CN112096873A - Floating sealing device for mechanical seal of hydrodynamic main pump of nuclear power station - Google Patents
Floating sealing device for mechanical seal of hydrodynamic main pump of nuclear power station Download PDFInfo
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- CN112096873A CN112096873A CN202010757083.4A CN202010757083A CN112096873A CN 112096873 A CN112096873 A CN 112096873A CN 202010757083 A CN202010757083 A CN 202010757083A CN 112096873 A CN112096873 A CN 112096873A
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- main pump
- mechanical seal
- guide sleeve
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- 238000007789 sealing Methods 0.000 title claims abstract description 13
- 230000003068 static effect Effects 0.000 claims description 37
- 239000011248 coating agent Substances 0.000 claims description 29
- 238000000576 coating method Methods 0.000 claims description 29
- 239000000463 material Substances 0.000 claims description 12
- 238000005299 abrasion Methods 0.000 claims description 8
- 229920002943 EPDM rubber Polymers 0.000 claims description 6
- 230000006835 compression Effects 0.000 claims description 6
- 238000007906 compression Methods 0.000 claims description 6
- -1 polytetrafluoroethylene Polymers 0.000 claims description 5
- 229920001343 polytetrafluoroethylene Polymers 0.000 claims description 5
- 239000004810 polytetrafluoroethylene Substances 0.000 claims description 5
- UFGZSIPAQKLCGR-UHFFFAOYSA-N chromium carbide Chemical compound [Cr]#C[Cr]C#[Cr] UFGZSIPAQKLCGR-UHFFFAOYSA-N 0.000 claims description 4
- 229910003470 tongbaite Inorganic materials 0.000 claims description 4
- 230000005489 elastic deformation Effects 0.000 claims description 3
- 238000012423 maintenance Methods 0.000 abstract description 3
- 238000005516 engineering process Methods 0.000 abstract 1
- 238000013461 design Methods 0.000 description 15
- 238000012360 testing method Methods 0.000 description 11
- 238000000034 method Methods 0.000 description 8
- 230000000052 comparative effect Effects 0.000 description 3
- 238000001125 extrusion Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000003746 surface roughness Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 229920000181 Ethylene propylene rubber Polymers 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 229920001577 copolymer Polymers 0.000 description 1
- 150000001993 dienes Chemical class 0.000 description 1
- 230000003203 everyday effect Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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- 239000002245 particle Substances 0.000 description 1
- 238000011056 performance test Methods 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 230000000379 polymerizing effect Effects 0.000 description 1
- 229920001296 polysiloxane Polymers 0.000 description 1
- 229930195734 saturated hydrocarbon Natural products 0.000 description 1
- BFKJFAAPBSQJPD-UHFFFAOYSA-N tetrafluoroethene Chemical group FC(F)=C(F)F BFKJFAAPBSQJPD-UHFFFAOYSA-N 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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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
- F16J15/3464—Mounting of the seal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/106—Shaft sealings especially adapted for liquid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/10—Shaft sealings
- F04D29/12—Shaft sealings using sealing-rings
- F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
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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
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
- F16J15/102—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing characterised by material
-
- 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
-
- 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
- F16J15/3496—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member use of special materials
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Sealing (AREA)
Abstract
The disclosure belongs to the technical field of nuclear power maintenance, and particularly relates to a floating sealing device for a mechanical seal of a hydrodynamic pressure type main pump of a nuclear power station. In the embodiment of the disclosure, because the size of the O-shaped ring stationary guide and the outer diameter of the stationary ring guide sleeve can be better matched, the friction resistance between the stationary ring guide sleeve and the stationary ring seat is greatly reduced compared with the related technology, so that the follow-up performance of the stationary ring is obviously improved, the O-shaped ring can still be kept in an original state after being used for a long time, the low-pressure leakage amount of the mechanical seal is effectively reduced, and the problem of high leakage amount is improved. The sealing structure of the hydrodynamic pressure type main pump mechanical equipment of the nuclear power station can solve the problem that a certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, has strong practicability and popularization value, and also has great significance for guaranteeing the safety of the nuclear power station.
