CN212959854U - Follow-up sealing structure of hydrodynamic pressure type main pump mechanical seal of nuclear power station - Google Patents
Follow-up sealing structure of hydrodynamic pressure type main pump mechanical seal of nuclear power station Download PDFInfo
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- CN212959854U CN212959854U CN202021556896.9U CN202021556896U CN212959854U CN 212959854 U CN212959854 U CN 212959854U CN 202021556896 U CN202021556896 U CN 202021556896U CN 212959854 U CN212959854 U CN 212959854U
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Abstract
The disclosure belongs to the technical field of nuclear power maintenance, and particularly relates to a follow-up sealing structure 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 utility model belongs to the technical field of the nuclear power maintenance, concretely relates to nuclear power station hydrodynamic pressure type main pump mechanical seal's follow-up seal structure.
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.
SUMMERY OF THE UTILITY MODEL
In order to overcome the problems in the related art, the follow-up sealing structure 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 follow-up seal structure of a mechanical seal of a hydrodynamic main pump of a nuclear power plant, including: o shape circle, quiet ring seat, quiet ring guide pin bushing, nuclear power station hydrodynamic pressure type main pump mechanical seal includes: the device comprises a main shaft, a shaft sleeve, a movable ring seat, a movable ring assembly, a static ring seat, a static ring guide sleeve and a shell, wherein the shaft sleeve is tubular, and the movable ring seat, the movable ring assembly, the static ring seat and the static ring guide sleeve are annular;
the shaft sleeve is fixedly sleeved on the outer side of the main shaft, the movable ring seat is fixedly sleeved on the outer side of the shaft sleeve, the movable ring assembly is sleeved on the outer side of the shaft sleeve and is fixedly connected with the movable ring seat, and the movable ring assembly is positioned above the movable ring seat;
the static ring guide sleeve is sleeved outside the shaft sleeve, a step part extending outwards in the radial direction is arranged at the upper end of the static ring guide sleeve, the step part is fixedly connected with the inner side of the shell, the upper surface of the static ring seat is elastically connected with the lower surface of the step part, the static ring assembly is fixedly connected with the static ring seat, the static ring assembly is positioned below the static ring seat, and a gap is formed between the lower surface of the static ring assembly and the upper surface of the movable ring assembly;
the edge of the static ring seat is provided with a boss extending upwards along the axial direction, the outer side of the lower end of the static ring guide sleeve is opposite to the inner side wall of the boss, the inner side wall of the boss is provided with a circumferential groove, 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;
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 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 servo seal structure 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.
In one possible implementation manner, the moving ring assembly comprises a moving ring, a moving ring embedding ring and a moving ring retaining ring which are nested from inside to outside;
the movable ring, the movable ring inlaying ring and the movable ring maintaining ring are in interference fit.
In one possible implementation, the static ring assembly comprises a static ring, a static ring inlaying ring and a static ring retaining ring which are nested from inside to outside;
and the static ring, the static ring embedding ring and the static ring retaining ring are in interference fit.
The beneficial effects of the utility model reside in that: 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 basically keep the 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 follow-up sealing structure 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, and has strong practicability and popularization value.
Drawings
Fig. 1 is a cross-sectional view of a follower seal structure of a nuclear power plant hydrodynamic type main pump mechanical seal shown in accordance with an exemplary embodiment.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
Fig. 1 is a cross-sectional view of a follower seal structure of a nuclear power plant hydrodynamic type main pump mechanical seal shown in accordance with an exemplary embodiment. As shown in fig. 1, the mechanical seal follower seal structure of the hydrodynamic pressure type main pump of the nuclear power plant includes: o shape circle 21, stationary ring seat 12, stationary ring guide pin bushing 10, nuclear power station hydrodynamic pressure type main pump mechanical seal includes: 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 upper surface of the static ring seat 12 is elastically connected with the lower surface of the step part (for example, 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 gap is formed between the lower surface of; 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 edge of the static ring seat 12 is provided with a boss extending upwards along the axial direction, the outer side of the lower end of the static ring guide sleeve 10 is opposite to the inner side wall of the boss, the inner side wall of the boss is provided with a circumferential groove, an 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 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 embodiment 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 80 HA.
In one example, the presently disclosed embodiments utilize an O-ring having an inner diameter of 286 mm, a wire diameter of 5.3 mm, and a shore hardness of 65HA-80HA, which was tested in a friction force comparison test under silicone grease lubrication conditions with an originally designed O-ring having an inner diameter of 291.47 mm, a wire diameter of 5.33 mm, and a shore hardness of 80-85 HA.
The compression amount of the O-ring with the inner diameter of 286 mm and the wire diameter of 5.3 mm 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 friction force corresponding to the O-shaped ring adopting the original design is more than 300 newton.
The friction force corresponding to the O-ring using the disclosed embodiment is 66 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 well 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.
In one example, the presently disclosed embodiments utilize an O-ring having an inner diameter of 286 mm, a wire diameter of 5.3 mm, and a shore hardness of 65HA-80HA, which was tested for resiliency under silicone grease lubrication conditions against an originally designed O-ring having an inner diameter of 291.47 mm, a wire diameter of 5.33 mm, and a shore hardness of 80-85 HA.
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.
In one example, the presently disclosed embodiments utilize an O-ring having an inner diameter of 286 mm, a wire diameter of 5.3 mm, and a shore hardness of 65HA-80HA, which was tested for wear resistance in comparison to an originally designed O-ring having an inner diameter of 291.47 mm, a wire diameter of 5.33 mm, and a shore hardness of 80-85HA under silicone grease lubrication conditions.
