CN112943932B - High-reliability zero-leakage steam turbine shaft end sealing method - Google Patents
High-reliability zero-leakage steam turbine shaft end sealing method Download PDFInfo
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- CN112943932B CN112943932B CN202110155809.1A CN202110155809A CN112943932B CN 112943932 B CN112943932 B CN 112943932B CN 202110155809 A CN202110155809 A CN 202110155809A CN 112943932 B CN112943932 B CN 112943932B
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- 238000007789 sealing Methods 0.000 title claims abstract description 105
- 238000000034 method Methods 0.000 title claims abstract description 17
- 230000003068 static effect Effects 0.000 claims abstract description 217
- 239000012530 fluid Substances 0.000 claims abstract description 83
- 230000001105 regulatory effect Effects 0.000 claims description 58
- 238000004891 communication Methods 0.000 claims description 21
- 230000000694 effects Effects 0.000 claims description 8
- 238000009434 installation Methods 0.000 description 8
- 230000002035 prolonged effect Effects 0.000 description 4
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 230000001960 triggered effect Effects 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 229910002804 graphite Inorganic materials 0.000 description 1
- 239000010439 graphite Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 description 1
- 229910010271 silicon carbide Inorganic materials 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3268—Mounting of sealing rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3284—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings characterised by their structure; Selection of materials
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Sealing (AREA)
Abstract
The invention provides a high-reliability zero-leakage steam turbine shaft end sealing method, which is used for sealing a gap between a casing and a rotating shaft of a steam turbine, wherein a high-pressure medium fluid cavity is arranged in the casing of the steam turbine, a low-pressure atmosphere side is arranged outside the casing of the steam turbine, a first-stage seal, a second-stage seal, a third-stage seal and a fourth-stage seal are sequentially arranged from the high-pressure medium fluid cavity to the low-pressure atmosphere side, the first-stage seal, the second-stage seal, the third-stage seal and the fourth-stage seal divide the high-pressure medium fluid cavity into a first-stage cavity, a second-stage cavity, a third-stage cavity and a fourth-stage cavity, the first-stage seal comprises a flexible static ring I and a movable ring I, the second-stage seal comprises a flexible static ring II and a movable ring II, the third-stage seal comprises a static ring III and a static ring IV, the flexible static ring IV is arranged at the outer end of each flexible static ring, the flexible static ring is internally provided with a pressure cavity, and the pressure cavity of the flexible static ring expands to enable the flexible ring to be in contact with the corresponding static ring through the friction part.
Description
Technical Field
The invention belongs to the technical field of mechanical sealing, and particularly relates to a high-reliability zero-leakage steam turbine shaft end sealing method.
Background
Relatively rotating sealed fluid devices such as steam turbines, centrifugal compressors include a rotor and a stator, typically a housing, with the rotor and housing rotating and stationary, with the housing containing a dielectric fluid, the rotating and stationary components requiring sealing to ensure fluid pressure within the cavity, and the shaft ends typically being sealed mechanically (mechanical end seals). The mechanical seal device comprises a moving ring and a stationary ring. The movable ring is fixedly arranged on the shaft sleeve or the shaft and rotates along with the shaft, the static ring is arranged on the static ring seat, the static ring seat is arranged on the equipment shell, and the static ring and the movable ring are tightly pressed by the spring so as to realize the sealing between the rotating part and the static part. Leakage of the rotating equipment media fluid often occurs at the end gap between the stationary and moving rings; in addition, seal failure will result from wear of the moving and stationary rings. In order to reduce the leakage of medium fluid at the shaft end of the rotating equipment, the shaft end sealing method of the steam turbine needs to be optimally designed.
Disclosure of Invention
The invention aims to solve the technical problems and provides a high-reliability zero-leakage steam turbine shaft end sealing method.
In order to achieve the above purpose, the invention adopts the following technical scheme:
a high-reliability zero-leakage steam turbine shaft end sealing method is used for sealing a gap between a casing and a rotating shaft of a steam turbine, a high-pressure medium fluid cavity is formed in the casing of the steam turbine, a low-pressure atmosphere side is arranged outside the casing of the steam turbine, a first-stage seal, a second-stage seal, a third-stage seal and a fourth-stage seal are sequentially arranged from the high-pressure medium fluid cavity to the low-pressure atmosphere side, the first-stage seal, the second-stage seal, the third-stage seal and the fourth-stage seal divide the high-pressure medium fluid cavity into a first-stage cavity, a second-stage cavity, a third-stage cavity and a fourth-stage cavity, the first-stage seal comprises a flexible static ring I and a dynamic ring I, the second-stage seal comprises a flexible static ring II and a dynamic ring II, the third-stage seal comprises a static ring III and a dynamic ring III, the fourth-stage seal comprises a static ring IV and a static ring IV, friction part is arranged at the outer end of each flexible static ring, the pressure cavity of each flexible static ring is internally provided with a pressure cavity, the flexible static ring is expanded to enable the flexible static ring to be in contact with the corresponding static ring, the friction part, the static ring is connected with the static ring I/the flexible static ring cavity, the flexible static ring I/the flexible ring is connected with the static ring I/the flexible ring cavity and the flexible ring II/the flexible ring cavity, the flexible ring cavity is connected with the static ring I/the static ring, the flexible ring cavity and the static ring; the high-pressure medium fluid in the first-stage cavity passes through the first pressure regulating cavity, the first pressure regulating cavity releases fluid pressure to enter the pressure cavity of the first flexible static ring, the pressure cavity of the first flexible static ring expands to enable the first flexible static ring to be pressed with the first movable ring to form a first-stage friction pair for sealing, the second-stage sealing of the second flexible static ring and the second movable ring is not started at first, when the pressure is generated by fluid leakage in the second-stage cavity, the leaked fluid passes through the second pressure regulating cavity, the second pressure regulating cavity releases fluid pressure to enter the pressure cavity of the second flexible static ring, the second flexible static ring is pressed with the second movable ring to form a second-stage friction pair for sealing, the third static ring and the third movable ring are pressed with each other through the pressure friction of the first spring to form a third-stage friction pair for sealing, and the fourth static ring and the fourth movable ring are pressed with each other through the pressure friction of the second spring to form a fourth-stage friction pair for sealing.
