CN112943932A - 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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- CN112943932A CN112943932A CN202110155809.1A CN202110155809A CN112943932A CN 112943932 A CN112943932 A CN 112943932A CN 202110155809 A CN202110155809 A CN 202110155809A CN 112943932 A CN112943932 A CN 112943932A
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- 238000007789 sealing Methods 0.000 title claims abstract description 116
- 238000000034 method Methods 0.000 title claims abstract description 20
- 230000003068 static effect Effects 0.000 claims abstract description 221
- 239000012530 fluid Substances 0.000 claims abstract description 79
- 230000001105 regulatory effect Effects 0.000 claims description 66
- 238000004891 communication Methods 0.000 claims description 19
- 230000000694 effects Effects 0.000 claims description 7
- 238000003825 pressing Methods 0.000 claims description 7
- 230000004913 activation Effects 0.000 description 2
- 239000000428 dust Substances 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000007770 graphite material Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material 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
- 230000001737 promoting 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
- 230000001960 triggered effect Effects 0.000 description 1
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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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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention provides a high-reliability zero-leakage steam turbine shaft end sealing method, which is used for sealing a gap between a shell and a rotating shaft of a steam turbine, wherein a high-pressure medium fluid cavity is arranged in the shell of the steam turbine, a low-pressure atmosphere side is arranged outside the shell 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 first flexible static ring and a first moving ring, the second-stage seal comprises a second flexible static ring and a second moving ring, the third-stage seal comprises a third static ring and a third moving ring, the fourth-stage seal comprises a, the pressure cavity of the flexible static ring is expanded to enable the flexible static ring to be in contact sealing with the corresponding movable 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
A sealing fluid device rotating relatively, such as a steam turbine and a centrifugal compressor, includes a rotor and a stator, the stator is generally a housing, the rotor and the housing rotate and are stationary, a medium fluid is provided in the housing, the rotating and stationary components need to be sealed to ensure the fluid pressure in the cavity, and a common sealing mode for the shaft ends is a mechanical seal (mechanical end face seal). The mechanical sealing device comprises a movable ring and a static ring. The rotating 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 rotating ring are compressed through a spring so as to realize the sealing between the rotating part and the static part. Leakage of rotating equipment medium fluid often occurs at the end face gap between the static ring and the dynamic ring; in addition, wear on the rotating and stationary rings can cause seal failure. In order to reduce the medium fluid leakage 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 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 shell and a rotating shaft of a steam turbine, a high-pressure medium fluid cavity is arranged in the steam turbine shell, a low-pressure atmosphere side is arranged outside the steam turbine shell, 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 first flexible static ring and a first movable ring, the second-stage seal comprises a second flexible static ring and a second movable ring, the third-stage seal comprises a third static ring and a third movable ring, the fourth-stage seal comprises a fourth static ring and a fourth movable ring, each flexible static, the pressure cavity of the flexible static ring is expanded to enable the flexible static ring to be in contact sealing with a corresponding movable ring through the friction part, the static ring III/the movable ring III is connected with a spring I used for pressing the static ring III/the movable ring III to the movable ring III/the static ring III, the static ring IV/the movable ring IV is connected with a spring II used for pressing the static ring IV/the movable ring IV to the movable ring IV/the static ring IV, a pressure regulator I with a pressure regulating cavity I and a pressure regulating cavity II is arranged, the pressure cavity of the flexible static ring I is connected with the first-stage cavity through the pressure regulating cavity I, and the pressure cavity of the flexible static ring II is connected with the second-stage cavity through the pressure regulating cavity II; 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, and the pressure cavity of the first flexible static ring expands, the first flexible static ring and the first movable ring are pressed 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, and only when fluid leaks from the second-stage cavity to generate pressure, the pressure chamber that the fluid of leakage was through pressure regulating chamber two, pressure regulating chamber two release fluid pressure got into flexible quiet ring two, and flexible quiet ring two just compresses tightly with rotating ring two and forms one and be used for sealed second grade friction pair, and quiet ring three and rotating ring three form one through the pressure friction contact of spring one and be used for sealed third grade friction pair, and quiet ring four and rotating ring four form one through the pressure friction contact of spring two and be used for sealed fourth grade friction pair.
