Radial deep hole impact type mechanical seal ring body structure and mechanical seal device

Abstract

The application relates to a radial deep-hole impact type mechanical seal ring body structure and a mechanical seal device, and belongs to the technical field of mechanical seals. The radial deep-hole impact type mechanical seal ring body structure comprises a sealing moving ring and a sealing stationary ring. The sealing moving ring and the sealing stationary ring both have sealing end faces. The outer rings of the sealing moving ring and the sealing stationary ring are used for being in communication with a sealing medium. A plurality of impact flow channels are arranged on the outer circumferential surfaces of the sealing moving ring and / or the sealing stationary ring. The radial depth of the impact flow channels on the corresponding sealing moving ring or sealing stationary ring is less than the width of the sealing end face on the corresponding sealing moving ring or sealing stationary ring. The application has the effect of improving the heat dissipation capacity of the mechanical seal under high-parameter working conditions, and the problem of thermal deformation and wear caused by excessively high end face temperature rise.

Description

Technical Field

[0001] This application relates to the field of mechanical seal technology, and in particular to a radial deep-hole impact mechanical seal ring structure and mechanical seal device. Background Technology

[0002] Mechanical seals are shaft sealing components widely used in rotating machinery such as centrifugal pumps, reactors, and compressors due to their high reliability, long service life, and good sealing performance. The sealing principle of mechanical seals mainly relies on the preload of elastic elements and fluid pressure to bring the stationary and rotating rings into contact, achieving a face seal. With increasingly demanding operating conditions, the sealing face generates a large amount of heat due to intense friction, causing a rapid rise in face temperature. Excessive temperature not only causes thermal deformation and accelerated wear of the sealing ring material but may also lead to vaporization or coking of the sealing medium, resulting in seal failure. Therefore, effectively controlling the face temperature rise is a core challenge in improving the performance and lifespan of mechanical seals.

[0003] Currently, to alleviate the temperature rise problem of the sealing end face, related technologies generally adopt the method of setting micro-textures such as micron-level shallow grooves and micro-pits on the sealing end face to improve local lubrication conditions and enhance heat dissipation. However, due to the microscopic scale of the sealing end face microtexture, its heat exchange capacity is still insufficient under harsh conditions such as high speed, high temperature and high pressure, making it difficult to effectively suppress the accumulation of heat on the sealing end face. Summary of the Invention

[0004] To help improve the problems of insufficient heat dissipation capacity and excessive end face temperature rise leading to thermal deformation and wear of mechanical seals under high parameter conditions, this application provides a radial deep hole impact mechanical seal ring structure and mechanical seal device.

[0005] Firstly, this application provides a radial deep-hole impact mechanical seal ring structure, which adopts the following technical solution: A radial deep-hole impact mechanical seal ring structure includes a sealing rotating ring and a sealing stationary ring. Both the sealing rotating ring and the sealing stationary ring have sealing end faces. The outer rings of the sealing rotating ring and the sealing stationary ring are used to communicate with the sealing medium. Multiple impact channels are formed on the outer circumferential surface of the sealing rotating ring and / or the sealing stationary ring. The radial depth of the impact channels on the corresponding sealing rotating ring or sealing stationary ring is less than the width of the sealing end face on the corresponding sealing rotating ring or sealing stationary ring.

[0006] Preferably, the distance from the central axis of the impact flow channel to the sealing end face of the corresponding sealing moving ring or sealing stationary ring is 1mm-6mm.

[0007] Preferably, the radial depth of the impact flow channel on the corresponding sealing moving ring or sealing stationary ring is 50%-90% of the width of the sealing end face on the corresponding sealing moving ring or sealing stationary ring.

[0008] Preferably, the cross-sectional area of ​​the impact channel is 1mm²-60mm².

[0009] Preferably, the plurality of impact channels are evenly spaced along the circumference of the corresponding sealing moving ring or sealing stationary ring, and the number of impact channels on the sealing moving ring and / or sealing stationary ring is 6-90.