Preferably, the third stationary ring is provided with dynamic pressure grooves on the contact surface with the third movable ring and the fourth stationary ring is provided with dynamic pressure grooves on the contact surface with the fourth movable ring, the dynamic pressure grooves comprise a plurality of spiral dynamic pressure groove units uniformly distributed along the circumference, the spiral dynamic pressure groove units on the third stationary ring extend from the inner diameter edge of the three end surfaces of the stationary ring to the middle part of the three end surfaces of the stationary ring, and the spiral dynamic pressure groove units on the fourth stationary ring extend from the outer diameter edge of the four end surfaces of the stationary ring to the middle part of the four end surfaces of the stationary ring; a second pressure regulator with a third pressure regulating cavity and an air compressor connected with the second pressure regulator are arranged, the fourth-stage cavity is connected with the air compressor through the third pressure regulating cavity, the air compressor generates pressure gas, and the pressure gas is injected into the fourth-stage cavity; the static ring III and the moving ring III have relative rotation movement, the speed of the relative rotation movement is high, medium fluid is pumped into the dynamic pressure groove from the edge of the dynamic pressure groove of the static ring III, the medium fluid is extruded to form a high-pressure area in the dynamic pressure groove of the static ring III, namely a fluid dynamic pressure effect, the high-pressure area enables the static ring III and the moving ring III to push away from each other, and a micron-sized non-contact gap is formed between the static ring III and the moving ring III; the static ring IV and the moving ring IV have relative rotation movement, the speed of the relative rotation movement is high, pressure gas generated by the air compressor pumps into the dynamic pressure groove from the edge of the dynamic pressure groove of the static ring IV, the pressure gas is extruded to form a high-pressure area in the dynamic pressure groove of the static ring IV, namely a fluid dynamic pressure effect, the high-pressure area pushes the static ring IV and the moving ring IV away from each other, and a micron-sized non-contact gap is formed between the static ring IV and the moving ring IV.
Preferably, the first pressure regulator comprises: a spring III and a plunger I are arranged in the pressure regulating cavity I, the spring III is abutted against one end of the plunger I, so that the plunger I seals a communication port between the pressure regulating cavity I and the first-stage cavity, when the pressure reaches a certain degree, the plunger I is pushed away, the communication port releases the fluid pressure to enter a pressure cavity of the flexible static ring I, the flexible static ring I expands, and the flexible static ring I is compressed with the movable ring I; the pressure regulating cavity II is internally provided with a spring IV and a plunger II, the spring IV is abutted against one end of the plunger II, so that the plunger II seals a communication port between the pressure regulating cavity II and the second-stage cavity, when the pressure reaches a certain degree, the plunger II is pushed away, the communication port releases fluid pressure to enter a pressure cavity of the flexible static ring II, the flexible static ring II expands, and the flexible static ring II is tightly pressed with the movable ring II.
After the technical scheme is adopted, the invention has the following advantages:
the high pressure fluid passes through the medium fluid chamber at the periphery of the flexible static ring one to reach the first-stage seal of the flexible static ring one and the movable ring one. The first flexible static ring is a structure capable of injecting air and pressure into the internal pressure cavity, and the first flexible static ring and the first movable ring are pressed by injecting air and pressure into the pressure cavity of the first flexible static ring. The pressure of the first injection to the flexible stationary ring is the fluid medium pressure using the medium fluid chamber, i.e. in the present invention, regulated by the steam pressure in the turbine. Because the pressure of the fluid medium in the medium fluid chamber is relatively high, and the flexible static ring I does not need such high pressure, the pressure regulator I is designed to regulate the pressure of the fluid entering the flexible static ring I pressure chamber. The principle of the first pressure regulator is that the first plunger is used for sealing a communication port between the first pressure regulating cavity and the medium fluid cavity, when the pressure reaches a certain degree, the first plunger is pushed away, and the communication port releases the fluid pressure to enter the pressure cavity of the first flexible static ring, so that the first flexible static ring expands, and the first flexible static ring is compressed with the first movable ring.
