CN106640740B - The Double End fluid dynamic and static pressure mechanical seal of sodium-cooled fast reactor core main pump - Google Patents
The Double End fluid dynamic and static pressure mechanical seal of sodium-cooled fast reactor core main pump Download PDFInfo
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- CN106640740B CN106640740B CN201611047370.6A CN201611047370A CN106640740B CN 106640740 B CN106640740 B CN 106640740B CN 201611047370 A CN201611047370 A CN 201611047370A CN 106640740 B CN106640740 B CN 106640740B
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- 239000012530 fluid Substances 0.000 title claims abstract description 147
- 230000003068 static effect Effects 0.000 title claims abstract description 120
- 238000007789 sealing Methods 0.000 claims abstract description 147
- 238000005452 bending Methods 0.000 claims abstract description 30
- 238000005086 pumping Methods 0.000 claims abstract description 21
- 230000009471 action Effects 0.000 claims abstract description 17
- 102000005393 Sodium-Potassium-Exchanging ATPase Human genes 0.000 claims abstract description 16
- 108010006431 Sodium-Potassium-Exchanging ATPase Proteins 0.000 claims abstract description 16
- XKRFYHLGVUSROY-UHFFFAOYSA-N Argon Chemical compound [Ar] XKRFYHLGVUSROY-UHFFFAOYSA-N 0.000 claims description 50
- 230000000903 blocking effect Effects 0.000 claims description 39
- 229910052786 argon Inorganic materials 0.000 claims description 25
- 239000011148 porous material Substances 0.000 claims description 24
- 239000007788 liquid Substances 0.000 claims description 14
- DGAQECJNVWCQMB-PUAWFVPOSA-M Ilexoside XXIX Chemical compound C[C@@H]1CC[C@@]2(CC[C@@]3(C(=CC[C@H]4[C@]3(CC[C@@H]5[C@@]4(CC[C@@H](C5(C)C)OS(=O)(=O)[O-])C)C)[C@@H]2[C@]1(C)O)C)C(=O)O[C@H]6[C@@H]([C@H]([C@@H]([C@H](O6)CO)O)O)O.[Na+] DGAQECJNVWCQMB-PUAWFVPOSA-M 0.000 claims description 10
- 229910052708 sodium Inorganic materials 0.000 claims description 10
- 239000011734 sodium Substances 0.000 claims description 10
- 230000006835 compression Effects 0.000 claims description 9
- 238000007906 compression Methods 0.000 claims description 9
- 238000000034 method Methods 0.000 claims description 6
- 230000008569 process Effects 0.000 claims description 6
- 230000000149 penetrating effect Effects 0.000 claims description 5
- 230000001681 protective effect Effects 0.000 claims description 5
- 229910052751 metal Inorganic materials 0.000 claims description 3
- 239000002184 metal Substances 0.000 claims description 3
- 230000008859 change Effects 0.000 claims description 2
- 238000005461 lubrication Methods 0.000 abstract description 2
- 230000007774 longterm Effects 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 28
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 10
- 239000010687 lubricating oil Substances 0.000 description 7
- 239000002826 coolant Substances 0.000 description 6
- XLYOFNOQVPJJNP-ZSJDYOACSA-N Heavy water Chemical compound [2H]O[2H] XLYOFNOQVPJJNP-ZSJDYOACSA-N 0.000 description 4
- 230000005484 gravity Effects 0.000 description 4
- 239000002245 particle Substances 0.000 description 4
- 239000007787 solid Substances 0.000 description 4
- 238000009835 boiling Methods 0.000 description 3
- 230000004992 fission Effects 0.000 description 3
- 238000011010 flushing procedure Methods 0.000 description 3
- 239000001307 helium Substances 0.000 description 3
- 229910052734 helium Inorganic materials 0.000 description 3
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 3
- 239000003921 oil Substances 0.000 description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910002804 graphite Inorganic materials 0.000 description 2
- 239000010439 graphite Substances 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 229910052770 Uranium Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001914 filtration Methods 0.000 description 1
- 229910001338 liquidmetal Inorganic materials 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 239000003758 nuclear fuel Substances 0.000 description 1
- 238000004806 packaging method and process Methods 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- JFALSRSLKYAFGM-UHFFFAOYSA-N uranium(0) Chemical compound [U] JFALSRSLKYAFGM-UHFFFAOYSA-N 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
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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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/06—Lubrication
- F04D29/061—Lubrication especially adapted for liquid pumps
-
- 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
- F04D29/58—Cooling; Heating; Diminishing heat transfer
- F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
- F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
-
- 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
- F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
- F04D29/708—Suction grids; Strainers; Dust separation; Cleaning specially for liquid pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention proposes a kind of sodium-cooled fast reactor core main pump Double End fluid dynamic and static pressure mechanical seal, working medium is polluted to solve the problems, such as the leakage of cycle fluid in existing sodium pump and obstruction that may be present leak into pump of fluid lubrication oil, ensures the safety and stability long-term operation of fast reactor.It forms stationary ring, spring, sealing shell from pumped fluid sealing structure etc. by rotating ring, with rotating ring both ends and forms；Rotating ring and the bayonet fittings on axle sleeve, realize and rotating ring circumferential and axial are positioned；Holding screw is arranged on axle sleeve；Limiter is removably disposed between sealing shell or spring base and axle sleeve, to limit the relative axial position of axle sleeve and spring base, changes spring force so that the pressure between rotating ring and two stationary rings is identical；When rotating ring rotates, obstruction fluid that external seal space that rotating ring, sealing shell etc. surround is filled with combines duct by axial-radial under differential pressure action and flows on rotating ring end face in the backward bending type fluid type groove opened, and forms each from pumping circulation.