Preferably, the third stationary ring and the fourth stationary ring are provided with dynamic pressure grooves on the contact surface with the third moving ring and the contact surface with the fourth moving ring, each dynamic pressure groove comprises 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 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 of the fourth stationary ring end surface; a pressure regulator II with a pressure regulating cavity III and an air compressor connected with the pressure regulator are arranged, a fourth-stage cavity is connected with the air compressor through the pressure regulating cavity III, and the air compressor generates pressure gas and injects pressure into the fourth-stage cavity; relative rotation motion exists between the third static ring and the third dynamic ring, the speed of the relative rotation motion is high, medium fluid is pumped into the dynamic pressure groove from the edge of the dynamic pressure groove of the third static ring, the medium fluid is squeezed, so that a high pressure area, namely a hydrodynamic pressure effect, is formed in the dynamic pressure groove of the third static ring, the high pressure area enables the third static ring and the third dynamic ring to be mutually pushed away, and a micron-sized non-contact gap is formed between the third static ring and the third dynamic ring; and the static ring IV and the dynamic ring IV have relative rotation movement, the speed of the relative rotation movement is very high, pressure gas generated by the air compressor is pumped into the dynamic pressure groove from the edge of the dynamic pressure groove of the static ring IV, the pressure gas is extruded, so that a high pressure area, namely a hydrodynamic pressure effect, is formed in the dynamic pressure groove of the static ring IV, and the high pressure area enables the static ring IV and the dynamic ring IV to be mutually pushed away, so that a micron-scale non-contact gap is formed between the static ring IV and the dynamic ring IV.
Preferably, the first pressure regulator has a pressure regulating method comprising: a third spring and a first plunger are arranged in the first pressure regulating cavity, the third spring abuts against one end of the first plunger, so that the first plunger seals a communication port of the first pressure regulating cavity and the first-stage cavity, when the pressure reaches a certain degree, the first plunger is pushed open, the communication port releases fluid pressure to enter a pressure cavity of the first flexible static ring, the first flexible static ring expands, and the first flexible static ring and the first movable ring are tightly pressed; and a fourth spring and a second plunger are arranged in the pressure regulating cavity II, the fourth spring is abutted against one end of the second plunger, so that the second plunger seals a communication port of the pressure regulating cavity II and the second-stage cavity, when the pressure reaches a certain degree, the second plunger is pushed open, the communication port releases fluid pressure to enter a pressure cavity of the second flexible static ring, the second flexible static ring expands, and the second flexible static ring is tightly pressed with the second movable ring.
After the technical scheme is adopted, the invention has the following advantages:
high-pressure fluid reaches the first-stage seal of the first flexible static ring and the first movable ring through the medium fluid cavity on the periphery of the first flexible static ring. The flexible static ring is a structure capable of injecting gas and pressure into the pressure cavity of the inner part, and the flexible static ring and the movable ring are compressed by injecting gas and pressure into the pressure cavity of the flexible static ring. The pressure of the fluid medium in the medium fluid cavity is used for feeding the flexible static ring, namely the pressure is adjusted by the steam pressure in the steam turbine. Since the fluid medium pressure of the medium fluid chamber is relatively high and such a high pressure is not required in the flexible stationary ring, a pressure regulator is designed to regulate the fluid pressure entering the flexible stationary ring and the pressure chamber. The principle of the first pressure regulator is that a first plunger piston is used for plugging a communicating port of a first pressure regulating cavity and a medium fluid cavity, when the pressure reaches a certain degree, the first plunger piston is pushed open, the communicating port releases fluid pressure to enter a pressure cavity of a first flexible static ring, so that the first flexible static ring expands, and the first flexible static ring and a first movable ring are pressed tightly.
The second-stage sealing of the second flexible static ring and the second flexible static ring is not started, and only when fluid leaks from a cavity between the second flexible static ring and the first flexible static ring to generate pressure, the second flexible static ring and the second flexible static ring are compressed to form a friction pair for sealing. When the first-stage seal fails, fluid leaks to a cavity between the second flexible static ring and the first flexible static ring, the second plunger is pushed open, the communication port releases fluid pressure to enter a pressure cavity of the second flexible static ring, the second flexible static ring expands, and the second flexible static ring and the second movable ring are compressed. The structure reduces the friction torque generated by sealing so as to reduce power consumption, and when the first-stage sealing is damaged, the second-stage sealing is automatically expanded and sealed so as to improve the overall reliability of the steam turbine and prolong the service life of the sealing method.