The second-stage sealing of the second flexible static ring and the first flexible static ring is not started at first, and the second flexible static ring and the first flexible static ring are pressed tightly to form a friction pair for sealing only when the cavity between the second flexible static ring and the first flexible static ring is pressurized by fluid leakage. When the first-stage seal fails, fluid leaks into a cavity between the second flexible static ring and the first flexible static ring, the second plunger is pushed away, and the communication port releases fluid pressure to enter a pressure cavity of the second flexible static ring, so that the second flexible static ring expands, and the second flexible static ring is compressed with the second movable ring. On the one hand, the structure reduces friction torque generated by sealing so as to reduce power consumption, and on the other hand, when the first-stage sealing is damaged, the second-stage sealing automatically expands and seals, so that the overall reliability of the steam turbine is improved, and the service life of the sealing method is prolonged.
In order to further ensure the reliability of the sealing method, the sealing method also adopts two-stage dry sealing of a third stationary ring, a third movable ring, a fourth stationary ring and a fourth movable ring, is non-contact sealing, has no friction power consumption, and has infinitely long theoretical service life. After the second-stage seal fails, the two-stage dry seal can also play a certain role in guaranteeing. And designing an air supply system, and generating pressure air by an air compressor to inject pressure into the cavities at the peripheries of the moving ring III and the moving ring IV. The dry-sealed sealing medium requires a clean sealing gas to be dried, so the dryer is designed to dry the pressurized gas generated by the air compressor. The gas leaked from the stationary ring IV and the moving ring IV is leaked to the atmosphere side, so the sealing requirement is not high, and the spiral dynamic pressure groove units on the stationary ring IV are designed to extend from the outer diameter edge of the stationary ring IV to the middle part of the stationary ring IV. The gas leaked from the stationary ring III and the movable ring III is leaked to the medium fluid side, and the second-stage sealing can be triggered to be started, so that the spiral dynamic pressure groove unit on the stationary ring III is designed to extend from the inner diameter edge of the three end surfaces of the stationary ring to the middle part of the three end surfaces of the stationary ring, and the sealing gas leaked from the high pressure side to the inner side is reversely pumped back to the high pressure side.
In conclusion, the shaft end sealing method has the advantages of high reliability, low torque, low power loss and good sealing performance.
Drawings
FIG. 1 is a schematic structural view of a high reliability low torque zero leakage steam turbine shaft end seal arrangement;
FIG. 2 is a schematic structural view of the flexible stationary ring, with the flexible stationary ring in an unexpanded state;
FIG. 3 is a schematic view of the structure of the flexible stationary ring as it expands and contacts the moving ring;
FIG. 4 is a schematic structural view of a flexible static ring, when the flexible static ring is fully inflated without blocking;
FIG. 5 is a schematic end-face structure of a stationary ring III;
FIG. 6 is a schematic end-face structure of a stationary ring IV;
in the figure:
1-a rotating shaft; 2-a casing; 201-a first seal ring mounting groove; 202-a first sealing ring; 3-stationary ring seat; 301-a stationary ring-mounting groove; 302-a second stationary ring mounting groove; 303-a stationary ring three mounting groove; 4-end caps; 401-four mounting slots of stationary ring; 5-a first movable ring seat; 501-a second seal ring mounting groove; 502-a second sealing ring; 503-a first movable ring mounting groove; 504-a second moving ring mounting groove; 505-seal ring mounting groove three; 506-a third sealing ring; 507-sealing ring mounting groove four; 508-sealing ring IV; 6-a second movable ring seat; 601-a movable ring three-mounting groove; 602-a four-mounting groove of a movable ring; 603-a seal ring mounting groove five; 604-a seal ring five; 605-seal ring mounting groove six; 606-a sixth sealing ring; 7-flexible static ring I; 8-a flexible static ring II; 9-stationary ring III; 10-stationary ring IV; 11-a first ring; 12-a second moving ring; 13-a third moving ring; 14-moving ring IV; 15-an anti-rotation pin; 16-friction part; 17-a pressure chamber; 18-first pressure regulator; 1801-pressure regulating cavity I; 1802-pressure regulating cavity II; 19-spring III; 20-plunger one; 21-spring IV; 22-a second plunger; 23-an outer tire layer; 2301—a clamping portion; 24-an inner tire layer; 2401-a through hole; 25-mounting seats; 26-spring one; 27-spring two; 28-dynamic pressure grooves; 2801-a spiral dynamic pressure groove unit; 29-a second pressure regulator; 2901-pressure regulating cavity III; 30-an air compressor; 31-spring five; 32-a third plunger; 33-dryer.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples.
As shown in fig. 1-6, a high-reliability zero-leakage steam turbine shaft end sealing device comprises a shell and a rotating shaft 1. The shell comprises a shell 2, a stationary ring seat 3 and an end cover 4, and a movable ring seat I5 and a movable ring seat II 6 are fixedly arranged on the rotating shaft 1. A medium fluid cavity is arranged between the shell and the rotating shaft 1, and for a steam turbine, the medium fluid in the medium fluid cavity is steam.
In order to conveniently express the structural relation of all the components, the invention distinguishes the left and right of the shaft end sealing device.
The left end face of the static ring seat 3 is fixedly connected with the shell 2 through a screw, and the right end face of the static ring seat 3 is fixedly connected with the end cover 4 through a screw. The contact surface of the machine shell 2 and the stationary ring seat 3 is provided with a first sealing ring installation groove 201, and a first sealing ring 202 is arranged in the first sealing ring installation groove 201. The left side of the shaft end sealing device is the air sealing side, namely the high-pressure medium side, and the right side is the atmosphere side, namely the low-pressure side.
