 410 ranges from 6 to 24. Regarding the dimensions of the spiral groove 410 in this embodiment, in actual use, they can be adaptively selected according to the actual situation, or the parameters of the spiral groove 410 in the prior art can be referred to for adaptive selection. In this regard, it will not be elaborated further.

[0045] Continue reading Figure 3 In the mechanical seal end face structure provided in this embodiment of the utility model, the depth of the guide groove 420 is b, where the value of b ranges from 50μm to 1000μm. For example, b can be 50μm, 100μm, 300μm, 500μm, 800μm, or 1000μm. The design of this depth range is based on the balance between eddy current suppression and heat dissipation efficiency: when the depth is less than 50 micrometers, the fluid 300 path jump is insufficient, making it difficult to effectively interrupt the eddy current in the middle of the spiral groove 410, and the exchange of hot and cold fluids is limited; when the depth exceeds 1000 micrometers, the leakage increases significantly, affecting the sealing stability.

[0046] In practical implementation, the depth of the guide channel 420 can be flexibly adjusted according to the operating conditions. For example, at a rotation speed of 5000 rpm, the depth of the guide channel 420 can be selected as 100 micrometers; at a high-speed operation of 25000 rpm, the depth can be increased to 500 micrometers to enhance the heat exchange effect. In addition, when the circumferential width of the spiral groove 410 is large (e.g., 20 mm), multiple guide channels 420 can be set in a single groove (e.g., two guide channels 420 with a width of 5 mm each), with the depth maintained in the range of 50 to 1000 micrometers.

[0047] Continue reading Figure 3It is understood that in the mechanical seal end face structure provided by this utility model embodiment, by limiting the depth of the guide groove 420 within the aforementioned range, and based on the stepped fluid path design, the formation of eddies within the spiral groove 410 is effectively suppressed, which can avoid the fluid circulation heating in the eddy zone, thereby effectively reducing local temperature rise. In addition, the design with a maximum depth of 1000 micrometers avoids excessive leakage, ensuring the reliability of the sealing system under high-speed extreme operating conditions.

[0048] Continue reading Figure 2 and Figure 3 In an optional embodiment of this utility model, the ratio of the width of the guide groove 420 to the width of the spiral groove 410 is c, where c ranges from 2 / 5 to 3 / 4. For example, b can be 2 / 5, 1 / 2, 3 / 5, or 3 / 4. This ratio range is designed based on the synergistic optimization of dynamic pressure effect and eddy current suppression: if the width ratio of the guide groove 420 is too low (e.g., less than 2 / 5), its fluid 300 guiding ability is insufficient, making it difficult to effectively interrupt the eddy current in the middle of the spiral groove 410, and the exchange of hot and cold fluids is limited; if the ratio is too high (e.g., more than 3 / 4), the guide groove 420 occupies too much space in the spiral groove 410, weakening the dynamic pressure effect and causing a decrease in the stability of the lubricating film. Therefore, by limiting the ratio, it can be ensured that the guide groove 420 forms an effective fluid 300 channel within the spiral groove 410 while retaining a sufficient dynamic pressure action area.

[0049] In practical implementation, the width ratio of the guide groove 420 can be flexibly adjusted according to the actual width of the spiral groove 410. For example, when the spiral groove 410 is 10 mm wide, the width of the guide groove 420 can be selected as 4 mm (c=0.4) or 7.5 mm (c=0.75); when the spiral groove 410 is 20 mm wide, the width of the guide groove 420 can be 8 mm (c=0.4) or 15 mm (c=0.75). In addition, if the circumferential width of the spiral groove 410 is large (such as 20 mm), multiple guide grooves 420 can be set in a single groove (such as two guide grooves 420 with a width of 5 mm each), wherein the total width ratio of the multiple guide grooves 420 still meets the requirement of 2 / 5 to 3 / 4.