Description
Technical Field
The invention belongs to the technical field of nuclear power maintenance, and particularly relates to a floating sealing device for a mechanical seal of a hydrodynamic pressure type main pump of a nuclear power station.
Background
Generally, a main coolant pump (called a main pump for short) of a nuclear power plant reactor is a key sensitive device of the nuclear power plant and is a heart of the nuclear power plant. Since the mechanical seal of the hydraulic pressure-actuated main pump of the nuclear power station is self-debugged, the time is as short as 5 years, and the events that the low-pressure leakage flow of the mechanical seal of the main pump is high and the pressure before the three-stage seal is reduced to 0 occur for nearly 20 times. The shutdown and shutdown maintenance or overhaul mainline delay of the nuclear power plant is caused, and the nuclear safety and the economic benefit of the nuclear power plant are seriously influenced, so that the leakage of the mechanical seal of the main pump is avoided, the safe and stable operation of the main pump is ensured, and the problem to be solved urgently is solved.
Disclosure of Invention
In order to overcome the problems in the related art, the floating sealing device for the mechanical seal of the hydrodynamic pressure type main pump of the nuclear power station is provided.
According to an aspect of the embodiments of the present disclosure, there is provided a floating seal device of a mechanical seal of a hydrodynamic main pump of a nuclear power plant, including: the fixed ring seat and the fixed ring guide sleeve are annular, the upper end of the fixed ring guide sleeve is provided with a step part which extends outwards along the radial direction, the edge of the fixed ring seat is provided with a boss which extends upwards along the axial direction, the lower surface of the step part is elastically connected with the upper surface of the boss, the outer side of the lower end of the fixed ring guide sleeve is opposite to the inner side wall of the boss, and the inner side wall of the boss is provided with a circumferential groove;
the check ring is sleeved on the outer side of the lower end of the stationary ring guide sleeve, a fixing groove is formed in the outer side of the check ring along the circumferential direction, the O-shaped ring is sleeved in the fixing groove in the outer side of the check ring, the check ring and the O-shaped ring are located in the groove, the groove extrudes the check ring to enable the check ring to generate elastic deformation, the O-shaped ring is further extruded between the fixing groove and the groove, and the check ring and the O-shaped ring are used for sealing a gap between the outer side of the lower end of the stationary ring guide sleeve and the inner side wall of the boss;
the outer diameter of the lower end of the static ring guide sleeve is 286.5 mm, the inner diameter of the retainer ring is 285 mm to 286 mm, the inner diameter of the O-shaped ring is 285.5 mm to 287 mm, the wire diameter of the O-shaped ring is 4.6 mm to 5 mm, and the Shore hardness of the O-shaped ring is 65HA to 80 HA;
and an anti-abrasion coating is coated on the region, opposite to the inner side wall of the boss, of the outer side of the lower end of the static ring guide sleeve.
In one possible implementation, the cross section of the fixing groove is circular arc.
In one possible implementation, the material of the wear protection coating comprises chromium carbide.
In one possible implementation, the thickness of the wear-resistant coating is between 0.2 mm and 0.45 mm;
the bonding strength of the anti-abrasion coating and the base material of the static ring guide sleeve is between 60 and 90 MPa.
In one possible implementation, the vickers hardness of the wear protection coating is between 600HV and 1100 HV.
In one possible implementation, the roughness of the wear protection coating is between 0.02 and 0.2 microns.
In one possible implementation, the O-ring material is ethylene propylene diene monomer.
In one possible implementation, the material of the retainer ring is polytetrafluoroethylene.
In one possible implementation, the precompression rate of the O-ring is between 0.0% and 0.55%.
In one possible implementation, the compression of the O-ring is between 10% and 15%.