The left end face of the static ring seat 3 is provided with a static ring one mounting groove 301 and a static ring two mounting groove 302, a flexible static ring one 7 is arranged in the static ring one mounting groove 301, and a flexible static ring two 8 is arranged in the static ring two mounting groove 302. The diameter of the flexible static ring II 8 is smaller than that of the flexible static ring I7. The right end face of the stationary ring seat 3 is provided with a stationary ring three mounting groove 303, and a stationary ring three 9 is arranged in the stationary ring three mounting groove 303. The inner end face of the left side of the end cover 4 is provided with a four-stationary-ring mounting groove 401, and a four-stationary-ring 10 is arranged in the four-stationary-ring mounting groove 401.
The first moving ring seat 5 is arranged on the rotating shaft 1 through a set screw, and the first moving ring seat 5 is fixedly provided with a first moving ring 11 and a second moving ring 12. The first moving ring 11 corresponds to the first flexible static ring 7, and the second moving ring 12 corresponds to the second flexible static ring 8. The contact surface of the first movable ring seat 5 and the rotating shaft 1 is provided with a second sealing ring mounting groove 501, and a second sealing ring 502 is arranged in the second sealing ring mounting groove 501. The first moving ring seat 5 is provided with a first moving ring mounting groove 503 and a second moving ring mounting groove 504 for mounting the first moving ring 11 and the second moving ring 12. A third sealing ring mounting groove 505 is formed in the bottom surface of the first moving ring mounting groove 503, and a third sealing ring 506 is arranged in the third sealing ring mounting groove 505; a fourth sealing ring mounting groove 507 is formed in the bottom surface of the second moving ring mounting groove 504, and a fourth sealing ring 508 is arranged in the fourth sealing ring mounting groove 507.
And a third movable ring 13 is fixedly arranged on the left end surface of the second movable ring seat 6, and a fourth movable ring 14 is fixedly arranged on the right end surface of the second movable ring seat 6. The third moving ring 13 corresponds to the third stationary ring 9, and the fourth moving ring 14 corresponds to the fourth stationary ring 10. The second moving ring seat 6 is provided with a third moving ring mounting groove 601 and a fourth moving ring mounting groove 602 for mounting a third moving ring 13 and a fourth moving ring 14. A seal ring installation groove five 603 is formed in the bottom surface of the movable ring three installation groove 601, and a seal ring five 604 is arranged in the seal ring installation groove five 603; the bottom surface of the fourth installation groove 602 of the movable ring is provided with a sixth installation groove 605 of the sealing ring, and a sixth 606 of the sealing ring is arranged in the sixth installation groove 605 of the sealing ring.
The first moving ring mounting groove 503, the second moving ring mounting groove 504, the third moving ring mounting groove 601 and the fourth moving ring mounting groove 602 are respectively provided with an anti-rotation pin 15 for preventing the moving ring from rotating relatively.
The first flexible static ring 7 and the second flexible static ring 8 are respectively provided with a friction part 16 and a pressure cavity 17. The shaft end sealing device further comprises a first pressure regulator 18, and a first pressure regulating cavity 1801 and a second pressure regulating cavity 1802 are arranged in the first pressure regulator 18. The first pressure regulating cavity 1801 is communicated with a medium fluid cavity at the periphery of the first flexible static ring 7, and the first pressure regulating cavity 1801 is communicated with a pressure cavity 17 of the first flexible static ring 7. The pressure regulating chamber one 1801 is internally provided with a spring three 19 and a plunger one 20, and the spring three 19 is abutted against one end of the plunger one 20, so that the plunger one 20 seals a communication port between the pressure regulating chamber one 1801 and the peripheral medium fluid chamber of the flexible static ring one 7. The second pressure regulating cavity 1802 is communicated with a cavity between the second flexible static ring 8 and the first flexible static ring 7, and the second pressure regulating cavity 1802 is communicated with a pressure cavity 17 of the second flexible static ring 8. The second pressure regulating cavity 1802 is internally provided with a fourth spring 21 and a second plunger 22, and the fourth spring 21 is abutted against one end of the second plunger 22, so that the second plunger 22 seals a communication port of the second pressure regulating cavity 1802 and a cavity between the second flexible static ring 8 and the first flexible static ring 7.
The flexible static ring I7 and the flexible static ring II 8 comprise an outer tire layer 23 and an inner tire layer 24, the friction part 16 is fixedly arranged on the left side end surface of the outer tire layer 23, the inner tire layer 24 is arranged in the outer tire layer 23, and the inner cavity of the inner tire layer 24 is the pressure cavity 17. The friction portion 16 has a convex ring shape. The friction portion 16 is made of silicon carbide or graphite, and the outer tire layer 23 and the inner tire layer 24 are made of rubber. The inner tire layer 24 is provided with a plurality of through holes 2401 which are communicated with the cavity between the pressure cavity 17 and the outer tire layer 23 and the inner tire layer 24, and when the pressure cavity 17 is injected, gas enters the cavity between the outer tire layer 23 and the inner tire layer 24 through the through holes 2401. The two-layer structure of the outer tire layer 23 and the inner tire layer 24 plays a certain role in buffering, and the friction part 16 is prevented from being broken.