[0010] Preferably, the impact flow channel extends toward the inner circumferential surface of the corresponding sealing moving ring or sealing stationary ring, and the extension path of the impact flow channel is straight, oblique, or curved.

[0011] Preferably, when the extension path of the impact channel is oblique, the angle between the central axis of the impact channel and the radial centerline of its corresponding position is greater than 0° and less than or equal to 60°.

[0012] Preferably, the cross-sectional shape of the impact channel is circular, I-shaped, or polygonal.

[0013] Preferably, the extension path of the impact flow channel is V-shaped, and both ends of the impact flow channel are located on the outer circumferential surface of the corresponding sealing dynamic ring or sealing stationary ring. The angle between the axis of the opening at one end of the impact flow channel and the radial center line is greater than the angle between the axis of the opening at the other end and the radial center line.

[0014] Secondly, the mechanical seal device provided in this application adopts the following technical solution: A mechanical seal device includes the aforementioned radial deep-hole impact mechanical seal ring structure, and further includes a bushing and a gland. The bushing is fixedly connected to a rotating shaft to rotate with the shaft. The rotating sealing ring is mounted on the bushing. The gland is connected to the equipment housing. The stationary sealing ring is axially slidably connected to the gland via an elastic element. A sealing cavity is formed between the gland, the rotating sealing ring, and the stationary sealing ring. The gland has a sealing medium inlet channel and a sealing medium outlet channel, both of which communicate with the sealing cavity. The sealing medium inlet channel is aligned with the sealing end faces of the rotating and stationary sealing rings and is inclined. The angle between the axis of the sealing medium inlet channel and the radial center line passing through the opening of the channel is equal to the angle between the axis of the water-facing end of the impact flow channel and the radial center line passing through the opening of the flow channel.

[0015] In summary, this application includes the following beneficial technical effects: In sealed operation, the sealing ring rotates at high speed with the shaft. The high-pressure, relatively low-temperature sealing medium continuously rushes into the sealing cavity, and under the action of dynamic water pressure, it flows from the outside along the impact channel inwards, generating impact flow. When the fluid impacts the bottom of the hole, kinetic energy is converted into pressure energy. After the impact, the fluid absorbs a large amount of heat and is subsequently thrown out again by centrifugal force along the hole wall or under the action of eddies. This forms a certain degree of convection of the sealing medium, which helps to quickly transfer the frictional heat generated on the sealing end face of the sealing ring to the flowing medium and carry it away efficiently. Simultaneously, the rotation of the sealing ring drives the sealing... The sealing medium on the outer ring of the stationary ring rotates synchronously. When this high-speed rotating circumferential fluid sweeps across the opening of the impact channel on the outer circumference of the stationary ring, the fluid passing through the orifice at high speed induces one or more secondary vortices inside the impact channel. These vortices force the hot fluid in the orifice to flow out of the orifice, while simultaneously entraining the cold sealing medium in the sealing cavity into the impact channel. This creates a continuous alternation of media within the impact channel of the stationary ring, significantly reducing the working temperature of the sealing end face of the stationary ring. This helps to improve the problem of insufficient heat dissipation capacity of mechanical seals under high-parameter operating conditions, and the problem of excessive end face temperature rise that easily leads to thermal deformation and wear. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of Embodiment 1 of this application.

[0017] Figure 2 This is a partial structural cross-sectional view of the sealing dynamic ring or sealing stationary ring in Embodiment 1 of this application.

[0018] Figure 3 This is a partial structural cross-sectional view of the sealing dynamic ring or sealing stationary ring in Embodiment 2 of this application.

[0019] Figure 4 This is a schematic diagram of the overall structure of Embodiment 3 of this application.

[0020] Figure 5 This is a schematic diagram of the overall structure of Embodiment 4 of this application.

[0021] Figure 6 This is a schematic diagram of the overall structure of Embodiment 5 of this application.

[0022] Figure 7 This is a partial structural cross-sectional view of the sealing dynamic ring or sealing stationary ring in Embodiment 5 of this application.

[0023] Figure 8 This is a schematic diagram of the overall structure of Embodiment 6 of this application.