[0050] Continue reading Figure 2 It is understood that in the mechanical seal end face structure provided by this utility model embodiment, when the width ratio of the guide groove 420 is in the range of 2 / 5 to 3 / 4, this ratio not only occupies enough space to guide the fluid 300 to flow in a directional manner and interrupt the vortex path, but also avoids excessive encroachment on the spiral groove 410 area, maintains the dynamic pressure effect, that is, effectively suppresses the formation of vortex and reduces local temperature rise.

[0051] In an optional embodiment of this invention, the helix angle of the guide groove 420 is the same as that of the helix angle of the helix groove 410. This design optimizes the movement trajectory of the fluid 300 on the sealing end face by maintaining the consistency of the flow direction of the two groove structures. The same helix angle means that the extension direction of the guide groove 420 is parallel to the helix of the helix groove 410, which can avoid additional flow resistance caused by angular deviation.

[0052] For example, when the helix angle of the spiral groove 410 is 18 degrees, the helix angle of the guide groove 420 is also set to 18 degrees; if the helix angle of the spiral groove 410 is adjusted to 22 degrees, the helix angle of the guide groove 420 is also adjusted to 22 degrees simultaneously. In addition, within the allowable range of operating conditions, the helix angle of the guide groove 420 can have a deviation of ±5 degrees from the helix angle of the spiral groove 410 (for example, when the spiral groove 410 is 20 degrees, the guide groove 420 can be 15 degrees or 25 degrees), but it must be ensured that the deviation will not significantly weaken the eddy current suppression effect.

[0053] It is understood that in the mechanical seal end face structure provided by this embodiment of the invention, the fluid 300 undergoes rotational shearing within the spiral groove 410 to form a directional flow. When the helix angle of the guide groove 420 is consistent with that of the spiral groove 410, the flow path of the fluid 300 from the spiral groove 410 into the guide groove 420 is smoothly transitioned, which can avoid turbulence or energy dissipation caused by abrupt angle changes. From another perspective, the design of the consistency between the helix angle of the guide groove 420 and the helix angle of the spiral groove 410 reduces flow resistance by optimizing the continuity of fluid 300 movement.

[0054] Continue reading Figure 2 and Figure 3 In an optional embodiment of the present invention, the sealing assembly 400 further includes an annular groove 430, which is disposed on the inner diameter side (i.e., downstream side) of the sealing assembly 400. Its depth is greater than or equal to the depth of the guide groove 420, and the annular groove 430 is connected to the guide groove 420. The annular groove 430 serves as the end of the heat dissipation channel and, together with the guide groove 420, forms a complete fluid 300 guiding path.

[0055] In practice, the relationship between the depth of the annular groove 430 and the depth of the guide groove 420 can be flexibly configured: for example, when the depth of the guide groove 420 is 100 micrometers, the depth of the annular groove 430 can be 120 micrometers (greater than the guide groove 420); when the depth of the guide groove 420 is 500 micrometers, the depth of the annular groove 430 can also be set to 500 micrometers (equal to the guide groove 420).

[0056] Continue reading Figure 2 and Figure 3It is understood that in the mechanical seal end face structure provided in this embodiment of the present invention, the fluid 300 is subjected to the rotational shearing action of the rotating ring 200 in the spiral groove 410 to form a dynamic pressure lubrication film. The guide channel 420 directionally guides the fluid into the downstream annular groove 430. Because the depth of the annular groove 430 is greater than that of the spiral groove 410, it can form a collection area, which enhances the static pressure effect of the fluid 300 in the annular groove 430. Secondly, the moving ring 200 drives the flow to flow at high speed in the annular groove 430, which will generate centrifugal force radially outward. This centrifugal force is directed towards the guide channel 420 and the spiral groove 410. After the fluid 300 in the guide channel 420 enters the annular groove 430, it will generate backflow under the impetus of centrifugal force. In summary, based on the dynamic pressure effect, static pressure effect, the law of conservation of medium exchange, and the existence of centrifugal force, the high-temperature fluid 300 and the low-temperature fluid 300 in the sealed cavity will be forcibly mixed, which will improve the convective heat transfer effect, effectively control the liquid film temperature field distribution, and avoid failure problems such as liquid film vaporization and end face deformation under high-temperature conditions.