In order to further guarantee the reliability of the sealing method, the sealing method also adopts two-stage dry sealing of a third static ring and a third dynamic ring, and a fourth static ring and a fourth dynamic ring, and the sealing method is non-contact sealing, has no friction power consumption and has infinite theoretical life. After the second-stage sealing fails, the two-stage dry sealing can also play a certain guarantee. And designing an air supply system, wherein an air compressor generates pressure gas, and the pressure gas is injected into the cavities at the peripheries of the third movable ring and the fourth movable ring. The dry sealing medium needs dry and clean sealing gas, so the drier is designed to dry the pressure gas generated by the air compressor. The gas leaked by the static ring four and the dynamic ring four is the sealing gas leaked to the atmosphere side, so the sealing requirement is not high, and the spiral dynamic pressure groove unit on the static ring four is designed to extend from the outer diameter edge of the static ring four end faces to the middle part of the static ring four end faces. And the gas leaked by the third static ring and the third dynamic ring is the sealing gas leaked to the medium side, and the activation of the second-stage seal can be triggered, so that the spiral dynamic pressure groove unit on the third static ring is designed to extend from the inner diameter edge of the three end faces of the static ring to the middle part of the three end faces of the static ring, and the sealing gas leaked inwards from the high pressure 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 diagram of a shaft end sealing device of a high-reliability low-torque zero-leakage steam turbine;
FIG. 2 is a schematic view of the flexible stationary ring in an unexpanded state;
FIG. 3 is a schematic view of the flexible stationary ring, as it expands and contacts the moving ring;
FIG. 4 is a schematic view of the flexible stationary ring, as it is fully expanded when unobstructed;
FIG. 5 is a schematic end view of a third stationary ring;
FIG. 6 is a schematic end view of a fourth stationary ring;
in the figure:
1-a rotating shaft; 2-a housing; 201-a first sealing ring mounting groove; 202-sealing ring one; 3-stationary ring seat; 301-a stationary ring mounting groove; 302-a second stationary ring mounting groove; 303-three mounting grooves of a stationary ring; 4-end cover; 401-four mounting grooves of stationary ring; 5-moving ring seat I; 501-a second sealing ring mounting groove; 502-seal ring two; 503-a mounting groove of the movable ring; 504-a second mounting groove of the movable ring; 505-sealing ring mounting groove III; 506-sealing ring III; 507-a sealing ring mounting groove IV; 508-seal ring four; 6-moving ring seat II; 601-three mounting grooves of the movable ring; 602-moving ring four mounting groove; 603-a sealing ring mounting groove five; 604-seal ring five; 605-a sealing ring mounting groove six; 606-sealing ring six; 7-flexible static ring I; 8-flexible stationary ring II; 9-stationary ring III; 10-stationary ring four; 11-moving ring one; 12-moving ring two; 13-rotating ring III; 14-moving ring four; 15-anti-rotation pins; 16-a friction portion; 17-a pressure chamber; 18-a pressure regulator one; 1801-pressure regulating Chamber one; 1802-pressure regulating cavity two; 19-spring three; 20-plunger one; 21-spring four; 22-plunger two; 23-a carcass ply; 2301-a clamping part; 24-an inner tyre layer; 2401-a through hole; 25-a mounting seat; 26-spring one; 27-spring two; 28-dynamic pressure groove; 2801-a helical dynamic pressure groove unit; 29-pressure regulator two; 2901-pressure regulating chamber III; 30-an air compressor; 31-spring five; 32-plunger III; 33-dryer.
Detailed Description
The present invention will be described in further detail with reference to the following drawings and specific 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 machine shell 2, a static ring seat 3 and an end cover 4, wherein a first moving ring seat 5 and a second moving ring seat 6 are fixedly arranged on the rotating shaft 1. A medium fluid cavity is formed between the outer shell and the rotating shaft 1, and for a steam turbine, medium fluid in the medium fluid cavity is steam.
In order to conveniently express the structural relationship of each part, the invention distinguishes the left side and the right side of the shaft end sealing device.
The left end face of the static ring seat 3 is fixedly connected with the casing 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. And a first sealing ring mounting groove 201 is formed in the contact surface of the machine shell 2 and the stationary ring seat 3, and a first sealing ring 202 is arranged in the first sealing ring mounting groove 201. The left side of the shaft end sealing device is a gas sealing side, namely a high-pressure medium side, and the right side of the shaft end sealing device is an atmosphere side, namely a low-pressure side.