[0024] Figure 9 This is a partial structural cross-sectional view of the sealing dynamic ring or sealing stationary ring in Embodiment 7 of this application.

[0025] Figure 10This is a structural cross-sectional view of the mechanical seal device in Embodiment 7 of this application.

[0026] Explanation of reference numerals in the attached drawings: 1. Sealing ring; 2. Sealing ring; 3. Sealing end face; 4. Impact flow channel; 5. Shaft sleeve; 6. Gland; 7. Sealing medium inlet channel; 8. Sealing medium outlet channel; 9. Sealing cavity. Detailed Implementation

[0027] The following combination Figures 1-10 This application will be described in further detail.

[0028] Example 1:

[0029] This application discloses a radial deep-hole impact type mechanical seal ring structure. (Refer to...) Figure 1 and Figure 2 The radial deep-hole impact mechanical seal ring structure includes a rotating sealing ring 1 and a stationary sealing ring 2. Both the rotating sealing ring 1 and the stationary sealing ring 2 have sealing end faces 3, which are used to cooperate to form a sealing structure. The outer rings of the rotating sealing ring 1 and the stationary sealing ring 2 are used to communicate with the sealing medium. The sealing medium refers to the flushing medium introduced into the sealing cavity from the outside. The pressure of the flushing medium is greater than the centrifugal force generated by the rotation of the rotating sealing ring 1. Specifically, the flushing medium is usually a treated fluid with the same composition as the internal process medium of the equipment or has no effect on the internal process medium of the equipment. Specifically, the rotating sealing ring 1 and the stationary sealing ring 2 are generally in the form of a ring, and both are usually made of wear-resistant and corrosion-resistant materials.

[0030] Reference Figure 1 and Figure 2 Furthermore, multiple impact channels 4 are formed on the outer peripheral surfaces of the sealing dynamic ring 1 and / or sealing stationary ring 2. In this embodiment, multiple impact channels 4 are formed on the outer peripheral surfaces of both the sealing dynamic ring 1 and the sealing stationary ring 2; in other embodiments, the impact channels 4 on the sealing dynamic ring 1 and the sealing stationary ring 2 can be designed as needed. The radial depth of the impact channel 4 on the corresponding sealing dynamic ring 1 or sealing stationary ring 2 is less than the width of the sealing end face 3 on the corresponding sealing dynamic ring 1 or sealing stationary ring 2.

[0031] In actual assembly, the rotating sealing ring 1 is fixed to the rotating shaft of the equipment via a bushing and rotates synchronously with it, while the stationary sealing ring 2 slides axially within the equipment housing via elastic elements and other structures. The elastic elements provide axial preload for the stationary sealing ring 2. During sealing operation, the rotating sealing ring 1 rotates at high speed with the shaft. The pressure of the high-pressure, relatively low-temperature sealing medium continuously entering the sealing cavity exceeds the centrifugal force generated by the rotating sealing ring 1, causing the sealing medium to flow from the outside along the impact channel 4 to the inside. When the fluid impacts the bottom of the hole, kinetic energy is converted into pressure energy. After the impact, the fluid absorbs a large amount of heat and is subsequently thrown out again by centrifugal force along the hole wall or under the action of eddies, forming convection to a certain extent. This helps to quickly conduct the frictional heat generated on the sealing end faces 3 of the rotating sealing ring 1 and the stationary sealing ring 2 to the flowing medium and efficiently carry it away. Simultaneously, the rotation of the rotating sealing ring 1 will cause the fluid's viscous shear force to... The sealing medium on the outer ring of the dynamic seal stationary ring 2 rotates synchronously. When this high-speed rotating circumferential fluid sweeps across the opening of the impact channel 4 on the outer circumference of the sealing stationary ring 2, the fluid that sweeps across the orifice at high speed will induce one or more secondary vortices inside the impact channel 4. These vortices will force the hot fluid in the impact channel 4 to flow out of the orifice, and at the same time entrain the cold sealing medium in the sealing cavity into the impact channel 4. A continuous medium exchange is formed in the impact channel 4 of the sealing stationary ring 2, which realizes forced heat exchange on the sealing end face 3 on the sealing stationary ring 2. This helps to improve the problem of insufficient heat dissipation capacity of mechanical seals under high parameter conditions, and the problem of excessive end face temperature rise that easily leads to thermal deformation and wear.