The flexible static ring I7 and the flexible static ring II 8 further comprise mounting seats 25, the outer tire layer 23 and the inner tire layer 24 are mounted in the mounting seats 25, the outer tire layer 23 comprises clamping portions 2301, and the outer tire layer 23 is clamped in the mounting seats 25 through the clamping portions 2301, so that the outer tire layer 23 and the inner tire layer 24 are prevented from falling off due to recoil force of air injection of the pressure cavity 17. The right end face of the inner tire layer 24 is fixedly connected to the right side face of the inner surface of the outer tire layer 23.
The friction surface of the friction part 16 is provided with a plurality of coaxially arranged friction rings 1601. The friction ring 1601 has a semicircular cross section. Contact wear swarf can enter the grooves between friction rings 1601, avoiding swarf from accelerating wear of the moving ring end face or flexible static ring friction portion 16. In addition, the friction rings 1601 form a multi-point seal with a large end face specific pressure and a good sealing effect.
The friction ring 1601 may be made to be highly non-uniform, i.e. peaks are not equally high. After the highest friction ring 1601 peak wears, the next highest friction ring 1601 peak is in contact with the moving ring. The service life of the flexible static ring is prolonged. The friction ring 1601 has a peak height difference of 0-100 microns.
The third static ring 9 and the fourth static ring 10 are rigid static rings. The spring I26 is arranged in the stationary ring III mounting groove 303, the spring II 27 is arranged in the stationary ring IV mounting groove 401, the stationary ring III 9 is connected with the stationary ring seat 3 through the spring I26, and the stationary ring IV 10 is connected with the end cover 4 through the spring II 27. Spring one 26 presses the stationary ring three 9 against the moving ring three 13, and spring two 27 presses the stationary ring four 10 against the moving ring four 14.
Dynamic pressure grooves 28 are formed in the contact surface of the third stationary ring 9 with the third movable ring 13 and the contact surface of the fourth stationary ring 10 with the fourth movable ring 14. The dynamic pressure groove 28 includes a plurality of spiral dynamic pressure groove units 2801 uniformly distributed along the circumference, and the depth of the spiral dynamic pressure groove units 2801 is in the order of micrometers. The two groups of stationary rings and the movable ring have relative rotation movement, the speed of the relative rotation movement is high, medium fluid is pumped into the movable groove 28 from the edge of the movable groove 28, the medium fluid is extruded to form a high-pressure area in the movable groove 28, namely a fluid dynamic pressure effect, the high-pressure area enables the stationary rings and the movable ring to be pushed away from each other, a micron-sized non-contact gap is formed between the stationary rings and the movable ring, the micron-sized non-contact gap can ensure good tightness between the stationary rings and the movable ring, in addition, no contact exists between the stationary rings and the movable ring, and the service life of the stationary rings and the movable ring can be prolonged.
The spiral dynamic pressure groove unit 2801 on the static ring three 9 extends from the inner diameter edge of the end surface of the static ring three 9 to the middle of the end surface of the static ring three 9, the high pressure side of the static ring three 9 is at the outer diameter side, the dynamic pressure groove 28 on the static ring three 9 can reversely pump the sealing gas leaking inwards from the high pressure side back to the high pressure side, and zero leakage or negative leakage of medium fluid can be realized.
The spiral dynamic pressure groove unit 2801 on the four stationary rings 10 extends from the outer diameter edge of the end face of the four stationary rings 10 to the middle of the end face of the four stationary rings 10, the high pressure side of the four stationary rings 10 is on the outer diameter side, and the dynamic pressure grooves 28 on the four stationary rings 10 are large in friction pressure and good in opening characteristic.
The shaft end sealing device further comprises a second pressure regulator 29, a third pressure regulating cavity 2901 is arranged in the second pressure regulator 29, the third pressure regulating cavity 2901 is communicated with the cavities on the peripheries of the third movable ring 13 and the fourth movable ring 14, the third pressure regulating cavity 2901 is further connected with an air compressor 30, a fifth spring 31 and a third plunger 32 are arranged in the third pressure regulating cavity 2901, the fifth spring 31 is abutted to one end of the third plunger 32, and the third plunger 32 is used for sealing a communication port of the third pressure regulating cavity 2901 and the air compressor 30. Compressed air output by the air compressor 30 is dried by the dryer 33 and then is introduced into the pressure regulating cavity III 2901.
The shaft end sealing device adopts a multistage series-parallel sealing structure.
Working principle: the left side of the sealing device is a gas sealing side and a high-pressure medium side, the right side is an atmosphere side and a low-pressure side, and high-pressure fluid reaches the first-stage sealing of the flexible static ring I7 and the movable ring I11 through a medium fluid cavity at the periphery of the flexible static ring I7.
The flexible static ring 7 is a structure capable of injecting air and pressure into the internal pressure cavity 17, and the air and pressure are injected into the pressure cavity 17 of the flexible static ring 7 so that the flexible static ring 7 and the movable ring 11 are compressed. The pressure injected into the flexible stator ring 7 is the fluid medium pressure using the medium fluid chamber, i.e. in the present invention, regulated by the steam pressure in the turbine. Since the pressure of the fluid medium in the medium fluid chamber is relatively high, and such a high pressure is not required in the flexible static ring 7, the pressure regulator 18 is designed to regulate the pressure of the fluid entering the pressure chamber 17 of the flexible static ring 7. The principle of the pressure regulator I18 is that a communication port between the pressure regulating cavity I1801 and a medium fluid cavity is blocked by the plunger I20, when the pressure reaches a certain degree, the plunger I20 is pushed away, and the communication port releases the fluid pressure to enter the pressure cavity 17 of the flexible static ring I7, so that the flexible static ring I7 expands, and the flexible static ring I7 is compressed with the movable ring I11.