Be equipped with quiet ring mounting groove 301 and two mounting grooves 302 of quiet ring on the left side terminal surface of quiet ring seat 3, be equipped with flexible quiet ring one 7 in the quiet ring mounting groove 301, be equipped with flexible quiet ring two 8 in the quiet ring two mounting grooves 302. The diameter of the second flexible static ring 8 is smaller than that of the first flexible static ring 7. And a stationary ring three mounting groove 303 is formed in the end face of the right side of the stationary ring seat 3, and a stationary ring three 9 is arranged in the stationary ring three mounting groove 303. And a fixed ring four mounting groove 401 is formed in the inner end face of the left side of the end cover 4, and a fixed ring four 10 is arranged in the fixed ring four mounting groove 401.
The first movable ring seat 5 is installed on the rotating shaft 1 through a set screw, and a first movable ring 11 and a second movable ring 12 are fixedly installed on the first movable ring seat 5. The first movable ring 11 corresponds to the first flexible stationary ring 7, and the second movable ring 12 corresponds to the second flexible stationary ring 8. And a second sealing ring mounting groove 501 is arranged on the contact surface of the first moving ring seat 5 and the rotating shaft 1, and a second sealing ring 502 is arranged in the second sealing ring mounting groove 501. The first movable ring seat 5 is provided with a first movable ring mounting groove 503 and a second movable ring mounting groove 504 for mounting the first movable ring 11 and the second movable 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; and 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.
A third movable ring 13 is fixedly installed on the left end face of the second movable ring seat 6, and a fourth movable ring 14 is fixedly installed on the right end face 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. And a third moving ring mounting groove 601 and a fourth moving ring mounting groove 602 are formed in the second moving ring seat 6 to mount a third moving ring 13 and a fourth moving ring 14. A fifth sealing ring mounting groove 603 is formed in the bottom surface of the third moving ring mounting groove 601, and a fifth sealing ring 604 is arranged in the fifth sealing ring mounting groove 603; and a sealing ring mounting groove six 605 is arranged on the bottom surface of the moving ring four mounting groove 602, and a sealing ring six 606 is arranged in the sealing ring mounting groove six 605.
And the first rotating ring mounting groove 503, the second rotating ring mounting groove 504, the third rotating ring mounting groove 601 and the fourth rotating ring mounting groove 602 are all internally provided with an anti-rotating pin 15 for preventing the rotating rings from rotating relatively.
The first flexible static ring 7 and the second flexible static ring 8 are both 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 formed 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. A spring III 19 and a plunger III 20 are arranged in the pressure regulating cavity I1801, the spring III 19 abuts against one end of the plunger III 20, and therefore the plunger III 20 seals a communication port of the pressure regulating cavity I1801 and a medium fluid cavity at the periphery of the flexible static ring I7. The pressure regulating cavity II 1802 is communicated with the cavity between the flexible static ring II 8 and the flexible static ring I7, and the pressure regulating cavity II 1802 is communicated with the pressure cavity 17 of the flexible static ring II 8. A spring four 21 and a plunger two 22 are arranged in the pressure regulating cavity two 1802, and the spring four 21 abuts against one end of the plunger two 22, so that the plunger two 22 blocks a communication port of a cavity between the pressure regulating cavity two 1802 and the flexible static ring two 8 and the flexible static ring one 7.
The first flexible static ring 7 and the second flexible static ring 8 comprise an outer tire layer 23 and an inner tire layer 24, the friction part 16 is fixedly arranged on the left end face 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 is formed in a convex ring shape. The friction part 16 is made of silicon carbide and graphite materials, and the outer tire layer 23 and the inner tire layer 24 are made of rubber materials. The inner tire layer 24 is provided with a plurality of through holes 2401 for communicating the pressure cavity 17 with the cavity between the outer tire layer 23 and the inner tire layer 24, and when pressure is injected into the pressure cavity 17, gas enters the cavity between the outer tire layer 23 and the inner tire layer 24 through the through holes 2401. The two-layer inner 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 crushed.