[0032] Reference Figure 1 and Figure 2 In this embodiment, the impact channel 4 extends from the outer peripheral surface of the corresponding sealing moving ring 1 or sealing stationary ring 2 toward the corresponding inner peripheral surface, such that the impact channel 4 is a blind hole with its opening located on the outer peripheral surface and does not penetrate the inner peripheral surface. Furthermore, the multiple impact channels 4 are evenly distributed along the circumference of the corresponding sealing moving ring 1 or sealing stationary ring 2, and this uniform distribution can make the cooling and heat dissipation effect more uniform.

[0033] Reference Figure 1 and Figure 2 The axial distance between the central axis of the impact channel 4 and the corresponding sealing end face 3 is 1mm-6mm. In this embodiment, the axial distance is 3mm. Because the impact channel 4 is close to the sealing end face 3, the fluid can instantly carry away the heat generated by friction on the sealing end face 3, thereby effectively suppressing the thermal deformation of the sealing dynamic ring 1 and the sealing stationary ring 2. In other embodiments, the distance between the impact channel 4 and the sealing end face 3 can be set according to actual needs.

[0034] Reference Figure 1 and Figure 2The number of impact channels 4 on the sealing dynamic ring 1 and / or sealing stationary ring 2 is 6-90. Specifically, the number of impact channels 4 on the sealing dynamic ring 1 and sealing stationary ring 2 can be set according to actual needs. For example, in some mechanical seal rings with small outer diameters, only 6-10 impact channels 4 can be set; while in large mechanical seal rings with more demanding operating conditions, 50-90 impact channels 4 can be set. Since too many impact channels 4 may affect the structural strength of the sealing dynamic ring 1 and sealing stationary ring 2, while too few impact channels 4 cannot provide sufficient cooling effect, this application limits the number of impact channels 4 to between 6-90, which not only meets the structural strength requirements but also effectively promotes cooling and heat dissipation.

[0035] Reference Figure 1 and Figure 2 The radial depth of the impact channel 4 on the corresponding sealing ring 1 or sealing ring 2 is 50%-90% of the width of the sealing end face 3 of the corresponding sealing ring 1 or sealing ring 2. The radial depth of the impact channel 4 refers to the projected distance of the impact channel 4 in the radial direction of the corresponding sealing ring 1 or sealing ring 2. If the radial depth of the impact channel 4 is too shallow, the cooling medium may not be able to effectively reach the high-temperature area near the sealing end face 3; if the radial depth of the impact channel 4 is too deep, it may weaken the strength of the corresponding sealing ring, leading to problems such as cracking during operation. Therefore, in this application, the radial depth of the impact channel 4 is 80% of the width of the corresponding sealing end face 3, which can ensure the cooling effect while avoiding excessive impact on the structural strength of the sealing ring.

[0036] Reference Figure 1 and Figure 2 The cross-sectional area of ​​the impingement channel 4 ranges from 1 mm² to 60 mm². Using a suitable cross-sectional area ensures sufficient flow rate and velocity of the cooling medium. If the cross-sectional area is too small, the flow rate of the cooling medium will be limited, preventing it from carrying away heat effectively; if the cross-sectional area is too large, the flow velocity of the cooling medium may be too low, affecting heat exchange efficiency. Therefore, the cross-sectional area of ​​the impingement channel 4 is set according to actual needs. For example, a smaller cross-sectional area can be selected under low-flow conditions, while a larger cross-sectional area is required under high-flow conditions.

[0037] Reference Figure 1 and Figure 2To suit different working conditions, the extension path of the impact channel 4 can be straight, oblique, or curved; the cross-sectional shape of the impact channel 4 can be circular, I-shaped, or polygonal. Furthermore, the extension path and cross-sectional shape of the impact channel 4 on the sealing ring 1 can be designed to be the same as or different from the extension path and cross-sectional shape of the impact channel 4 on the sealing ring 2 as needed; at the same time, the extension paths and cross-sectional shapes of the impact channel 4 on the sealing ring 1 and the sealing ring 2 can be combined as needed.