The invention has the beneficial effects that: in the embodiment of the disclosure, the outer diameters of the O-shaped ring and the stationary ring guide sleeve can be better matched, the hardness of the O-shaped ring is moderate, the friction resistance between the stationary ring guide sleeve and the stationary ring seat is effectively reduced, in addition, the retainer ring and the stationary ring guide sleeve are in slight stretching fit, the reciprocating motion resistance of the O-shaped ring and the stationary ring guide sleeve can be reduced by the retainer ring, meanwhile, the friction resistance between the stationary ring guide sleeve and the stationary ring seat can be further reduced by the anti-abrasion coating coated on the region, opposite to the inner side wall of the boss, of the lower end of the stationary ring guide sleeve, so that the follow-up performance of the stationary ring is obviously improved, the O-shaped ring can still be basically kept in an original state after long-term use, the low-pressure leakage. The floating sealing device of the nuclear power station hydrodynamic pressure type main pump mechanical seal can solve the problem that a certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, has strong practicability and popularization value, is widely applied to domestic nuclear power stations and is estimated slightly at first, solves the problem that the certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, creates economic value of more than 5000 ten thousand every year, and has great significance for guaranteeing the safety of the nuclear power stations.
Drawings
FIG. 1 is a cross-sectional view of a floating seal arrangement of a nuclear power plant hydrodynamic type main pump mechanical seal shown in accordance with an exemplary embodiment.
FIG. 2 is a partial cross-sectional view of a floating seal arrangement of a nuclear power plant hydrodynamic type main pump mechanical seal shown in accordance with an exemplary embodiment.
Detailed Description
The invention is described in further detail below with reference to the figures and the embodiments.
FIG. 1 is a floating seal arrangement of a nuclear power plant hydrodynamic type main pump mechanical seal, according to an exemplary embodiment. FIG. 2 is a partial cross-sectional view of a floating seal arrangement of a nuclear power plant hydrodynamic type main pump mechanical seal shown in accordance with an exemplary embodiment. As shown in fig. 1 and 2, the floating seal device for a mechanical seal of a hydrodynamic main pump of a nuclear power plant includes: the device comprises an O-shaped ring 21, a retainer ring 22, a static ring seat 12 and a static ring guide sleeve 10.
As shown in fig. 1, the hydrodynamic type main pump mechanical seal of the nuclear power plant may include: the main shaft 20, the shaft sleeve 19, the moving ring seat 17, the moving ring assembly 15, the stationary ring assembly 14, the stationary ring seat 12, the stationary ring guide 10, and a housing (not shown in the figure), wherein the main shaft 20, the shaft sleeve 19, the moving ring seat 17, the moving ring assembly 15, the stationary ring assembly 14, the stationary ring seat 12, and the stationary ring guide 10 are located in the housing.
The shaft sleeve 19 can be tubular, and the movable ring seat 17, the movable ring assembly 15, the static ring assembly 14, the static ring seat 12 and the static ring guide sleeve 10 are annular; the moving ring assembly 15 comprises a moving ring 153, a moving ring insert 152 and a moving ring retaining ring 151 which are nested from inside to outside; the movable ring, the movable ring embedding ring and the movable ring retaining ring are in interference fit; stationary ring assembly 14 may include a stationary ring 143, a stationary ring insert 142, and a stationary ring retainer 141 nested inside-out; the static ring, the static ring inlaying ring and the static ring retaining ring are in interference fit. It should be noted that, the stationary ring assembly 14 and the moving ring assembly 15 with different structures may be selected as needed, and the structure and the connection manner of the stationary ring assembly 14 and the moving ring assembly 15 are not limited in the embodiment of the present disclosure.