[0057] In addition, the annular groove 430 can increase the convective heat transfer area between the high-temperature fluid 300 on the inner diameter side and the fluid 300 on the outer diameter side of the sealing end face, which is also beneficial to the temperature reduction. At the same time, the throttling and pressure reducing structure of the annular groove 430, that is, the "static pressure zone" formed in the annular groove 430, blocks the diffusion of the high pressure zone generated by the spiral groove 410 to the downstream side, which can balance the radial pressure distribution and effectively reduce the pressure gradient of the fluid 300 on the inner diameter side, so that the sealing leakage rate can be effectively controlled.

[0058] Compared to the prior art structure that relies solely on the spiral groove 410, this embodiment of the invention pre-interrupts the vortex and guides the fluid 300 to flow in a directional manner due to the depth jump effect of the guide groove 420, followed by secondary mixing through the annular groove 430, which can improve the temperature drop effect from multiple dimensions. This improvement balances the contradiction of increased leakage or insufficient heat dissipation caused by increasing the groove depth in the traditional technology, providing a reliable solution for high-parameter operating conditions.

[0059] Continue reading Figure 2 In an optional embodiment of this utility model, the width of the annular groove 430 is d, where the value of d ranges from 2mm to 5mm. For example, the value of b is 2mm, 3mm, 4mm or 5mm. The selection of this width range is based on the balance between heat dissipation efficiency and leakage control: when the width of the annular groove 430 is less than 2mm, the mixing space of the fluid 300 is insufficient, and the heat dissipation efficiency is limited; when the width exceeds 5mm, the effective width of the sealing dam area 450 is reduced, which will lead to a significant increase in leakage.

[0060] In practical implementation, the width of the annular groove 430 can be flexibly adjusted according to the size of the sealing ring: for example, when the inner diameter of the sealing ring is 40 mm, the width of the annular groove 430 can be selected as 2 mm (the width of the sealing dam area 450 is about 3 mm); when the inner diameter is 50 mm, the width can be selected as 5 mm (the width of the sealing dam area 450 is about 2 mm). When the radial space of the sealing end face is limited, the width of the annular groove 430 can be set to a lower limit of 2 mm; under high-speed and high heat dissipation requirements, the width can be increased to an upper limit of 5 mm to enhance fluid 300 mixing.

[0061] Continue reading Figure 2 It is understood that in the mechanical seal end face structure provided by this utility model embodiment, when the width of the annular groove 430 is in the range of 2 mm to 5 mm, its space is sufficient to promote the full heat exchange of the hot and cold fluids 300, while avoiding excessive narrowing of the sealing dam area 450.

[0062] Continue reading Figure 2 In an optional embodiment of this utility model, a sealing dam area 450 (non-groove area) is provided on the inner diameter side of the annular groove 430. The width e of the sealing dam area 450 is in the range of 1mm to 3mm, for example, e is 1mm, 2mm or 3mm. The design of this size range is based on the balance between sealing reliability and heat dissipation efficiency: if the width of the sealing dam area 450 is less than 1mm, its ability to block the leakage of fluid 300 is insufficient, and high-pressure fluid 300 is easy to flow directly to the low-pressure side; if the width exceeds 3mm, it occupies too much radial space and affects the heat dissipation area layout of the annular groove 430.

[0063] In practical implementation, the width of the sealing dam area 450 can be adjusted according to the working conditions. For example, when the inner diameter of the sealing ring is 40 mm, the width of the dam area can be selected as 1.5 mm; when the inner diameter is 50 mm, the width can be selected as 3 mm. In addition, when the width of the annular groove 430 is large (such as 5 mm), the width of the dam area can be taken as the upper limit of 3 mm to enhance the sealing performance; under working conditions with high heat dissipation requirements, the width can be taken as the lower limit of 1 mm to expand the mixing space of the fluid 300 in the annular groove 430.