[0038] Reference Figure 1 and Figure 2 Specifically, in the embodiments of this application, the cross-sectional shape of the impact channel 4 is rectangular, and the extension path of the impact channel 4 is straight. That is, the angle between the central axis of the impact channel 4 and its own radial center line on the corresponding sealing end face 3 is 0°. The impact channel 4 adopts a straight rectangular hole, which not only meets the heat dissipation requirements, but also meets the requirements of low cost and high processing efficiency.

[0039] The implementation principle of Embodiment 1 of this application is as follows: When the seal is running, the sealing ring 1 rotates at high speed with the shaft. The pressure of the high-pressure, relatively low-temperature sealing medium continuously rushing into the sealing cavity is greater than the centrifugal force generated by the sealing ring 1, causing the sealing medium to generate impact flow from the outside along the impact flow channel 4 to the inside. When the fluid hits the bottom of the hole, the kinetic energy is converted into pressure energy. After the impact, the fluid absorbs a large amount of heat, and then is thrown out again by centrifugal force along the hole wall or under the action of eddies. To a certain extent, convection of the sealing medium is formed, which helps to quickly conduct the frictional heat generated on the sealing end face 3 of the sealing ring 1 and the sealing stationary ring 2 to the flowing medium and carry it away efficiently.

[0040] Simultaneously, the rotation of the sealing ring 1 will cause the sealing medium on the outer ring of the sealing stationary ring 2 to rotate synchronously. When this high-speed rotating circumferential fluid sweeps across the opening of the impact channel 4 on the outer circumference of the sealing stationary ring 2, it will induce one or more secondary vortices inside the impact channel 4. These vortices will force the hot fluid in the impact channel 4 to flow out of the orifice, and at the same time, they will entrain the cold sealing medium in the sealing cavity into the impact channel 4. Similarly, a continuous medium exchange is formed in the impact channel 4 of the sealing stationary ring 2, realizing forced heat exchange on the sealing end face 3 on the sealing stationary ring 2. This helps to improve the problem of insufficient heat dissipation capacity of mechanical seals under high parameter conditions, and the problem of excessive end face temperature rise that easily leads to thermal deformation and wear. It can be widely used in the sealing systems of rotating mechanical equipment such as centrifugal pumps, reactors, and compressors.

[0041] Example 2:

[0042] Reference Figure 1 and Figure 3The difference between this embodiment and Embodiment 1 is that the extension path of the impact channel 4 is oblique, that is, the central axis of the impact channel 4 is inclined relative to the radial center line of its own position. Specifically, the angle between the central axis of the impact channel 4 and the radial center line of its own position on the corresponding sealing end face 3 is greater than 0° and less than or equal to 60°. Further, in this embodiment, the angle between the central axis of the impact channel 4 and the radial center line at the corresponding position is 30°.

[0043] The implementation principle of Embodiment 2 of this application is as follows: when the sealing ring 1 rotates with the shaft, the rotation direction of the sealing ring 1 is consistent with the inclination direction of the impact flow channel 4 from the inner circumferential surface to the outer circumferential surface, that is... Figure 3 The rotation direction of the central sealing ring 1 is clockwise; this increases the tangential velocity component on top of the radial impact velocity of the medium, thereby enhancing the pumping effect and disturbance of the fluid, further improving the impact cooling efficiency, and making it suitable for working conditions with high heat dissipation requirements.

[0044] Example 3:

[0045] Reference Figure 4 The difference between this embodiment and embodiment 1 is that the cross-sectional shape of the impact channel 4 is triangular.

[0046] The implementation principle of Embodiment 3 of this application is as follows: the sharp corner structure of the triangular cross section helps to guide the fluid flow, induces a more significant secondary flow in the impact channel 4, effectively destroys the flow boundary layer, and thus enhances the heat exchange between the impact fluid and the inner wall of the impact channel 4.

