CN111911632A - Sealing assembly of nuclear power station hydrodynamic pressure type main pump mechanical seal - Google Patents
Sealing assembly of nuclear power station hydrodynamic pressure type main pump mechanical seal Download PDFInfo
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- CN111911632A CN111911632A CN202010756108.9A CN202010756108A CN111911632A CN 111911632 A CN111911632 A CN 111911632A CN 202010756108 A CN202010756108 A CN 202010756108A CN 111911632 A CN111911632 A CN 111911632A
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- ring
- nuclear power
- main pump
- mechanical seal
- guide sleeve
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- 238000007789 sealing Methods 0.000 title abstract description 11
- 230000003068 static effect Effects 0.000 claims description 44
- 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 11
- 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
- 238000005299 abrasion Methods 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
- 239000004519 grease Substances 0.000 claims description 3
- 229920001296 polysiloxane Polymers 0.000 claims description 3
- 238000012423 maintenance Methods 0.000 abstract description 3
- 238000013461 design Methods 0.000 description 16
- 238000012360 testing method Methods 0.000 description 11
- 238000000034 method Methods 0.000 description 9
- 230000000052 comparative effect Effects 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000001125 extrusion Methods 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000003746 surface roughness 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
- 230000008859 change Effects 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
- -1 ethylene, propylene Chemical group 0.000 description 1
- 230000003203 everyday effect Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 238000011056 performance test Methods 0.000 description 1
- 229930195734 saturated hydrocarbon Natural products 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
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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
- F04D29/106—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
-
- 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)
- Gasket Seals (AREA)
Abstract
The disclosure belongs to the technical field of nuclear power maintenance, and particularly relates to a sealing assembly for a mechanical seal of a hydrodynamic pressure type main pump of a nuclear power station. In the embodiment of the disclosure, because the outer diameters of the O-ring and the stationary ring guide sleeve can be better matched, the frictional resistance between the stationary ring guide sleeve and the stationary ring seat is greatly reduced compared with the related art, so that the follow-up performance of the stationary ring is obviously improved, the O-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 solved. 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 sealing assembly of 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
To overcome the problems in the related art, a seal assembly of a mechanical seal of a hydrodynamic type main pump of a nuclear power plant is provided.
According to an aspect of the embodiments of the present disclosure, there is provided a seal assembly of a mechanical seal of a hydrodynamic main pump of a nuclear power plant, the seal assembly including: the outer side of the lower end of the static ring guide sleeve is opposite to the inner side wall of the boss, a circumferential groove is formed in the inner side wall of the boss, the O-shaped ring is sleeved on the outer side of the lower end of the static ring guide sleeve, and the O-shaped ring is positioned in the groove so as to seal a gap between the outer side of the lower end of the static ring guide sleeve and the inner side wall of the boss;
an anti-abrasion coating is coated on the region of the outer side of the lower end of the static ring guide sleeve, which is opposite to 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 O-shaped ring is 285.5 mm to 287 mm, the wire diameter of the O-shaped ring is 5 mm to 5.4 mm, and the Shore hardness of the O-shaped ring is 65HA to 80 HA.
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 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%.
In one possible implementation, the surface of the O-ring material is coated with silicone grease.
In one possible implementation, the seal assembly of the mechanical seal of the hydrodynamic main pump of the nuclear power plant further includes: a support ring;
the support ring is located in the groove, and the support ring is located below the O-ring.
The invention has the beneficial effects that: in the embodiment of the disclosure, because the external diameter of O shape circle and quiet ring guide pin bushing can be better cooperation, make frictional resistance between quiet ring guide pin bushing and the quiet ring seat descend by a wide margin in comparison with correlation technique, in addition, the regional coating wear-resisting coating that the inside wall of quiet ring guide pin bushing lower extreme outside and boss is relative, further effectively reduced the wearing and tearing between O shape circle and the quiet ring guide pin bushing, make the follow-up performance of quiet ring obviously improve from this, the O shape circle still can keep the original state basically after long-term the use, effectively reduce the low pressure leakage volume of mechanical seal, the high problem of leakage volume can be improved. The sealing assembly 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, is estimated slightly at first, solves the problem that the certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, can create more than 5000 ten thousand economic values 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 seal assembly 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 cross-sectional view of a seal assembly of a nuclear power plant hydrodynamic type main pump mechanical seal shown in accordance with an exemplary embodiment. As shown in fig. 1, the seal assembly of the mechanical seal of the hydrodynamic main pump of the nuclear power plant includes: the O-shaped ring 21, the static ring seat 12 and the static ring guide sleeve 10, and the hydrodynamic type main pump mechanical seal of the nuclear power station can comprise: 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 is 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;
the inner side wall of the boss of the static ring seat 12 is provided with a circumferential groove, the O-shaped ring 21 is sleeved on the outer side of the lower end of the static ring guide sleeve 10, and the O-shaped ring 21 is positioned in the groove so as to seal a gap between the outer side of the lower end of the static ring guide sleeve 10 and the inner side wall of the boss.