[0064] Continue reading Figure 2 It is understood that in the mechanical seal end face structure provided by this utility model embodiment, when the width of the sealing dam area 450 is within the range of 1 mm to 3 mm, an effective throttling barrier can be formed, increasing the resistance of the fluid 300 leakage path and reducing the leakage amount. At the same time, this width range can avoid excessive compression of the annular groove 430 area, ensuring the space required for the mixing of hot and cold fluids 300.

[0065] Continue reading Figure 3In an optional embodiment of this utility model, the depth of the annular groove 430 is f, where f ranges from 50 μm to 1000 μm. For example, f can be 50 μm, 100 μm, 300 μm, 500 μm, 800 μm, or 1000 μm. The selection of this depth range is based on the balance between heat dissipation efficiency and sealing stability: when the depth of the annular groove 430 is less than 50 μm, it will limit the depth of the guide groove 420, resulting in insufficient jump in liquid film thickness, limited reduction in the shearing effect of fluid 300, and insignificant cooling effect; when the depth exceeds 1000 μm, the leakage will increase sharply, the throttling effect of the sealing dam area 450 will be weakened, and the sealing reliability will be affected.

[0066] In practical implementation, the depth of the annular groove 430 can be flexibly adjusted based on the depth of the guide groove 420: for example, when the depth of the guide groove 420 is 100 micrometers, the depth of the annular groove 430 can be 120 micrometers (greater than the guide groove 420); when the depth of the guide groove 420 is 500 micrometers, the depth of the annular groove 430 can be set to 500 micrometers (equal to the guide groove 420). Furthermore, when there is sufficient axial space along the mechanical seal end face structure, the depth of the annular groove 430 can be set to an upper limit of 1000 micrometers to enhance heat dissipation; under conditions with strict leakage control requirements, the depth can be set to a lower limit of 50 micrometers.

[0067] Continue reading Figure 3 It is understood that in the mechanical seal end face structure provided in this embodiment of the present invention, after the high-temperature fluid 300 flows directionally into the annular groove 430 through the guide groove 420, under the aforementioned dimensional constraints, the fluid film thickness in the groove area of ​​the annular groove 430 is relatively large, thus effectively reducing the shear rate of the fluid 300 and decreasing the viscous heat generation. Simultaneously, the area within the annular groove 430 can promote forced convection heat exchange between the low-temperature fluid 300 and the high-temperature fluid 300 within the sealing cavity.

[0068] A second aspect of this utility model provides a high-speed pump, which includes the mechanical seal end face structure described in any of the foregoing embodiments. The mechanical seal end face structure is installed in a sealing cavity between the rotating shaft and the pump housing of the high-speed pump to prevent high-pressure fluid 300 from leaking along the rotating shaft. Specifically, the high-speed pump comprises basic components such as a pump body, impeller, rotating shaft, and sealing cavity. The moving ring 200 of the mechanical seal end face structure is fixed on the rotating shaft and rotates synchronously with the shaft, while the stationary ring 100 is fixed to the pump housing side of the pump body. Depending on the actual working conditions, the sealing end face structure can adopt any combination of the foregoing embodiments. For more detailed assembly instructions of the mechanical seal end face structure and the high-speed pump, please refer to similar products in the prior art, which will not be repeated here.

[0069] After the high-speed pump starts, the impeller drives the medium to flow under pressure within the pump chamber. The rotating shaft drives the rotating ring 200 to rotate at high speed. The fluid 300 in the sealed chamber enters the gap between the sealing end faces, i.e., the flow gap, under the action of pressure difference and shear force of the rotating ring 200. The spiral groove 410 forms a lubricating film through the dynamic pressure effect, and the guide groove 420 inhibits the formation of vortices in the middle of the spiral groove 410 and guides the fluid 300 to flow in a directional direction. If a structure with an annular groove 430 is adopted, the fluid 300 flows into the annular groove 430 through the guide groove 420 and is forced to mix with the low-temperature medium to cool down. The liquid film temperature is reduced through heat exchange, avoiding the vaporization of high-viscosity media. Throughout the process, the multi-stage structure of the sealing end face works together to maintain a non-contact operating state, ensuring the continuous operation of the pump.