[0047] Example 4:

[0048] Reference Figure 5 The difference between this embodiment and embodiment 1 is that the cross-sectional shape of the impact channel 4 is I-shaped.

[0049] The implementation principle of Embodiment 4 of this application is as follows: the I-shaped cross-section significantly increases the inner wall surface area of ​​the impact flow channel 4, providing a larger heat exchange area; its unique shape can generate a specific form of disturbance to the impact flow medium, effectively enhancing the fluid mixing and heat exchange intensity, thereby further improving the overall heat dissipation capacity on the basis of straight impact.

[0050] Example 5:

[0051] Reference Figure 6 and Figure 7 The difference between this embodiment and embodiment 1 is that the cross-sectional shape of the impact channel 4 is circular; the extension path of the impact channel 4 is curved.

[0052] The implementation principle of Embodiment 5 of this application is as follows: A circular cross-section is naturally streamlined, minimizing fluid flow resistance and facilitating smooth impact flow of the medium within the curved path. Simultaneously, the curved path significantly extends the flow path and residence time of the sealing medium within the impact channel 4, and easily generates eddies, resulting in a more thorough impact cooling process. Furthermore, the fluid generates centrifugal force as it flows through the curved channel, creating secondary eddies on the cross-section of the impact channel 4. These internal eddies continuously disrupt the thermal boundary layer adhering to the orifice wall. Combined with the minimal flow resistance provided by the circular cross-section, this achieves extremely efficient heat exchange, making it particularly suitable for high-temperature reactor mechanical seal applications.

[0053] Example 6:

[0054] Reference Figure 8 The difference between this embodiment and embodiment 1 is that the cross-sectional shape of the impact channel 4 is a regular hexagon, the extension path of the impact channel 4 is oblique, and the angle between the central axis of the impact channel 4 and the radial center line at the corresponding position is 30°.

[0055] The implementation principle of Embodiment 6 of this application is as follows: The regular hexagonal cross section is an efficient structural form that provides a large flow cross-sectional area and heat exchange area while maintaining a uniform stress distribution on the channel wall and high structural strength.

[0056] Example 7:

[0057] Reference Figure 1 and Figure 9 The difference between this embodiment and Embodiment 1 is that the extension path of the impact channel 4 is V-shaped, and both ends of the impact channel 4 are located on the outer circumferential surface of the corresponding sealing moving ring 1 or sealing stationary ring 2. Furthermore, the angle between the axis of the V-shaped impact channel 4 and the radial centerline at one end is greater than the angle between the axis of the other end and the radial centerline. The V-shaped impact channel 4 can also be designed such that the cross-sectional area of ​​one end is greater than the cross-sectional area of ​​the other end; specifically, the end with the larger angle to the radial centerline has a larger cross-sectional area.

[0058] Reference Figure 1 and Figure 9 The larger cross-sectional area of ​​the impact channel 4 is the water-facing side, used to introduce the sealing medium; the smaller cross-sectional area is the back-water side, where the jet suction effect generated by the fluid passing over the small opening accelerates the discharge of the medium. Furthermore, the inner wall of the impact channel 4 on the water-facing side is provided with spiral microgrooves along its own axial direction.

[0059] During processing, the three-dimensional digital model of the impact channel 4 is imported into the control system of the five-axis femtosecond laser machine tool. The machine tool automatically generates laser tool paths based on the different included angles and cross-sectional areas at both ends of the impact channel 4. First, the channel on the water-facing side of the impact channel 4 is processed. Using the three-dimensional dynamic focusing galvanometer equipped with the femtosecond laser combined with circularly polarized light, the material is removed by a layer-by-layer spiral cutting method. The extremely short pulses of the femtosecond laser cause the material to vaporize instantly without generating microcracks and thermal stress, thus ensuring the strength performance of the sealing ring structure. During the process of advancing towards the bottom of the hole, the laser system is linked with the five axes. By changing the trajectory of the laser focus on the inner wall of the channel, the spiral microgrooves are directly ablated or written. By using the same process and clamping during the advancement of the channel on the water-facing side, the spiral microgrooves on the inner wall are written in the same way, avoiding secondary clamping errors.

