Turbine end dynamic sealing device
By adding a fluid dynamic pressure spiral groove and a positioning structure to the sealing end face of the turbine end dynamic seal device, the problem of loose sealing is solved, and a higher sealing effect and longer service life are achieved.
Patent Information
- Application Number
- CN202423187937.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-23
- Publication Date
- 2025-10-14
- Estimated Expiration
- 2034-12-23
AI Technical Summary
The existing mechanical seal device cannot effectively seal for a long time at the starter turbine end, especially in the oil mist and instantaneous oil flow environment, resulting in serious leakage, and severe friction and wear of the sealing end surface.
A circle of fluid dynamic pressure spiral grooves is added to the sealing end face, combined with a wave spring and a positioning structure to form a fluid dynamic pressure effect to improve sealing ability, reduce friction and wear, and ensure the precise positioning of the sealing ring through the positioning block.
It improves the bearing capacity of the seal, reduces leakage, extends the service life, and reduces the friction and temperature of the seal end face.
Smart Images
Figure CN223434399U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of mechanical seals, in particular to a turbine end dynamic sealing device. Background Art
[0002] The starter turbine-end dynamic seal is installed on the starter's power-end turbine shaft and is used for turbine-end sealing. The lubricating oil medium is 4106 or 4050 synthetic aviation lubricant for aircraft turbine engines, and the ambient medium is air. The starter has two stable speed operating conditions: one is the overrunning condition, and the other is the cold running condition. Both conditions operate continuously from 0 rpm to the specified rpm. Under normal operating conditions, the maximum pressure difference is 0.03 MPa, and under abnormal conditions, the extreme pressure difference is 0.13 MPa. The operating ambient temperature is from -40°C to 150°C, and the gas medium temperature is from -54°C to 250°C. Under extreme operating conditions, oil mist will form on the sliding oil side, and the dynamic seal device may also be submerged in the instantaneous oil flow. Currently, conventional mechanical seals are unable to effectively seal for a long time when in use. Utility Model Content
[0003] The technical problem to be solved by the utility model is to provide a turbine end dynamic sealing device which adopts the method of adding a circle of fluid dynamic pressure spiral grooves on the sealing end face of the dynamic ring, thereby improving the bearing capacity of the seal, reducing the friction and wear of the sealing end face, and lowering the temperature of the sealing end face.
[0004] The technical solution of the present utility model is to provide a turbine end dynamic sealing device with the following structure, including a sealing dynamic ring and a spring seat, a sealing static ring, and a wave spring that are sleeved on the outside of the shaft. One end of the spring seat is provided with an annular groove. The sealing static ring is located in the annular groove of the spring seat and its end extends out of the annular groove. A cavity is provided between the inner end surface of the sealing static ring and the inner bottom surface of the spring seat. The wave spring is located in the cavity and abuts between the inner end of the sealing static ring and the inner end surface of the sealing static ring. The wave spring pushes the outer end sealing surface of the sealing static ring to tightly fit with the outer end sealing surface of the sealing dynamic ring to achieve dynamic sealing. The outer end sealing surface of the sealing dynamic ring is provided with a circle of fluid dynamic pressure spiral grooves arranged along the circumferential direction.
[0005] A portion of each fluid dynamic pressure spiral groove is in close contact with the outer end sealing surface of the sealing static ring.
[0006] The inner end surface of the sealing static ring is provided with a push ring, which is sleeved outside the inner side surface of the annular groove and moves axially with the sealing static ring.
[0007] The inner end of the sealing static ring is provided with a stepped inner hole and a sealing ring is provided at this position for sealing between the inner wall of the sealing static ring and the inner side wall of the annular groove.
[0008] A clamping ring is provided on the inner side of the port of the annular groove of the spring seat. There is a distance between the clamping ring and the sealing static ring in both axial and radial directions, and the inner diameter of the clamping ring is smaller than the outer diameter of the sealing static ring.
[0009] The outer side wall of the spring seat and the annular groove is provided with at least one set of circumferentially symmetrical positioning blocks, and the outer wall of the sealing static ring is provided with at least one set of circumferentially symmetrical positioning grooves, each positioning block is embedded in a corresponding positioning groove for circumferential positioning.