The spindle sleeve 19 is fixedly sleeved outside the spindle 20, the movable ring seat 17 is fixedly sleeved outside the spindle sleeve 19 (for example, the movable ring seat 17 may be fixedly connected to the spindle sleeve 19 through the fixing pin 18), the movable ring assembly 15 is sleeved outside the spindle sleeve 19, the movable ring assembly 15 is fixedly connected to the movable ring seat 17, and the movable ring assembly 15 is located above the movable ring seat 17 (for example, the movable ring assembly 15 may be fixedly connected to the movable ring seat 17 through the second spring pin 16 and the fixing pin 18, respectively, and a sealing ring 23 may be further disposed between the movable ring assembly 15 and the movable ring seat 17 to increase the stability between the movable ring assembly 12 and the movable ring seat 17);
the static ring guide sleeve 10 is sleeved outside the shaft sleeve 19, the upper end of the static ring guide sleeve 10 is provided with a step part which extends outwards along the radial direction, the step part is fixedly connected with the inner side of the shell, the edge of the static ring seat 12 is provided with a boss which extends upwards along the axial direction, the upper surface of the boss is elastically connected with the lower surface of the step part (for example, the upper surface of the boss of the static ring seat 12 can be elastically connected with the lower surface of the step part through a spring 25, in addition, a positioning pin 11 can be inserted between the upper surface of the static ring seat 12 and the lower surface of the step part), the static ring component 14 is fixedly connected with the static ring seat 12, the static ring component 14 is positioned below the static ring seat 12 (for example, the static ring component 14 can be fixedly connected with the static ring seat 12 through a first spring pin 13 and a fixing pin 18 respectively), and a;
generally, the gap between the stationary ring assembly 14 and the moving ring assembly 15 is required to have a spacing of 5 microns to 10 microns to effectively prevent liquid from leaking out of the gap between the stationary ring assembly 14 and the moving ring assembly 15.
The main pump is at the operation in-process, because establish the cold water temperature, the bearing seal is poured into the temperature and all is changing every day, lead to quiet ring subassembly and quiet ring seat to carry out small up-and-down reciprocating motion for quiet ring guide cover all the time, the O shape circle in the quiet ring guide cover outside is the wave distortion, cause quiet ring seat in the reciprocating motion in-process big friction resistance for quiet ring guide cover, and quiet ring guide cover surface produces wearing and tearing after long-time operation, surface wear has increaseed friction resistance, form vicious circle, finally lead to quiet ring seat very easily to jam in the reciprocating motion process for quiet ring guide cover, the following performance of quiet ring subassembly and quiet ring guide cover seriously descends, make the gap interval between the upper surface of the lower surface of quiet ring subassembly and rotating ring subassembly too big (for example be greater than 10 microns), cause mechanical seal low pressure to leak. After overhaul, the original design is found to be in accordance with the standard ISO 3601-2; 2018-08, the inner diameter of an O-shaped ring sleeved on the outer side of the lower end of a static ring guide sleeve is 291.47 mm, the wire diameter is 5.33 mm, and the original designed O-shaped ring is too large relative to the outer diameter of a 286.5 mm static ring guide sleeve, so that the static ring seat is easily distorted and deformed in the reciprocating motion process relative to the static ring guide sleeve, and further the mechanical seal low-pressure leakage is caused; 2018-08 does not record the size data of the O-ring that is adapted to the size of the stationary ring guide sleeve. Because the difference between the sizes of various O-shaped rings is as small as 0.1 millimeter, the O-shaped ring with proper size and hardness needs to be selected from the O-shaped rings with mass sizes to seal between the static ring guide sleeve and the static ring seat.
To this problem, this disclosed embodiment establishes retaining ring 22 cover in the outside of quiet ring guide pin bushing lower extreme, the fixed slot is seted up along circumference in the outside of retaining ring 22, O shape circle 21 cover is established in the fixed slot in the outside of retaining ring, retaining ring 22 and O shape circle 21 are located the recess, the width of recess can slightly be less than retaining ring 22's width, and like this, the recess can form the extrusion to retaining ring 22, make retaining ring 22 produce elastic deformation, and then extrude O type circle between fixed slot and recess, and like this, can effectively avoid O shape circle round trip movement in the recess, reduce the wearing and tearing of O shape circle to quiet ring guide pin bushing. In addition, the inner diameter of the retainer ring is set to be between 285 mm and 286 mm, the inner diameter of the O-shaped ring at the lower end of the stationary ring guide sleeve can be set to be between 285.5 mm and 287 mm, the wire diameter of the O-shaped ring is set to be between 4.6 mm and 5 mm, and the Shore hardness of the O-shaped ring is between 65HA and 70-80 HA. And a wear-resistant coating is coated on the region, opposite to the inner side wall of the boss of the stationary ring seat 12, of the outer side of the lower end of the stationary ring guide sleeve 10, wherein the wear-resistant coating may be made of chromium carbide (it should be noted that the wear-resistant coating may also be made of ceramic particles, etc., and the embodiment of the disclosure does not limit the material of the wear-resistant coating as long as the wear-resistant coating can reduce the wear between the stationary ring guide sleeve and the stationary ring seat as well as between the stationary ring guide sleeve and the O-ring).