[0060] After the flow channel on the water-facing side is machined, the flow channel on the water-repellent side is machined next; after the sealing ring is machined, ultrasonic cleaning and polishing of the sealing end face are performed. This application solves the comprehensive challenges of high-precision irregular flow channel, heat-free processing, and internal wall microstructure machining by using a combination of technologies such as a five-axis femtosecond laser machine tool, a three-dimensional dynamic focusing galvanometer, circularly polarized light, spiral cutting, and controllable ablation of focal trajectory.

[0061] For sealing rings made of materials such as ceramics and silicon carbide, a processing method can be adopted, which involves pressing the sealing ring blank into shape, drilling holes in the sealing ring blank to form a V-shaped channel, then placing graphite rods with a cross-section smaller than the corresponding cross-section at both ends of the V-shaped channel for support, and finally sintering. After sintering, the graphite rods are removed, thereby forming a V-shaped impact flow channel 4 on the sealing ring.

[0062] The implementation principle of the mechanical seal ring structure in Embodiment 7 of this application is as follows: The impact channel 4 is designed as a V-shape with two inclined channels connected, which helps the sealing medium entering the impact channel 4 to be discharged quickly, improves the flow efficiency of the sealing medium, and further enhances the heat dissipation effect on the sealing end face 3; at the same time, the design of the spiral microgroove forcibly breaks the laminar boundary layer of the fluid rushing into the channel on the water-facing side, induces strong micro-vortices inside the impact channel 4, and causes the cold medium to undergo violent convective heat transfer with the high-temperature hole wall, thereby improving the heat transfer effect.

[0063] Embodiment 7 of this application also discloses a mechanical seal device. (Refer to...) Figure 1 and Figure 10The mechanical seal device includes the aforementioned mechanical seal ring structure, and further includes a bushing 5 and a gland 6. The bushing 5 is fixedly connected to the rotating shaft to rotate with it. The rotating sealing ring 1 is fixedly sleeved on the bushing 5. The gland 6 is connected to the equipment housing. The stationary sealing ring 2 is axially slidably connected to the gland 6 via an elastic element. A sealing cavity 9 is formed between the gland 6, the rotating sealing ring 1, and the stationary sealing ring 2. The gland 6 has a sealing medium inlet channel 7 and a sealing medium outlet channel 8, both of which communicate with the sealing cavity 9. The sealing medium inlet channel 7 is used to introduce the sealing medium; the sealing medium outlet channel 8 is used to discharge the sealing medium. The sealing medium inlet channel 7 is aligned with the sealing... The sealing end faces 3 of the rotating ring 1 and the sealing stationary ring 2 are inclined. Furthermore, the sealing medium inlet channel 7 and the sealing medium outlet channel 8 are located on the same side of the central axis of the rotating shaft. The angle between the axis of the sealing medium inlet channel 7 and the radial center line of the rotating shaft at its corresponding position is equal to the angle between the axis of the water-facing end of the impact channel 4 and the radial center line of the rotating shaft at its corresponding position. Under the pressure at the sealing medium inlet channel 7, the sealing medium will enter the impact channel 4 and then leave the inside of the sealing cavity 9 under the action of centrifugal force. The hydraulic pressure outside the sealing cavity 9 is greater than that inside, which helps to increase the flow rate of the sealing medium outlet channel 8. The heat tends to transfer from the inside to the outside of the sealing cavity 9.

[0064] The implementation principle of the mechanical seal device in this embodiment 7 is as follows: When the seal is running, the sealing ring 1 rotates with the shaft, and the sealing medium enters the sealing cavity through the sealing medium inlet channel 7 and then exits through the sealing medium outlet channel 8. When the impact flow channel 4 on the sealing ring 1 passes through the sealing medium inlet channel 7, it can be parallel to the length direction of the sealing medium inlet channel 7, so that the sealing medium can enter the impact flow channel 4 on the sealing ring 1 and / or the sealing stationary ring 2, further improving the cooling and heat exchange effect.