Description
Technical Field
The invention belongs to the technical field of sealing, and particularly relates to a self-pumping mechanical seal with a fluid dynamic and static pressure effect, which is suitable for sealing between a main pump shell and a pump shaft of a sodium-cooled fast reactor nuclear reactor.
Background
Nuclear power is coming to a new round of high-speed development worldwide. Since the first prototype nuclear power plant was built in the world from the end of the 50 s to the beginning of the 60 s of the 20 th century, the development of nuclear power technology has gone through the first and second generations, and is currently advancing to the third generation and even the fourth generation. The reactors of the nuclear power plant are of various types and can be divided into a light water reactor (including a pressurized water reactor and a boiling water reactor), a heavy water reactor, a graphite gas cooled reactor, a fast breeder reactor and the like. According to the thermodynamic system, the nuclear power station has 3 types, namely a single-loop system, a double-loop system and a three-loop system. In the single loop system, working medium directly enters a steam turbine or a gas turbine from a reactor, such as a boiling water reactor and a high-temperature gas cooled reactor adopting a helium turbine direct circulation mode; in the double-loop system, the heat of the reactor is transferred from a primary loop to a secondary loop working medium through a steam generator to generate steam, and then a steam turbine is pushed to do work, and a pressurized water reactor and a high-temperature gas cooled reactor adopting a steam turbine circulation mode belong to the type; the three-circuit system is more complex, and the main reactor type is a fast breeder reactor. Regardless of the thermodynamic system and the reactor type, the coolant is required to take heat generated by nuclear fission in the reactor core out to cool the reactor core and perform a subsequent power generation process, and the cooling loop is a loop system which is a core system of the reactor of the nuclear power station.
The coolant circulating in the primary loop system of the reactor often has the characteristics of high temperature, high pressure, strong radioactivity and the like, and the leakage of the coolant must be strictly controlled. Because rotating equipment such as a pump/fan/compressor/steam turbine/gas turbine exists in a loop circulating system, in order to solve the problem of coolant sealing brought by the rotating equipment, 2 schemes are generally adopted in engineering: firstly, shaft seal type equipment, namely high-reliability nuclear-grade mechanical seal, is adopted; secondly, the driving motor of the equipment such as the pump is integrally arranged in a loop pressure shell, so that the dynamic seal with leakage risk is converted into a static seal with zero leakage, and an external auxiliary system is greatly simplified, but the technical difficulty is transferred to the equipment or parts such as the motor, the bearing and the like by the scheme. For example, for a pressurized water reactor, a coolant pump (nuclear main pump) motor must adopt a shielding type or a wet stator type, and a main pump bearing must adopt a water-lubricated bearing in all; for a high-temperature gas cooled reactor of steam turbine circulation, oil-free bearings such as electromagnetic bearings are needed for a main shaft bearing of a helium fan. Because the motor and the bearing have high technical difficulty and high manufacturing cost, and the problems of working efficiency and reliability are difficult to solve particularly under the conditions of high power and large size, a loop system applying mechanical seal still occupies a leading position at present.