In one possible implementation, the wear-resistant coating may have a thickness of between 0.2 mm and 0.45 mm, for example, the wear-resistant coating may have a thickness of 0.3 mm. The bonding strength of the anti-abrasion coating and the base material of the static ring guide sleeve is between 60 and 90 MPa.
In one possible implementation, the vickers hardness of the wear resistant coating is between 600HV and 1100 HV. For example, the vickers hardness of the wear resistant coating may be 900 HV.
In one possible implementation, the wear resistant coating has a roughness between 0.02 microns and 0.2 microns. For example, the wear resistant coating may have a roughness of 0.2 microns.
In a possible implementation manner, the cross section of the fixing groove of the retainer ring can be arc-shaped, and can be better matched with the outline of the O-shaped ring, so that the O-shaped ring can be better fixed.
In one possible implementation, the O-ring material may be Ethylene Propylene Diene Monomer (EPDM). The ethylene propylene diene rubber is a copolymer of ethylene, propylene and a small amount of non-conjugated diene, is one of ethylene propylene rubbers, and has excellent ozone resistance, heat resistance, weather resistance and other aging resistance because the main chain of the ethylene propylene diene rubber is composed of chemically stable saturated hydrocarbon and only contains unsaturated double bonds in the side chain.
In a possible implementation manner, the material of the retainer ring may be Polytetrafluoroethylene (PTFE) which is a polymer prepared by polymerizing tetrafluoroethylene as a monomer, and the polytetrafluoroethylene has an extremely low friction coefficient, so that abrasion of the stationary ring guide sleeve can be effectively reduced.
In one example, the design of an embodiment of the present disclosure includes: an O-shaped ring with the inner diameter of 286 mm, the wire diameter of 5 mm and the Shore hardness of 70-80HA is adopted, a check ring with the inner diameter of 285.5 mm is adopted, the groove width of a groove is 7.6 mm (the groove width of the groove can be 152% of the size of the O-shaped ring), and a chromium carbide wear-resistant coating with the thickness of 0.3 mm is coated on the region, opposite to the inner side wall of a boss of a static ring seat, of the outer side of the lower end of a static ring guide sleeve, the Vickers hardness of the wear-resistant coating is 900HV, and the roughness of the wear-resistant coating is. The original design adopts an O-shaped ring with the inner diameter of 291.47 mm, the wire diameter of 5.33 mm and the Shore hardness of 80-85HA, and the surface of the stationary ring guide sleeve is not coated, so that the design of the embodiment of the disclosure and the original design are subjected to the following comparative test under the condition of silicone grease lubrication.
1. Comparative friction test
The compression amount of the O-ring designed in the embodiment of the present disclosure is 10.85%, the pre-compression rate is 0.22%, and the compression amount a of the O-ring can be determined according to the formula a being 1-B/C, where B is the groove depth of the groove of the inner wall of the boss of the stationary ring seat, and C is the wire diameter of the O-ring. The precompression ratio D of the O-ring may be determined according to the formula D/(F + C2), where E is the difference between the outer diameter of the O-ring and the outer diameter of the groove of the inner wall of the boss of the stationary ring seat, F is the inner diameter of the O-ring, and C is the wire diameter of the O-ring.
The original design corresponds to a friction force of greater than 300 newtons.
The design of the disclosed embodiment corresponds to a friction of 85 newtons.