By adopting the originally designed O-shaped ring, after 100-hour test, the surface roughness of the guide sleeve of the static ring is obviously increased compared with that before the test; mean change Ra +0.115 um;
when the O-shaped ring of the embodiment of the disclosure is adopted, after a 100-hour test, the surface roughness of the static ring guide sleeve is only slightly increased compared with that before the test, the surface of the static ring guide sleeve is still smooth and normal, and the mean value is changed to Ra +0.055 um.
In one example, the presently disclosed embodiments utilize an O-ring with an inner diameter of 286 mm, a wire diameter of 5.3 mm, and a shore hardness of 65HA-80HA, for post-test profile comparison with an originally designed O-ring with an inner diameter of 291.47 mm, a wire diameter of 5.33 mm, and a shore hardness of 80-85HA under silicone grease lubrication conditions.
When the O-shaped ring disclosed by the embodiment of the disclosure is adopted, after a test of 100 hours, the O-shaped ring has a normal shape and has no extrusion, torsion and deformation traces.
By adopting the originally designed O-shaped ring, after 100-hour test, the cross section of the O-shaped ring has obvious extrusion, torsion and deformation traces.
In one example, the disclosed embodiments utilize an O-ring with an inner diameter of 286 mm, a wire diameter of 5.3 mm, and a shore hardness of 65HA-80HA, compared to an originally designed O-ring with an inner diameter of 291.47 mm, a wire diameter of 5.33 mm, and a shore hardness of 80-85HA for post-test leakage flow rate under silicone grease lubrication conditions.
An O-shaped ring with original design is adopted, and through a 100-hour durability test, the low-pressure leakage flow fluctuates at 12-15l/h (liter per hour), and the median value is about 13.6 l/h;
by adopting the O-shaped ring of the embodiment of the disclosure, through a durability test 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 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 follow-up sealing structure 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, and has strong practicability and popularization value.
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 (8)
1. A follow-up seal structure of a mechanical seal of a hydrodynamic pressure type main pump of a nuclear power plant is characterized by comprising: o shape circle, quiet ring seat, quiet ring guide pin bushing, nuclear power station hydrodynamic pressure type main pump mechanical seal includes: the device comprises a main shaft, a shaft sleeve, a movable ring seat, a movable ring assembly, a static ring seat, a static ring guide sleeve and a shell, wherein the shaft sleeve is tubular, and the movable ring seat, the movable ring assembly, the static ring seat and the static ring guide sleeve are annular;
the shaft sleeve is fixedly sleeved on the outer side of the main shaft, the movable ring seat is fixedly sleeved on the outer side of the shaft sleeve, the movable ring assembly is sleeved on the outer side of the shaft sleeve and is fixedly connected with the movable ring seat, and the movable ring assembly is positioned above the movable ring seat;
the static ring guide sleeve is sleeved outside the shaft sleeve, a step part extending outwards in the radial direction is arranged at the upper end of the static ring guide sleeve, the step part is fixedly connected with the inner side of the shell, the upper surface of the static ring seat is elastically connected with the lower surface of the step part, the static ring assembly is fixedly connected with the static ring seat, the static ring assembly is positioned below the static ring seat, and a gap is formed between the lower surface of the static ring assembly and the upper surface of the movable ring assembly;
the edge of the static ring seat is provided with a boss extending upwards along the axial direction, the outer side of the lower end of the static ring guide sleeve is opposite to the inner side wall of the boss, the inner side wall of the boss is provided with a circumferential groove, 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;
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 follow-up seal structure of a mechanical seal of a hydrodynamic pressure type main pump of a nuclear power plant as claimed in claim 1, wherein the material of the O-ring is ethylene propylene diene monomer.
3. The follower seal structure of a mechanical seal of a main pump of the nuclear power plant hydrodynamic type according to claim 1, wherein a precompression rate of the O-ring is between 0.0% and 0.55%.
4. The follow-up seal structure of a mechanical seal of a main pump of hydrodynamic type of a nuclear power plant as claimed in claim 1, wherein the compression amount of the O-ring is 10 to 15%.
5. The follow-up seal structure of a mechanical seal of a main pump of hydrodynamic type of a nuclear power plant as claimed in claim 1, wherein the surface of the material of the O-ring is coated with silicone grease.
6. The servo seal structure of a mechanical seal of a hydrodynamic main pump of a nuclear power plant as claimed in 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.
7. The follow-up seal structure of a mechanical seal of a hydrodynamic main pump of a nuclear power plant as claimed in claim 1, wherein the rotating ring assembly comprises a rotating ring, a rotating ring insert ring and a rotating ring retainer ring which are nested from inside to outside;
the movable ring, the movable ring inlaying ring and the movable ring maintaining ring are in interference fit.
8. The follow-up seal structure of a mechanical seal of a main pump of hydrodynamic type of a nuclear power plant as claimed in claim 1, wherein the stationary ring assembly includes a stationary ring, a stationary ring insert ring, and a stationary ring retainer ring which are nested from inside to outside;
and the static ring, the static ring embedding ring and the static ring retaining ring are in interference fit.
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| CN202021556896.9U CN212959854U (en) | 2020-07-31 | 2020-07-31 | Follow-up sealing structure of hydrodynamic pressure type main pump mechanical seal of nuclear power station |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111810644A (en) * | 2020-07-31 | 2020-10-23 | 中核核电运行管理有限公司 | Follow-up sealing structure of hydrodynamic pressure type main pump mechanical seal of nuclear power station |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111810644A (en) * | 2020-07-31 | 2020-10-23 | 中核核电运行管理有限公司 | Follow-up sealing structure of hydrodynamic pressure type main pump mechanical seal of nuclear power station |
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