As a fourth generation reactor, a fast reactor, namely a fast neutron breeder, directly uses fast neutrons generated by fission to initiate nuclear fission chain reaction without using a moderator, and can breed nuclear fuel, fully utilize uranium resources and greatly reduce long-life nuclides in nuclear waste. Fast reactor coolant needs to have the properties of good heat transfer performance and no moderation of neutrons, and is mainly liquid metal and helium at present. The primary loop system of the sodium-cooled fast reactor consists of a reactor core, a main pump (primary sodium pump), a heat exchanger, a main pipeline and other parts. Compared with the mechanical seal of a primary loop main circulating pump of other reactors, the mechanical seal of the sodium-cooled fast reactor nuclear main pump has the advantages of low working condition pressure (571kPa) and low temperature (70 ℃) and is beneficial to realizing the seal. However, the sodium has strong activity and can explode when meeting water or air, so the reliability requirement of the sodium pump sealing is high, the design needs to strictly ensure zero leakage of liquid sodium, and meanwhile, the short-time reliable sealing under the action of earthquake load is also guaranteed so as to lead out heat of the reactor core and the shutdown.
Fig. 1 is a schematic diagram of a primary-loop sodium pump of a sodium-cooled fast reactor prototype reactor (PFBR) (wangyoming, huangweifeng, li forever, nuclear power plant loop with mechanical seal, tribology, 2011,31 (4): 408-416). The upper part of the free liquid level of liquid sodium in the shell of the sodium pump is filled with argon, and a mechanical seal is arranged at a certain height away from the liquid level of the sodium. The design form avoids direct contact between sealing and liquid sodium with the temperature as high as 400-500 ℃, and eliminates a plurality of harsh limitations on materials, structures and the like, so that the conventional mechanical sealing design can be used.
According to the prior art, a sodium pump references the 3 rd-level sealing of a light water reactor (comprising a pressurized water reactor and a boiling water reactor), a heavy water reactor and a graphite gas cooled reactor, namely, the sealing is realized by adopting a double-end mechanical seal blocked by lubricating oil or a dry gas seal blocked by gas. For the double-end mechanical seal blocked by the lubricating oil, the pressure of the blocked lubricating oil is usually kept higher than that of the working medium gas so as to prevent the protective argon from leaking into the blocked fluid, and an oil slinger is arranged on a shaft sleeve at the lower part of the working medium gas side mechanical seal so as to ensure that the blocking lubricating oil with higher pressure can flow into a liquid collecting barrel through the oil slinger and a liquid collecting channel when leaking into a pump cavity and does not pollute sodium liquid. For dry gas seals that employ gas block, the blocking gas pressure is typically maintained above the pressure of the working fluid gas to prevent the leakage of protective argon gas into the blocking gas.
However, with a dry gas seal that is gas-blocked, the auxiliary system is required to provide a clean blocking gas to maintain non-contact operation of the dry gas seal during operation; meanwhile, blocking gas with pressure higher than that of working medium gas can leak into the pump cavity through the gap of the sealing end face, so that blocking gas loss, protection argon pollution and pressure rise are caused. Particularly, after the sealing end face is instantaneously separated under the action of abnormal axial loads such as earthquakes and the like, when a large amount of lubricating oil leaks into the oil slinger, the liquid collecting pore channel cannot flow through in time, and the lubricating oil flows into the pump cavity along the air passage to form sodium liquid pollution, so that the safety of the sodium-cooled fast reactor is seriously threatened.
Disclosure of Invention
The invention aims to provide a double-end-face fluid dynamic static pressure self-pumping mechanical seal for a sodium-cooled fast reactor nuclear main pump, which is used for solving the problems of leakage of a circulating working medium in the conventional sodium pump and pollution of the working medium caused by blocking of possible leakage of fluid lubricating oil into the pump, and ensuring safe and stable long-period operation of the fast reactor.