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 address this problem, in the embodiments of the present disclosure, the inner diameter of the O-ring at the lower end of the stationary ring guide sleeve is set to be between 285.5 mm and 287 mm, the wire diameter of the O-ring is set to be between 5 mm and 5.4 mm, and the shore hardness of the O-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 the embodiment of the disclosure, because the outer diameters of the O-ring and the stationary ring guide sleeve can be better matched, the frictional resistance between the stationary ring guide sleeve and the stationary ring seat is greatly reduced compared with the related art, so that the follow-up performance of the stationary ring is obviously improved, the O-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 solved. The sealing assembly 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, is estimated slightly at first, solves the problem that the certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, can create more than 5000 ten thousand economic values every year, and has great significance for guaranteeing the safety of the nuclear power stations.
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 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 5.3 mm and the Shore hardness of 70-80HA is adopted, a chromium carbide wear-resistant coating with the thickness of 0.3 mm is coated on the area, opposite to the inner side wall of the boss of the static ring seat, of the outer side of the lower end of the static ring guide sleeve, the Vickers hardness of the wear-resistant coating is 900HV, and the roughness of the wear-resistant coating is 0.2 micron. 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 force of 29 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 O-shaped ring and the surface of the stationary ring guide sleeve in the original design.
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 shape circle frictional force, the phenomenon that the quiet ring seat "crawled" on quiet ring guide can be observed to the naked eye in the experimentation, and in the upward motion process of replying, 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 this disclosed embodiment is tested for 100 hours for stationary ring guide pin bushing surface roughness has reduced on the contrary, observes the phenomenon of similar mechanical structure "running in", and mean value variation value Δ Ra is-0.14 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 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 12.7 l/h; compared with the leakage flow rate reduced by about 0.9l/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, because the outer diameters of the O-ring and the stationary ring guide sleeve can be better matched, the frictional resistance between the stationary ring guide sleeve and the stationary ring seat is greatly reduced compared with the related art, so that the follow-up performance of the stationary ring is obviously improved, the O-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 solved. The sealing structure of the nuclear power station hydrodynamic pressure type main pump mechanical equipment 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, is estimated slightly at first, solves the problem that the certain hydrodynamic pressure type main pump mechanical seal frequently breaks down, can create more than 5000 ten thousand economic values every year, and has great significance for guaranteeing the safety of the nuclear power stations.
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 one possible implementation, as shown in fig. 1, the servo seal structure of a mechanical seal of a hydrodynamic main pump of a nuclear power plant further includes: a support ring 22, the support ring 22 may be located within the groove, and the support ring 22 may be located below the O-ring.
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 seal assembly of a nuclear power plant hydrodynamic pressure type main pump mechanical seal, characterized by comprising: the outer side of the lower end of the static ring guide sleeve is opposite to the inner side wall of the boss, a circumferential groove is formed in the inner side wall of the boss, the O-shaped ring is sleeved on the outer side of the lower end of the static ring guide sleeve, and the O-shaped ring is positioned in the groove so as to seal a gap between the outer side of the lower end of the static ring guide sleeve and the inner side wall of the boss;
an anti-abrasion coating is coated on the region of the outer side of the lower end of the static ring guide sleeve, which is opposite to 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 O-shaped ring is 285.5 mm to 287 mm, the wire diameter of the O-shaped ring is 5 mm to 5.4 mm, and the Shore hardness of the O-shaped ring is 65HA to 80 HA.
2. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the material of said wear-resistant coating comprises chromium carbide.
3. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the 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.
4. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the vickers hardness of the wear-resistant coating is between 600HV and 1100 HV.
5. The seal assembly 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.
6. The seal assembly of a nuclear power plant hydrodynamic pressure type main pump mechanical seal according to claim 1, characterized in that the O-ring material is ethylene propylene diene monomer rubber.
7. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the precompression rate of the O-ring is between 0.0% and 0.55%.
8. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, wherein the O-ring compression is between 10% and 15%.
9. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal according to claim 1, wherein the O-ring material surface is coated with silicone grease.
10. The seal assembly of a nuclear power plant hydrodynamic main pump mechanical seal of claim 1, further comprising: a support ring;
the support ring is located in the groove, and the support ring is located below the O-ring.
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| CN212509527U (en) * | 2020-07-31 | 2021-02-09 | 中核核电运行管理有限公司 | Sealing assembly of nuclear power station hydrodynamic pressure type main pump mechanical seal |
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2020
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