[0065] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. A radial deep-hole impact mechanical seal ring structure, characterized in that: It includes a sealing moving ring (1) and a sealing stationary ring (2), both of which have a sealing end face (3). The outer rings of the sealing moving ring (1) and the sealing stationary ring (2) are used to communicate with the sealing medium. Multiple impact channels (4) are opened on the outer circumferential surface of the sealing moving ring (1) and / or the sealing stationary ring (2). The radial depth of the impact channel (4) on the corresponding sealing moving ring (1) or sealing stationary ring (2) is less than the width of the sealing end face (3) on the corresponding sealing moving ring (1) or sealing stationary ring (2).

2. The radial deep-hole impact mechanical seal ring structure according to claim 1, characterized in that: The distance from the central axis of the impact channel (4) to the sealing end face (3) of the corresponding sealing moving ring (1) or sealing stationary ring (2) is 1mm-6mm.

3. The radial deep-hole impact mechanical seal ring structure according to claim 1, characterized in that: The radial depth of the impact channel (4) on the corresponding sealing moving ring (1) or sealing stationary ring (2) is 50%-90% of the width of the sealing end face (3) on the corresponding sealing moving ring (1) or sealing stationary ring (2).

4. The radial deep-hole impact mechanical seal ring structure according to claim 3, characterized in that: The cross-sectional area of ​​the impact channel (4) is 1 mm²-60 mm².

5. The radial deep-hole impact mechanical seal ring structure according to claim 1, characterized in that: Multiple impact channels (4) are evenly distributed around the circumference of the corresponding sealing ring (1) or sealing ring (2), and the number of impact channels (4) on the sealing ring (1) and / or sealing ring (2) is 6-90.

6. A radial deep-hole impact mechanical seal ring structure according to any one of claims 1-5, characterized in that: The impact flow channel (4) extends toward the inner circumferential surface of the corresponding sealing moving ring (1) or sealing stationary ring (2), and the extension path of the impact flow channel (4) is straight, oblique or curved.

7. The radial deep-hole impact mechanical seal ring structure according to claim 6, characterized in that: When the extension path of the impact channel (4) is oblique, the angle between the central axis of the impact channel (4) and the radial centerline of its corresponding position is greater than 0° and less than or equal to 60°.

8. The radial deep-hole impact mechanical seal ring structure according to claim 6, characterized in that: The cross-sectional shape of the impact channel (4) is circular, I-shaped, or polygonal.

9. A radial deep-hole impact mechanical seal ring structure according to any one of claims 1-5, characterized in that: The extension path of the impact channel (4) is V-shaped. Both ends of the impact channel (4) are located on the outer circumferential surface of the corresponding sealing ring (1) or sealing ring (2). The angle between the axis of the opening at one end of the impact channel (4) and the radial center line is greater than the angle between the axis of the opening at the other end and the radial center line.

10. A mechanical seal device, comprising the radial deep-hole impact type mechanical seal ring structure as described in claim 9, characterized in that: It also includes a bushing (5) and a pressure cap (6). The bushing (5) is used to be fixedly connected to the rotating shaft so as to rotate with the shaft. The sealing moving ring (1) is installed on the bushing (5). The pressure cap (6) is used to connect with the equipment housing. The sealing stationary ring (2) is axially slidably connected to the pressure cap (6) through an elastic element. A sealing cavity (9) is formed between the pressure cap (6), the sealing moving ring (1) and the sealing stationary ring (2). A sealing medium inlet channel (7) and a sealing medium outlet channel (8) are provided on the pressure cap (6). The sealing medium inlet channel (7) and the sealing medium outlet channel (8) are both connected to the sealing cavity (9). The sealing medium inlet channel (7) is aligned with the sealing end face (3) of the sealing moving ring (1) and the sealing stationary ring (2) and is inclined. The angle between the axis of the sealing medium inlet channel (7) and the radial center line passing through the opening of the channel is equal to the angle between the axis of the water-facing end of the impact flow channel (4) and the radial center line passing through the opening of the flow channel.

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