The first flexible stationary ring 7 and the second flexible stationary ring 8 further comprise a mounting seat 25, the outer tire layer 23 and the inner tire layer 24 are mounted in the mounting seat 25, the outer tire layer 23 comprises a clamping portion 2301, the outer tire layer 23 is clamped in the mounting seat 25 through the clamping portion 2301, and the outer tire layer 23 and the inner tire layer 24 are prevented from falling off due to recoil force of gas injection of the pressure cavity 17. The right side 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.
A plurality of coaxially arranged friction rings 1601 are arranged on the friction surface of the friction part 16. The friction ring 1601 has a semicircular cross section. The abrasive dust from contact wear can enter the grooves between the friction rings 1601 to avoid the abrasive dust accelerating the wear of the dynamic ring end surface or the flexible static ring friction part 16. In addition, a plurality of friction rings 1601 form the multiple spot sealed, and the terminal surface is than pressing, and is sealed effectual.
The friction ring 1601 may be made to be of a non-uniform height, i.e., not as high as the peaks. After the highest wave peak of the friction ring 1601 is worn, the next highest wave peak of the friction ring 1601 is in contact with the moving ring. The service life of the flexible static ring is prolonged. The difference in the height of the peaks of the friction ring 1601 is 0-100 microns.
The third static ring 9 and the fourth static ring 10 are rigid static rings. Be equipped with spring one 26 in the three mounting grooves of quiet ring 303, be equipped with spring two 27 in the four mounting grooves of quiet ring 401, quiet ring three 9 with quiet ring seat 3 passes through spring one 26 to be connected, quiet ring four 10 with end cover 4 passes through spring two 27 to be connected. A first spring 26 presses the stationary ring three 9 towards the moving ring three 13, and a second spring 27 presses the stationary ring four 10 towards the moving ring four 14.
The static ring three 9 is provided with a dynamic pressure groove 28 on the contact surface with the dynamic ring three 13, and the static ring four 10 is provided with a dynamic pressure groove 28 on the contact surface with the dynamic ring four 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. Relative rotation motion exists between the two groups of static rings and the moving rings, the speed of the relative rotation motion is high, a medium fluid is pumped into the dynamic pressure groove 28 from the edge of the dynamic pressure groove 28, the medium fluid is extruded to form a high-pressure area in the dynamic pressure groove 28, namely, a fluid dynamic pressure effect, the high-pressure area enables the static rings and the moving rings to be mutually pushed away, a micron-sized non-contact gap is formed between the static rings and the moving rings, the micron-sized non-contact gap can guarantee good sealing performance between the static rings and the moving rings, in addition, no contact exists between the static rings and the moving rings, no abrasion exists, and the service lives of the static rings and the moving rings can be prolonged.
The spiral dynamic pressure groove unit 2801 on the third stationary ring 9 extends from the inner diameter edge of the end face of the third stationary ring 9 to the middle of the end face of the third stationary ring 9, the high pressure side of the third stationary ring 9 is on the outer diameter side, and the dynamic pressure groove 28 on the third stationary ring 9 can pump the sealing gas leaked from the high pressure side to the high pressure side in a reverse manner, so that zero leakage or negative leakage of the medium fluid can be realized.
The spiral dynamic pressure groove unit 2801 on the fourth stationary ring 10 extends from the outer diameter edge of the end face of the fourth stationary ring 10 to the middle of the end face of the fourth stationary ring 10, the high pressure side of the fourth stationary ring 10 is on the outer diameter side, and the dynamic pressure groove 28 on the fourth stationary ring 10 has high friction and good opening characteristics.
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 peripheral cavities 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 abuts against one end of the third plunger 32, and therefore the third plunger 32 blocks a communication port of the third pressure regulating cavity 2901 and the air compressor 30. The compressed air output by the air compressor 30 is dried by the dryer 33 and then enters the third pressure regulating chamber 2901.
The shaft end sealing device adopts a multistage series-parallel connection sealing structure.
The working principle is as follows: the left side of the sealing device is a gas sealing side and a high-pressure medium side, the right side of the sealing device is an atmosphere side and a low-pressure side, and high-pressure fluid reaches the first-stage seal of the first flexible static ring 7 and the first movable ring 11 through the medium fluid cavity on the periphery of the first flexible static ring 7.