The second-stage sealing of the flexible static ring II 8 and the movable ring II 12 is not started at first, and the flexible static ring II 8 and the movable ring II 12 are pressed tightly to form a friction pair for sealing only when the cavity between the flexible static ring II 8 and the flexible static ring I7 is pressurized by fluid leakage. When the first-stage seal fails, fluid leaks into a cavity between the flexible static ring II 8 and the flexible static ring I7, the plunger II 22 is pushed away, and the communication port releases fluid pressure to enter the pressure cavity 17 of the flexible static ring II 8, so that the flexible static ring II 8 expands, and the flexible static ring II 8 is compressed with the movable ring II 12. On the one hand, the structure reduces friction torque generated by sealing so as to reduce power consumption, and on the other hand, when the first-stage sealing is damaged, the second-stage sealing automatically expands and seals, so that the overall reliability of the steam turbine is improved, and the service life of the sealing device is prolonged.
In order to further guarantee the reliability of the sealing device, the sealing device also adopts two-stage dry sealing of a third stationary ring 9, a third movable ring 13, a fourth stationary ring 10 and a fourth movable ring 14, is non-contact sealing, has no friction power consumption, and has infinitely long theoretical service life. After the second-stage seal fails, the two-stage dry seal can also play a certain role in guaranteeing. The air supply system is designed, the air compressor 30 generates pressure air, and the pressure air is injected into the cavities at the peripheries of the third moving ring 13 and the fourth moving ring 14. The dry-sealed sealing medium requires a clean sealing gas to be dried, and thus the dryer 33 is designed to dry the pressurized gas generated by the air compressor 30. The gas leaked from the stationary ring four 10 and the movable ring four 14 is a sealing gas leaked to the atmosphere side, so that the sealing requirement is not high here, and the spiral dynamic pressure groove unit 2801 on the stationary ring four 10 is designed to extend from the outer diameter edge of the end face of the stationary ring four 10 to the middle of the end face of the stationary ring four 10. The gas leaked from the stationary ring three 9 and the movable ring three 13 is leaked to the medium fluid side, and the second-stage sealing can be triggered to be started, so that the spiral dynamic pressure groove unit 2801 on the stationary ring three 9 is designed to extend from the inner diameter edge of the end surface of the stationary ring three 9 to the middle part of the end surface of the stationary ring three 9, and the sealing gas leaked inwards from the high pressure side is reversely pumped back to the high pressure side.
Based on the shaft end sealing device, the invention provides a high-reliability zero-leakage steam turbine shaft end sealing method.
A high-reliability zero-leakage steam turbine shaft end sealing method is used for sealing a gap between a casing and a rotating shaft 1 of a steam turbine, a high-pressure medium fluid cavity is arranged in the casing of the steam turbine, a low-pressure atmosphere side is arranged outside the casing of the steam turbine, a first-stage seal, a second-stage seal, a third-stage seal and a fourth-stage seal are sequentially arranged from the high-pressure medium fluid cavity to the low-pressure atmosphere side, the first-stage seal, the second-stage seal, the third-stage seal and the fourth-stage seal divide the high-pressure medium fluid cavity into a first-stage cavity, a second-stage cavity, a third-stage cavity and a fourth-stage cavity, the first-stage seal comprises a flexible static ring I7 and a dynamic ring I11, the second-stage seal comprises a flexible static ring II 8 and a dynamic ring II 12, the third-stage seal comprises a static ring III 9 and a dynamic ring III 13, the fourth-stage seal comprises a fourth static ring 10 and a fourth dynamic ring 14, friction parts 16 are arranged at the outer ends of the flexible static rings, pressure cavities 17 are arranged in the flexible static rings, the pressure cavities 17 of the flexible static rings expand to enable the flexible static rings to be in contact sealing with corresponding dynamic rings through the friction parts 16, a spring I26 used for pressing the third static ring 9/the third dynamic ring 13 to the third dynamic ring 13/the third static ring 9 is connected with the third static ring 9/the third dynamic ring 13, a spring II 27 used for pressing the fourth static ring 10/the fourth dynamic ring 14 to the fourth dynamic ring 14/the fourth static ring 10 is connected with the fourth static ring 10/the fourth static ring, a pressure regulator I18 with a pressure regulating cavity I1801 and a pressure regulating cavity II 1802 is arranged, the pressure cavities 17 of the first flexible static ring 7 are connected with the first-stage cavity through the pressure regulating cavity I1801, and the pressure cavities of the second-stage flexible static ring 8 are connected with the second-stage cavity through the pressure regulating cavity II 1802; the high-pressure medium fluid in the first-stage cavity passes through a first pressure regulating cavity 1801, the first pressure regulating cavity 1801 releases fluid pressure to enter a pressure cavity of a first flexible static ring 7, the pressure cavity of the first flexible static ring 7 expands, the first flexible static ring 7 is tightly pressed with a first movable ring 11 to form a first-stage friction pair for sealing, the second-stage sealing of a second flexible static ring 8 and a second movable ring 12 is not started at first, when only the second-stage cavity has fluid leakage to generate pressure, the leaked fluid passes through a second pressure regulating cavity 1802, the second pressure regulating cavity 1802 releases fluid pressure to enter the pressure cavity of a second flexible static ring 8, the second flexible static ring 8 is tightly pressed with the second movable ring 12 to form a second-stage friction pair for sealing, a third-stage friction pair for sealing is formed by the pressure friction contact of a third spring 26, and a fourth-stage friction pair for sealing is formed by the pressure friction contact of a fourth spring 27 and a fourth spring 14.