[0010] There is a spacing between adjacent fluid dynamic pressure spiral grooves and they are arranged along the circumference of the sealing dynamic ring.
[0011] After adopting the above structure, the utility model has the following advantages:
[0012] 1. A hydrodynamic spiral groove is added to the sealing end face of the dynamic ring. The relative rotation generates a hydrodynamic effect, forming an extremely thin liquid film between the sealing end faces. This liquid film has both hydrodynamic and static pressure, providing lubrication and pressure balance, while preventing media leakage. This improves the seal's load-bearing capacity, reduces friction and wear on the sealing end face, and lowers the temperature of the sealing end face. This reduces leakage and extends service life.
[0013] 2. The outer wall of the spring seat and the annular groove is provided with at least one set of circumferentially symmetrical positioning blocks, and the outer wall of the static seal ring is provided with at least one set of circumferentially symmetrical positioning grooves. Each positioning block is embedded in a corresponding positioning groove for circumferential positioning. In addition, during processing and measurement, the distance between the two opposite positioning grooves can be directly measured, which well ensures the processing size of the sealing ring and makes the force on the end face of the mechanical seal more uniform. BRIEF DESCRIPTION OF THE DRAWINGS
[0014] Figure 1 It is a cross-sectional schematic diagram of the turbine end dynamic sealing device of the present invention.
[0015] Figure 2 It is a schematic diagram of the spring seat of the present utility model.
[0016] Figure 3 for Figure 2 AA cross-sectional diagram of .
[0017] Figure 4 It is a schematic diagram of the sealing static ring of the present utility model.
[0018] Figure 5 for Figure 4 BB cross-section diagram.
[0019] Figure 6 It is a cross-sectional schematic diagram of the sealing dynamic ring of the present utility model.
[0020] Figure 7 It is a schematic diagram of the sealing dynamic ring of the present utility model.
[0021] Shown in the figure: 1. Shaft, 2. Sealing dynamic ring, 3. Spring seat, 4. Sealing static ring, 5. Wave spring, 6. Annular groove, 7. Cavity, 8. Fluid dynamic pressure spiral groove, 9. Push ring, 10. Sealing ring, 11. Retaining ring, 12. Positioning block, 13. Positioning groove. DETAILED DESCRIPTION
[0022] The present invention will be further described below with reference to the accompanying drawings.
[0023] like Figure 1-7 As shown, a turbine end dynamic seal device of the present invention includes a sealing dynamic ring 2 and a spring seat 3, a sealing static ring 4, and a wave spring 5 that are sleeved on the outside of the shaft 1. One end of the spring seat 3 is provided with an annular groove 6. The sealing static ring 4 is located in the annular groove 4 of the spring seat 3 and its end protrudes from the annular groove 6. The opening of the sealing dynamic ring 2 faces the sealing dynamic ring 2, and the end surface of the sealing static ring 4 that protrudes from the annular groove 6 is in contact with the sealing dynamic ring 2 for sealing.
[0024] A cavity 7 is provided between the inner end face of the sealing static ring 4 and the inner bottom face of the spring seat 3. The cavity 7 is annular in structure. The wave spring 5 is located in the cavity 7 and abuts against the inner end of the sealing static ring 4 and the inner end face of the sealing static ring 4. The wave spring pushes the outer end sealing surface of the sealing static ring 4 to closely adhere to the outer end sealing surface of the sealing dynamic ring 2 to form a dynamic seal. The outer end sealing surface of the sealing dynamic ring 2 is provided with a circle of fluid dynamic pressure spiral grooves 8 arranged along the circumferential direction.
[0025] like Figure 1 and Figure 7 As shown, a portion of each fluid dynamic pressure spiral groove 8 is in close contact with the outer end sealing surface of the sealing static ring 4, and there is a gap between adjacent fluid dynamic pressure spiral grooves 8 and they are arranged along the circumference of the sealing dynamic ring 2, with a circle forming an outward-swinging structure.