[0070] It is understood that the high-speed pump provided in this utility model embodiment, because it includes the mechanical seal end face structure described in any of the foregoing embodiments, also has the beneficial effects of the mechanical seal end face structure in any of the foregoing embodiments; for the high-speed pump, the design of the sealing component 400 effectively suppresses the shear temperature rise of the fluid 300, avoiding the problem of vaporization of the fluid 300 and seal failure caused by overheating in traditional high-speed pump seals.

[0071] Compared to pumps in the prior art that employ shallow grooves or single deep groove sealing structures, this embodiment of the invention utilizes the synergistic heat dissipation effect of the guide groove 420 and the annular groove 430 to maintain a stable liquid film thickness at extreme speeds, reducing the risk of wear. Furthermore, the throttling and pressure-reducing design of the annular groove 430 can simultaneously control the leakage rate, balancing heat dissipation and sealing performance. This improvement is applicable to high-parameter pump equipment in aerospace, petrochemical, and other fields, solving the temperature rise bottleneck caused by high-speed operation.

[0072] It should be noted that the technical solutions in the various embodiments of this utility model can be combined with each other, but the basis for such combination is that they can be implemented by those skilled in the art. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such combination of technical solutions does not exist, that is, it is not within the protection scope of this utility model.

[0073] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this utility model, and not to limit it. Although this utility model has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this utility model.

Claims

1. A mechanical seal end face structure characterized by, include: Static ring (100); A moving ring (200) is disposed opposite to the stationary ring (100) at a distance. The stationary ring (100) and the moving ring (200) together restrict a flow gap for fluid (300) to flow. A sealing assembly (400) is disposed in at least one of the stationary ring (100) and the rotating ring (200), the sealing assembly (400) comprising: Multiple spiral grooves (410) are provided on the outer diameter side of the sealing assembly (400) and are spaced apart circumferentially along the sealing assembly (400); The bottom wall of each of the spiral grooves (410) is provided with at least one guide groove (420).

2. The mechanical seal face structure of claim 1 wherein, The depth of the spiral groove (410) is a, where the value of a ranges from 5μm to 30μm.

3. The mechanical seal face structure of claim 2 wherein, The depth of the guide groove (420) is b, where the value of b ranges from 50μm to 1000μm.

4. The mechanical seal face structure of claim 1 wherein, The ratio of the width of the guide groove (420) to the width of the spiral groove (410) is c, where the value of c ranges from 2 / 5 to 3 / 4.

5. The mechanical seal face structure of claim 1 wherein, The helix angle of the guide groove (420) is the same as that of the helix groove (410).

6. The mechanical seal face structure according to any one of claims 1 to 5, characterized by The sealing assembly (400) further includes: An annular groove (430) is provided on the inner diameter side of the sealing assembly (400), the depth of the annular groove (430) is greater than or equal to the depth of the guide groove (420), and the annular groove (430) is connected to the guide groove (420).

7. The mechanical seal face structure of claim 6 wherein, The width of the annular groove (430) is d, where the value of d ranges from 2mm to 5mm.

8. The mechanical seal face structure of claim 6 wherein, The inner diameter side of the annular groove (430) is a sealing dam area (450), and the width of the sealing dam area (450) is e, wherein the value of e ranges from 1mm to 3mm.

9. The mechanical seal face structure of claim 6 wherein, The depth of the annular groove (430) is f, where the value of f ranges from 50μm to 1000μm.

10. A high speed pump characterized by, Includes the mechanical seal end face structure as described in any one of claims 1 to 9.

Images