Dynamic pressure grooves 28 are formed in the contact surface of the static ring III 9 and the dynamic pressure groove 13 and the contact surface of the static ring IV 10 and the dynamic pressure groove 14, the dynamic pressure grooves comprise a plurality of spiral dynamic pressure groove units 2801 which are uniformly distributed along the circumference, the spiral dynamic pressure groove units 2801 on the static ring III 9 extend from the inner diameter edge of the end surface of the static ring III 9 to the middle part of the end surface of the static ring III 9, and the spiral dynamic pressure groove units 2801 on the static ring IV 10 extend from the outer diameter edge of the end surface of the static ring IV 10 to the middle part of the end surface of the static ring IV 10; a second pressure regulator 29 with a third pressure regulating cavity 2901 and an air compressor 30 connected with the second pressure regulator 2902 are arranged, a fourth-stage cavity is connected with the air compressor 30 through the third pressure regulating cavity 2901, the air compressor 30 generates pressure gas, and injection pressure is carried out on the fourth-stage cavity; there is a relative rotational movement between the stationary ring three 9 and the movable ring three 13, and the speed of the relative rotational movement is very high, medium fluid is pumped into the dynamic pressure groove 28 from the edge of the dynamic pressure groove 28 of the stationary ring three 9, the medium fluid is extruded to form a high pressure area in the dynamic pressure groove 28 of the stationary ring three 9, namely, a hydrodynamic pressure effect, the high pressure area pushes the stationary ring three 9 and the movable ring three 13 away from each other, and a micron-sized non-contact gap is formed between the stationary ring three 9 and the movable ring three 13; there is a relative rotational movement between the stationary ring IV 10 and the movable ring IV 14, and the speed of the relative rotational movement is high, the pressure gas generated by the air compressor 30 is pumped into the dynamic pressure groove 2801 from the edge of the dynamic pressure groove 28 of the stationary ring IV 10, the pressure gas is extruded to form a high pressure area in the dynamic pressure groove 28 of the stationary ring IV 10, namely, a hydrodynamic pressure effect, the high pressure area pushes the stationary ring IV 10 and the movable ring IV 14 away from each other, and a micron-sized non-contact gap is formed between the stationary ring IV 10 and the movable ring IV 14.
The pressure regulating method of the first pressure regulator 18 is as follows: a third spring 19 and a first plunger 20 are arranged in the first pressure regulating cavity 1801, the third spring 19 is abutted against one end of the first plunger 20, so that the first plunger 20 seals a communication port between the first pressure regulating cavity 1801 and the first-stage cavity, when the pressure reaches a certain degree, the first plunger 20 is pushed away, the communication port releases the fluid pressure to enter a pressure cavity 17 of the first flexible static ring 7, the first flexible static ring 7 expands, and the first flexible static ring 7 is compressed with the first movable ring 11; and a spring IV 21 and a plunger II 22 are arranged in the pressure regulating cavity II 1802, the spring IV 21 is abutted against one end of the plunger II 22, so that the plunger II 22 seals a communication port between the pressure regulating cavity II 1802 and the second-stage cavity, when the pressure reaches a certain degree, the plunger II 22 is pushed away, the communication port releases the fluid pressure to enter the pressure cavity 17 of the flexible static ring II 8, the flexible static ring II 8 expands, and the flexible static ring II 8 and the movable ring II 12 are compressed.
In addition to the above preferred embodiments, the present invention has other embodiments, and various changes and modifications may be made by those skilled in the art without departing from the spirit of the invention, which is defined in the appended claims.