In tests, the inner diameter of the O-shaped ring disclosed by the embodiment of the disclosure enables the O-shaped ring to be better attached to the movable ring guide sleeve, and the compression amount meets the range requirement of the dynamic sealing standard from 4% to 11%, so that the friction force corresponding to the O-shaped ring disclosed by the embodiment of the disclosure is greatly reduced compared with the friction force between the originally designed O-shaped ring and the surface of the stationary ring guide sleeve.
2. Comparative rebound Performance test.
In the vice reciprocating motion in-process of friction, it is great to adopt the fluctuation of original design O circle frictional force, the phenomenon that the quiet ring seat "crawled" on quiet ring guide sleeve can be observed to the naked eye in the experimentation, and in the upward motion process that replies, the quiet ring seat pressure that receives of testing is 0, the follow-up performance of explanation quiet ring seat is not enough, the resilience performance is poor, and the O shape circle of this disclosure, 3 experimental good repeatability, the quiet ring seat pressure differential that receives of testing is stable, and in the reciprocating motion in-process, the original point can be got back to fast to the quiet ring seat, the follow-up performance of explanation quiet ring seat is good, the resilience performance is good.
3. And (5) carrying out a wear resistance comparison test.
After the original design is tested for 100 hours, the surface roughness of the guide sleeve of the static ring is obviously increased compared with that before the test; mean change Ra +0.115um (micrometers);
after the design of the embodiment of the disclosure is tested for 100 hours, the surface roughness of the static ring guide sleeve is not obviously increased, and the mean value change of the surface roughness of the static ring guide sleeve is equal to +0.01 um.
4. And comparing the appearance after the test.
After the design of the embodiment of the disclosure is tested for 100 hours, the originally designed O-shaped ring has a normal appearance and basically has no extrusion, torsion and deformation traces.
After the original design is tested for 100 hours, the cross section of the O-shaped ring designed by the embodiment of the disclosure has obvious extrusion, torsion and deformation traces.
5. And (4) comparing the leakage flow after the test.
After the original design is tested for 100 hours, the low-pressure leakage flow fluctuates at 12-15l/h (liter per hour) through a durability test for 100 hours, and the median value is about 13.6 l/h;
after the design of the embodiment of the disclosure is tested for 100 hours, the low-pressure leakage flow fluctuates at 10-13l/h, and the median value is about 11.5 l/h; compared with the leakage flow rate reduced by about 2.1l/h after the original design test, the follow-up property of the improved O-shaped ring is improved, the thickness of the mechanical sealing liquid film is reduced, and the low-pressure leakage flow is reduced.
In the embodiment of the disclosure, the outer diameters of the O-shaped ring and the stationary ring guide sleeve can be better matched, the hardness of the O-shaped ring is moderate, the friction resistance between the stationary ring guide sleeve and the stationary ring seat is effectively reduced, in addition, the retainer ring and the stationary ring guide sleeve are in slight stretching fit, the reciprocating motion resistance of the O-shaped ring and the stationary ring guide sleeve can be reduced by the retainer ring, meanwhile, the friction resistance between the stationary ring guide sleeve and the stationary ring seat can be further reduced by the anti-abrasion coating coated on the region, opposite to the inner side wall of the boss, of the lower end of the stationary ring guide sleeve, so that the follow-up performance of the stationary ring is obviously improved, the O-shaped ring can still be basically kept in an original state after long-term use, the low-pressure leakage. The floating sealing device of the nuclear power station hydrodynamic pressure type main pump mechanical seal can solve the problem that a certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, has strong practicability and popularization value, is widely applied to domestic nuclear power stations and is estimated slightly at first, solves the problem that the certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, creates economic value of more than 5000 ten thousand every year, and has great significance for guaranteeing the safety of the nuclear power stations.
Having described embodiments of the present disclosure, the foregoing description is intended to be exemplary, not exhaustive, and not limited to the disclosed embodiments. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the described embodiments. The terms used herein were chosen in order to best explain the principles of the embodiments, the practical application, or technical improvements to the techniques in the marketplace, or to enable others of ordinary skill in the art to understand the embodiments disclosed herein.