The first flexible static ring 7 is a structure capable of injecting air and pressure into the pressure cavity 17 inside, and the air and pressure injection into the pressure cavity 17 of the first flexible static ring 7 causes the first flexible static ring 7 and the first movable ring 11 to be pressed tightly. The pressure of the fluid to be injected into the first flexible static ring 7 is adjusted by utilizing the pressure of the fluid medium of the medium fluid cavity, namely the steam pressure in the steam turbine. Since the fluid medium pressure in the medium fluid chamber is high and such a high pressure is not required in the flexible stationary ring one 7, the pressure regulator one 18 is designed to regulate the fluid pressure entering the pressure chamber 17 of the flexible stationary ring one 7. The principle of the first pressure regulator 18 is that the first plunger 20 seals a communication port of the first pressure regulating cavity 1801 and the medium fluid cavity, when the pressure reaches a certain degree, the first plunger 20 is pushed open, the communication port releases fluid pressure to enter the pressure cavity 17 of the first flexible static ring 7, the first flexible static ring 7 is expanded, and the first flexible static ring 7 is tightly pressed with the first movable ring 11.
The second-stage sealing of the second flexible static ring 8 and the second flexible static ring 12 is not started, and only when fluid leaks from a cavity between the second flexible static ring 8 and the first flexible static ring 7 to generate pressure, the second flexible static ring 8 and the second flexible static ring 12 are pressed to form a friction pair for sealing. When the first-stage sealing fails, fluid leaks to a cavity between the second flexible static ring 8 and the first flexible static ring 7, the second plunger 22 is pushed away, the communication port releases fluid pressure to enter the pressure cavity 17 of the second flexible static ring 8, the second flexible static ring 8 expands, and the second flexible static ring 8 and the second movable ring 12 are pressed tightly. Above-mentioned structure reduces the friction torque that sealed production on the one hand to reduce the consumption, on the other hand when the sealed emergence of first order damages, the sealed automatic expansion of second level is sealed, makes the steam turbine overall reliability obtain improving, and sealing device's life also can obtain promoting.
In order to further guarantee the reliability of the sealing device, the sealing device also adopts two-stage dry sealing of a third static ring 9 and a third dynamic ring 13, and a fourth static ring 10 and a fourth dynamic ring 14, and the sealing device is non-contact sealing, has no friction power consumption and has infinite theoretical life. After the second-stage sealing fails, the two-stage dry sealing can also play a certain guarantee. And an air supply system is designed, and the air compressor 30 generates pressure air to inject pressure into the cavities at the peripheries of the third movable ring 13 and the fourth movable ring 14. Since the dry-sealed sealing medium requires a dry and clean sealing gas, the dryer 33 is designed to dry the pressure gas generated by the air compressor 30. The gas leaked from the static ring four 10 and the dynamic ring four 14 is the sealing gas leaked to the atmosphere side, so the sealing requirement is not high here, and the spiral dynamic pressure groove unit 2801 on the static ring four 10 is designed to extend from the outer diameter edge of the end face of the static ring four 10 to the middle of the end face of the static ring four 10. And the gas leaked from the static ring three 9 and the dynamic ring three 13 is the sealing gas leaked to the medium fluid side, which may trigger the activation of the second stage of sealing, so the spiral dynamic pressure groove unit 2801 on the static ring three 9 is designed to extend from the inner diameter edge of the end surface of the static ring three 9 to the middle part of the end surface of the static ring three 9, and the sealing gas leaked from the high pressure side to the inside is 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 shell of a steam turbine and a rotating shaft 1, a high-pressure medium fluid cavity is arranged in the steam turbine shell, a low-pressure atmosphere side is arranged outside the steam turbine shell, 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 static ring IV 10 and a dynamic, each flexible static ring is internally provided with a pressure cavity 17, the pressure cavity 17 of each flexible static ring is expanded to enable the flexible static ring to be in contact sealing with the corresponding dynamic ring through the friction part 16, the static ring three 9/dynamic ring three 13 is connected with a first spring 26 for pressing the static ring three 9/dynamic ring three 13 to the dynamic ring three 13/static ring three 9, the static ring four 10/dynamic ring four 14 is connected with a second spring 27 for pressing the static ring four 10/dynamic ring four 14 to the dynamic ring four 14/static ring four 10, a first pressure regulator 18 with a first pressure regulating cavity 1801 and a second pressure regulating cavity 1802 is arranged, the pressure cavity 17 of the first flexible static ring 7 is connected with the first stage cavity through the first pressure regulating cavity 1801, and the pressure cavity of the second flexible static ring 8 is connected with the second stage cavity through the second pressure regulating cavity 1802; high-pressure medium fluid in the first-stage cavity passes through the first pressure regulating cavity 1801, the first pressure regulating cavity 1801 releases the fluid pressure to enter the pressure cavity of the first flexible static ring 7, the pressure cavity of the first flexible static ring 7 expands, the first flexible static ring 7 and the first movable ring 11 are pressed to form a first-stage friction pair for sealing, the second-stage sealing of the second flexible static ring 8 and the second movable ring 12 is not started, and only when the pressure is generated due to fluid leakage in the second-stage cavity, the leaked fluid passes through the pressure regulating cavity II 1802, the pressure regulating cavity II 1802 releases the fluid pressure to enter a pressure cavity of the flexible static ring II 8, the flexible static ring II 8 is tightly pressed with the dynamic ring II 12 to form a second-stage friction pair for sealing, the static ring III 9 and the dynamic ring III 13 form a third-stage friction pair for sealing through the pressure friction contact of the spring I26, and the static ring IV 10 and the dynamic ring IV 14 form a fourth-stage friction pair for sealing through the pressure friction contact of the spring II 27.