Claims (3)
1. The shaft end sealing method of the high-reliability zero-leakage steam turbine is used for sealing a gap between a casing and a rotating shaft of the steam turbine, a high-pressure medium fluid cavity is formed in the casing of the steam turbine, and a low-pressure atmosphere side is arranged outside the casing of the steam turbine, and is characterized in that a first-stage seal, a second-stage seal, a third-stage seal and a fourth-stage seal are sequentially arranged from the high-pressure medium fluid cavity to the low-pressure atmosphere side, the first-stage seal, the second-stage seal, the third-stage seal and the fourth-stage seal divide the high-pressure medium fluid cavity into a first-stage cavity, a second-stage cavity, a third-stage cavity and a fourth-stage cavity, the first-stage seal comprises a flexible static ring I and a dynamic ring II, the third-stage seal comprises a static ring III and a dynamic ring III, the fourth-stage seal comprises a static ring IV and a static ring IV, friction part is arranged at the outer end of each flexible static ring, the pressure cavity of each flexible static ring is internally provided with a pressure cavity, the flexible static ring is expanded to enable the flexible static ring to be connected with the corresponding contact static ring through the friction part, the static ring III-seal is connected with the first-stage cavity, the flexible static ring is connected with the flexible static ring cavity through the flexible static ring I and the flexible static ring cavity, the flexible static ring cavity is connected with the flexible static ring cavity I and the flexible static ring cavity, the flexible ring cavity is connected with the flexible static ring cavity I and the flexible ring cavity, the flexible ring cavity is connected with the flexible static ring cavity and the flexible ring cavity;
the high-pressure medium fluid in the first-stage cavity passes through the first pressure regulating cavity, the first pressure regulating cavity releases fluid pressure to enter the pressure cavity of the first flexible static ring, the pressure cavity of the first flexible static ring expands to enable the first flexible static ring to be pressed with the first movable ring to form a first-stage friction pair for sealing, the second-stage sealing of the second flexible static ring and the second movable ring is not started at first, when the pressure is generated by fluid leakage in the second-stage cavity, the leaked fluid passes through the second pressure regulating cavity, the second pressure regulating cavity releases fluid pressure to enter the pressure cavity of the second flexible static ring, the second flexible static ring is pressed with the second movable ring to form a second-stage friction pair for sealing, the third static ring and the third movable ring are pressed with each other through the pressure friction of the first spring to form a third-stage friction pair for sealing, and the fourth static ring and the fourth movable ring are pressed with each other through the pressure friction of the second spring to form a fourth-stage friction pair for sealing.
2. The high-reliability zero-leakage steam turbine shaft end sealing method according to claim 1, wherein a third stationary ring is provided with dynamic pressure grooves on a contact surface with the third stationary ring and a fourth stationary ring is provided with dynamic pressure grooves on a contact surface with the fourth stationary ring, the dynamic pressure grooves comprise a plurality of spiral dynamic pressure groove units uniformly distributed along the circumference, the spiral dynamic pressure groove units on the third stationary ring extend from the inner diameter edge of the third stationary ring end surface to the middle part of the third stationary ring end surface, and the spiral dynamic pressure groove units on the fourth stationary ring extend from the outer diameter edge of the fourth stationary ring end surface to the middle part of the fourth stationary ring end surface; a second pressure regulator with a third pressure regulating cavity and an air compressor connected with the second pressure regulator are arranged, the fourth-stage cavity is connected with the air compressor through the third pressure regulating cavity, the air compressor generates pressure gas, and the pressure gas is injected into the fourth-stage cavity;
the static ring III and the moving ring III have relative rotation movement, the speed of the relative rotation movement is high, medium fluid is pumped into the dynamic pressure groove from the edge of the dynamic pressure groove of the static ring III, the medium fluid is extruded to form a high-pressure area in the dynamic pressure groove of the static ring III, namely a fluid dynamic pressure effect, the high-pressure area enables the static ring III and the moving ring III to push away from each other, and a micron-sized non-contact gap is formed between the static ring III and the moving ring III; the static ring IV and the moving ring IV have relative rotation movement, the speed of the relative rotation movement is high, pressure gas generated by the air compressor pumps into the dynamic pressure groove from the edge of the dynamic pressure groove of the static ring IV, the pressure gas is extruded to form a high-pressure area in the dynamic pressure groove of the static ring IV, namely a fluid dynamic pressure effect, the high-pressure area pushes the static ring IV and the moving ring IV away from each other, and a micron-sized non-contact gap is formed between the static ring IV and the moving ring IV.
3. The high-reliability zero-leakage steam turbine shaft end sealing method according to claim 1, wherein the first pressure regulator comprises the following steps: a spring III and a plunger I are arranged in the pressure regulating cavity I, the spring III is abutted against one end of the plunger I, so that the plunger I seals a communication port between the pressure regulating cavity I and the first-stage cavity, when the pressure reaches a certain degree, the plunger I is pushed away, the communication port releases the fluid pressure to enter a pressure cavity of the flexible static ring I, the flexible static ring I expands, and the flexible static ring I is compressed with the movable ring I; the pressure regulating cavity II is internally provided with a spring IV and a plunger II, the spring IV is abutted against one end of the plunger II, so that the plunger II seals a communication port between the pressure regulating cavity II and the second-stage cavity, when the pressure reaches a certain degree, the plunger II is pushed away, the communication port releases fluid pressure to enter a pressure cavity of the flexible static ring II, the flexible static ring II expands, and the flexible static ring II is tightly pressed with the movable ring II.
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| CN112303239A (en) * | 2020-10-28 | 2021-02-02 | 中国计量大学 | Novel active dynamic pressure type air film end face sealing device and intelligent control method thereof |
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| US10100932B2 (en) * | 2014-09-29 | 2018-10-16 | New Way Machine Components, Inc. | Thrust bearing as a seal |
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| EP0021243A1 (en) * | 1979-06-22 | 1981-01-07 | Howaldtswerke-Deutsche Werft Ag | Sealing arrangement for stern tubes of ships |
| US4613141A (en) * | 1984-12-22 | 1986-09-23 | M.A.N. Maschinenfabrik Augsburg-Nurnberg Ag | Hydrostatic and hydrodynamic seal for rotating a rotating shaft |
| CN201306445Y (en) * | 2008-10-16 | 2009-09-09 | 东营海森密封技术有限责任公司 | Liquid film lubrication double end surface non-contact mechanical seal device |
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