Claims (10)
1. A floating seal device of a mechanical seal of a hydrodynamic pressure type main pump of a nuclear power plant is characterized by comprising: the fixed ring seat and the fixed ring guide sleeve are annular, the upper end of the fixed ring guide sleeve is provided with a step part which extends outwards along the radial direction, the edge of the fixed ring seat is provided with a boss which extends upwards along the axial direction, the lower surface of the step part is elastically connected with the upper surface of the boss, the outer side of the lower end of the fixed ring guide sleeve is opposite to the inner side wall of the boss, and the inner side wall of the boss is provided with a circumferential groove;
the check ring is sleeved on the outer side of the lower end of the stationary ring guide sleeve, a fixing groove is formed in the outer side of the check ring along the circumferential direction, the O-shaped ring is sleeved in the fixing groove in the outer side of the check ring, the check ring and the O-shaped ring are located in the groove, the groove extrudes the check ring to enable the check ring to generate elastic deformation, the O-shaped ring is further extruded between the fixing groove and the groove, and the check ring and the O-shaped ring are used for sealing a gap between the outer side of the lower end of the stationary ring guide sleeve and the inner side wall of the boss;
the outer diameter of the lower end of the static ring guide sleeve is 286.5 mm, the inner diameter of the retainer ring is 285 mm to 286 mm, the inner diameter of the O-shaped ring is 285.5 mm to 287 mm, the wire diameter of the O-shaped ring is 4.6 mm to 5 mm, and the Shore hardness of the O-shaped ring is 65HA to 80 HA;
and an anti-abrasion coating is coated on the region, opposite to the inner side wall of the boss, of the outer side of the lower end of the static ring guide sleeve.
2. The floating seal device of a mechanical seal of a hydrodynamic main pump of a nuclear power plant as claimed in claim 1, wherein the cross-section of the fixing groove is circular arc-shaped.
3. The floating seal arrangement of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the material of said wear-resistant coating comprises chromium carbide.
4. The floating seal arrangement of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein said wear-resistant coating has a thickness of 0.2 mm to 0.45 mm;
the bonding strength of the anti-abrasion coating and the base material of the static ring guide sleeve is between 60 and 90 MPa.
5. The floating seal arrangement of a hydrodynamic main pump mechanical seal of a nuclear power plant as claimed in claim 1, wherein said wear-resistant coating has a vickers hardness of between 600HV and 1100 HV.
6. The floating seal arrangement of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein said wear-resistant coating has a roughness of 0.02 to 0.2 microns.
7. The floating seal device of a mechanical seal of a hydrodynamic main pump of a nuclear power plant as claimed in claim 1, wherein the material of the O-ring is ethylene propylene diene monomer.
8. The floating seal device for the mechanical seal of the hydrodynamic main pump of a nuclear power plant as claimed in claim 1, wherein the material of the retainer ring is polytetrafluoroethylene.
9. The floating seal arrangement of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the precompression rate of said O-ring is between 0.0% and 0.55%.
10. The floating seal arrangement of a hydrodynamic main pump mechanical seal of a nuclear power plant as claimed in claim 1, wherein the compression of said O-ring is between 10% and 15%.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010757083.4A CN112096873A (en) | 2020-07-31 | 2020-07-31 | Floating sealing device for mechanical seal of hydrodynamic main pump of nuclear power station |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010757083.4A CN112096873A (en) | 2020-07-31 | 2020-07-31 | Floating sealing device for mechanical seal of hydrodynamic main pump of nuclear power station |
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| CN112096873A true CN112096873A (en) | 2020-12-18 |
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| CN202010757083.4A Pending CN112096873A (en) | 2020-07-31 | 2020-07-31 | Floating sealing device for mechanical seal of hydrodynamic main pump of nuclear power station |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112879570A (en) * | 2021-04-19 | 2021-06-01 | 重庆胤合石油化工机械制造有限公司 | Spring mechanical seal compensating ring assembly |
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