The static ring III 9 is provided with dynamic pressure grooves 28 on the contact surface with the dynamic ring III 13 and the static ring IV 10 is provided with dynamic pressure grooves 28 on the contact surface with the dynamic ring IV 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, the fourth-stage cavity is connected with the air compressor 30 through the third pressure regulating cavity 2901, and the air compressor 30 generates pressure gas to inject pressure into the fourth-stage cavity; relative rotation motion exists between the static ring III 9 and the dynamic ring III 13, the speed of the relative rotation motion is high, medium fluid is pumped into the dynamic pressure groove 28 from the edge of the dynamic pressure groove 28 of the static ring III 9, the medium fluid is squeezed, so that a high pressure area, namely a hydrodynamic pressure effect, is formed in the dynamic pressure groove 28 of the static ring III 9, the high pressure area enables the static ring III 9 and the dynamic ring III 13 to be mutually pushed away, and a micron-scale non-contact gap is formed between the static ring III 9 and the dynamic ring III 13; relative rotation motion exists between the static ring IV 10 and the dynamic ring IV 14, the speed of the relative rotation motion is high, 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 static ring IV 10, the pressure gas is squeezed, so that a high pressure area, namely a hydrodynamic pressure effect, is formed in the dynamic pressure groove 28 of the static ring IV 10, and the high pressure area enables the static ring IV 10 and the dynamic ring IV 14 to be mutually pushed away, so that a non-contact gap in a micron order is formed between the static ring IV 10 and the dynamic ring IV 14.
The pressure regulating method of the first pressure regulator 18 is as follows: a spring III 19 and a plunger I20 are arranged in the pressure regulating cavity I1801, the spring III 19 abuts against one end of the plunger I20, so that the plunger I20 blocks a communication port between the pressure regulating cavity I1801 and the first-stage cavity, when the pressure reaches a certain degree, the plunger I20 is pushed open, the communication port releases fluid pressure to enter a pressure cavity 17 of the flexible static ring I7, the flexible static ring I7 is expanded, and the flexible static ring I7 is tightly pressed with the movable ring I11; and a spring IV 21 and a plunger II 22 are arranged in the pressure regulating cavity II 1802, the spring IV 21 abuts 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 open, the communication port releases fluid pressure to enter a pressure cavity 17 of the flexible static ring II 8, the flexible static ring II 8 is expanded, and the flexible static ring II 8 is tightly pressed with the movable ring II 12.
Other embodiments of the present invention than the preferred embodiments described above will be apparent to those skilled in the art from the present invention, and various changes and modifications can be made therein without departing from the spirit of the present invention as defined in the appended claims.