[0026] The inner end surface of the static seal ring 4 is provided with a push ring 9, which is sleeved outside the inner side surface of the annular groove 4 and moves axially with the static seal ring 4. The push ring 9 is a gasket structure, which is clamped on the end of the static seal ring 4, making the thrust applied by the wave spring 5 on the static seal ring 4 more balanced and preventing tilting.
[0027] The inner end of the sealing static ring 4 is provided with a stepped inner hole and a sealing ring 10 is provided at this position for sealing between the inner wall of the sealing static ring 4 and the inner side wall of the annular groove 6. The sealing ring 10 is an O-ring.
[0028] A clamping ring 11 is provided on the inner side of the port of the annular groove 6 of the spring seat 3. The clamping ring 11 is spaced apart from the sealing static ring 4 in both axial and radial directions, and the inner diameter of the clamping ring 11 is smaller than the outer diameter of the sealing static ring 4. The clamping ring 11 serves as an axial limit for the sealing static ring 4 to prevent the sealing static ring 4 from falling off.
[0029] like Figure 2 and Figure 3 As shown, the outer walls of the spring seat 3 and annular groove 6 are provided with at least one set of circumferentially symmetrical positioning blocks 12. The outer wall of the static seal ring 4 is provided with at least one set of circumferentially symmetrical positioning grooves 13. Each positioning block 12 is embedded in a corresponding positioning groove 13 for circumferential positioning. In this embodiment, there are four positioning blocks 12 and four positioning grooves 13, each corresponding to the other.
Claims
1. A turbine end dynamic sealing device, characterized in that: The invention comprises a sealing dynamic ring (2) and a spring seat (3), a sealing static ring (4), and a wave spring (5) sleeved on the outside of the shaft (1), wherein one end of the spring seat (3) is provided with an annular groove (6), the sealing static ring (4) is located in the annular groove (6) of the spring seat (3) and the end thereof extends out of the annular groove (6), a cavity (7) is provided between the inner end surface of the sealing static ring (4) and the inner bottom surface of the spring seat (3), the wave spring (5) is located in the cavity (7) and abuts between the inner end of the sealing static ring (4) and the inner end surface of the sealing static ring (4), the wave spring pushes the outer end sealing surface of the sealing static ring (4) to be in close contact with the outer end sealing surface of the sealing dynamic ring (2) to form a dynamic seal, and the outer end sealing surface of the sealing dynamic ring (2) is provided with a circle of fluid dynamic pressure spiral grooves (8) arranged along the circumferential direction.
2. A turbine end dynamic sealing device according to claim 1, characterized in that: A portion of each fluid dynamic pressure spiral groove (8) is in close contact with the outer end sealing surface of the sealing static ring (4).
3. The turbine end dynamic sealing device according to claim 1, characterized in that: The inner end surface of the sealing static ring (4) is provided with a push ring (9), and the push ring (9) is sleeved on the outside of the inner side surface of the annular groove (6) and moves axially with the sealing static ring (4).
4. The turbine end dynamic seal device according to claim 1, characterized in that: The inner end of the sealing static ring (4) is provided with a stepped inner hole, and a sealing ring (10) is provided at the position of the stepped inner hole, which is used to seal between the inner wall of the sealing static ring (4) and the inner side wall of the annular groove (6).
5. The turbine end dynamic sealing device according to claim 1, characterized in that: A clamping ring (11) is provided on the inner side of the port of the annular groove (6) of the spring seat (3), and a spacing is provided between the clamping ring (11) and the sealing static ring (4) in both the axial and radial directions, and the inner diameter of the clamping ring (11) is smaller than the outer diameter of the sealing static ring (4).
6. The turbine end dynamic sealing device according to claim 1, characterized in that: The outer side walls of the spring seat (3) and the annular groove (6) are provided with at least one set of circumferentially symmetrical positioning blocks (12), and the outer side wall of the sealing static ring (4) is provided with at least one set of circumferentially symmetrical positioning grooves (13), each positioning block (12) is embedded in a corresponding positioning groove (13) for circumferential positioning.
7. The turbine end dynamic seal device according to claim 1, characterized in that: Adjacent fluid dynamic pressure spiral grooves (8) are spaced apart and arranged along the circumference of the sealing dynamic ring (2).