Claims (3)
1. A high-reliability zero-leakage steam turbine shaft end sealing method is used for sealing a gap between a shell and a rotating shaft of a steam turbine, a high-pressure medium fluid cavity is arranged in the steam turbine shell, and a low-pressure atmosphere side is arranged outside the steam turbine shell, 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 and 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 first flexible static ring and a first moving ring, the second-stage seal comprises a second flexible static ring and a second moving ring, the third-stage seal comprises a third static ring and a third moving ring, the fourth-stage seal comprises a fourth static ring and a fourth moving ring, and each flexible static ring is provided with a friction part at the outer end, each flexible static ring is internally provided with a pressure cavity, the pressure cavity of each flexible static ring expands to enable the flexible static ring to be in contact sealing with a corresponding dynamic ring through the friction part, a static ring III/dynamic ring III is connected with a spring I for pressing the static ring III/dynamic ring III to a dynamic ring III/static ring III, a static ring IV/dynamic ring IV is connected with a spring II for pressing the static ring IV/dynamic ring IV to a dynamic ring IV/static ring IV, a pressure regulator I with a pressure regulating cavity I and a pressure regulating cavity II is arranged, the pressure cavity of the flexible static ring I is connected with the first-stage cavity through the pressure regulating cavity I, and the pressure cavity of the flexible static ring II is connected with the second-stage cavity through the pressure regulating cavity II;
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, and the pressure cavity of the first flexible static ring expands, the first flexible static ring and the first movable ring are pressed 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, and only when fluid leaks from the second-stage cavity to generate pressure, the pressure chamber that the fluid of leakage was through pressure regulating chamber two, pressure regulating chamber two release fluid pressure got into flexible quiet ring two, and flexible quiet ring two just compresses tightly with rotating ring two and forms one and be used for sealed second grade friction pair, and quiet ring three and rotating ring three form one through the pressure friction contact of spring one and be used for sealed third grade friction pair, and quiet ring four and rotating ring four form one through the pressure friction contact of spring two and be used for sealed fourth grade friction pair.
2. The high-reliability zero-leakage steam turbine shaft end sealing method of claim 1, wherein the third stationary ring is provided with dynamic pressure grooves on the contact surface with the third moving ring and the fourth stationary ring is provided with dynamic pressure grooves on the contact surface with the fourth moving ring, the dynamic pressure grooves comprise a plurality of spiral dynamic pressure groove units which are 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 third stationary ring to the middle of the three end surfaces of the third 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 fourth stationary ring to the middle of the four end surfaces of the fourth stationary ring; a pressure regulator II with a pressure regulating cavity III and an air compressor connected with the pressure regulator are arranged, a fourth-stage cavity is connected with the air compressor through the pressure regulating cavity III, and the air compressor generates pressure gas and injects pressure into the fourth-stage cavity;
relative rotation motion exists between the third static ring and the third dynamic ring, the speed of the relative rotation motion is high, medium fluid is pumped into the dynamic pressure groove from the edge of the dynamic pressure groove of the third static ring, the medium fluid is squeezed, so that a high pressure area, namely a hydrodynamic pressure effect, is formed in the dynamic pressure groove of the third static ring, the high pressure area enables the third static ring and the third dynamic ring to be mutually pushed away, and a micron-sized non-contact gap is formed between the third static ring and the third dynamic ring; and the static ring IV and the dynamic ring IV have relative rotation movement, the speed of the relative rotation movement is very high, pressure gas generated by the air compressor is pumped into the dynamic pressure groove from the edge of the dynamic pressure groove of the static ring IV, the pressure gas is extruded, so that a high pressure area, namely a hydrodynamic pressure effect, is formed in the dynamic pressure groove of the static ring IV, and the high pressure area enables the static ring IV and the dynamic ring IV to be mutually pushed away, so that a micron-scale non-contact gap is formed between the static ring IV and the dynamic ring IV.
3. The high-reliability zero-leakage steam turbine shaft end sealing method as claimed in claim 1, wherein the pressure regulating method of the first pressure regulator is as follows: a third spring and a first plunger are arranged in the first pressure regulating cavity, the third spring abuts against one end of the first plunger, so that the first plunger seals a communication port of the first pressure regulating cavity and the first-stage cavity, when the pressure reaches a certain degree, the first plunger is pushed open, the communication port releases fluid pressure to enter a pressure cavity of the first flexible static ring, the first flexible static ring expands, and the first flexible static ring and the first movable ring are tightly pressed; and a fourth spring and a second plunger are arranged in the pressure regulating cavity II, the fourth spring is abutted against one end of the second plunger, so that the second plunger seals a communication port of the pressure regulating cavity II and the second-stage cavity, when the pressure reaches a certain degree, the second plunger is pushed open, the communication port releases fluid pressure to enter a pressure cavity of the second flexible static ring, the second flexible static ring expands, and the second flexible static ring is tightly pressed with the second movable ring.
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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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| 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 |
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| CN112943932B (en) | 2024-01-19 |
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