The technical scheme of the invention is as follows:
a double-end-face fluid dynamic and static pressure mechanical seal for a sodium-cooled fast reactor main pump is arranged between a shell of the sodium pump and a pump shaft 2 and comprises a movable ring 10, an O-shaped ring 9 for the movable ring, static rings 8 and 12, O-shaped rings 7 and 13 for the static rings, springs 6 and 15, spring seats 5 and 14, a seal shell 16, a shaft sleeve 1, an O-shaped ring 17 for the shaft sleeve, a limiter 4, a pin 11, a set screw 3 and the like,
the movable ring 10, the static rings 8 and 12 on the two sides of the movable ring, and the spring seats 5 and 14 are all sleeved on the shaft sleeve 1 in a penetrating manner; the movable ring 10 is hermetically connected with the shaft sleeve 1 by an O-shaped ring 9; the upper end and the lower end of the moving ring 10 are moving ring sealing end faces, each moving ring sealing end face is matched with 1 static ring, and the outer circular faces of the static rings 8 and 12 are in sealing connection with the sealing shell 16 through O-shaped rings 7 and 13; the other end face of the static ring is respectively supported with more than 3 springs, the other ends of the springs act on the spring seats 5 and 14, the spring seats 5 and 14 are connected with the sealing shell, and a certain end face specific pressure is obtained between the sealing end face of the dynamic ring and the end face of the static ring; the movable ring 10 is matched with a pin 11 on the shaft sleeve through a pin hole which is positioned at the lower part of the movable ring and is radially closed and axially opened, so that the circumferential positioning of the movable ring 10 is realized, and the pin 11 is kept in contact with the bottom of the pin hole and the axial positioning of the movable ring 10 is realized at the same time; the set screw 3 arranged on the shaft sleeve is used for fixing the relative position of the shaft sleeve 1 and the pump shaft 2; the limiter 4 is detachably arranged between the seal shell 16 or the spring seats 5 and 14 and the shaft sleeve 1 and is used for limiting the axial relative position of the shaft sleeve 1 and the seal shell 16 or the spring seats 5 and 14 so as to change the elastic force of the springs supporting the two static rings, so that the pressure between the sealing end surfaces at the two ends of the dynamic ring and the two static rings is the same;
the static ring is enclosed into an outer sealing space by the O-shaped rings 7 and 13, the dynamic ring 10 and the sealing shell 16, and a blocking fluid is filled into the outer sealing space;
the sealing end face of the movable ring matched with the static rings 8 and 12 is divided into a groove area and a sealing dam 37, the groove area is distributed on the outer side part of the end face, and the sealing dam 37 is distributed on the inner side part of the end face; more than 3 groups of backward bending type fluid grooves 39 are arranged in the groove area, and sealing end faces between the backward bending type fluid grooves 39 form a sealing weir; the groove areas and the sealing dams 37 on the sealing end surfaces of the movable ring at the upper end and the lower end of the movable ring 10 are symmetrically arranged with the middle section M-M of the movable ring;
the backward bending type fluid type groove 39 comprises a slope groove 32 and a flat groove 33, wherein the slope groove 32 is positioned at the large radius part of the end surface of the moving ring, and the flat groove 33 is positioned at the small radius part of the end surface of the moving ring;
the outlet of the backward bent fluid type groove 39 is positioned at the outer diameter of the sealing end face of the moving ring, the inlet 31 is positioned in the middle of the sealing surface of the moving ring 10, and the inlet 31 of the backward bent fluid type groove 39 is communicated with the outer sealing space through the axial and radial combined pore passage 30 on the moving ring 10;
two side groove walls of the backward bending type fluid groove 39 are provided, one side is a working surface 34, and the other side is a non-working surface 35;
when the moving ring rotates, the blocking fluid in the backward-bent fluid type groove 39 is accelerated into high-speed fluid by the working surface of the backward-bent fluid type groove 39, the high-speed fluid flows along the non-working surface 35 to the outer diameter side of the moving ring 10 under the action of centrifugal force and is pumped into the outer sealing space, a low-pressure area is formed at the inlet 31 of the backward-bent fluid type groove 39, and the blocking fluid in the outer sealing space flows into the backward-bent fluid type groove 39 through the axial and radial combined pore passage 30, communicated with the outer sealing space, on the moving ring 10 under the action of differential pressure, so that primary self-pumping circulation is formed;
the working surface 34 of the backward-bent fluid groove 39 is accelerated to be high-speed blocking fluid, and in the process of being pumped out of the backward-bent fluid groove 39, along with the gradual increase of the flow cross-sectional area of the backward-bent fluid groove 39, the flow speed is reduced, the pressure is increased, and the opening force for separating the movable ring 10 and the static rings 8 and 12 is formed.
The pin 11 contacts with the bottom of the pin hole to realize the axial positioning of the movable ring 10, so that the weight of the movable ring is supported by the pin, the weight of the movable ring cannot be transmitted to the stationary ring at the lower part, and the upper spring supporting the stationary ring at the upper part can have certain compression amount. If no pin is used for axially positioning the movable ring 10, the lower spring for supporting the lower static ring needs to bear the weight of 2 static rings and the weight of one movable ring, and the pressure between the sealing end surfaces at the two ends of the movable ring and the two static rings cannot be the same. In the self-pumping circulation process, on one hand, self-lubrication of mechanical seal is realized; on the other hand, the fluid is blocked in the outer sealing space to continuously circulate between the sealing surfaces, so that the frictional heat between the sealing surfaces is taken away in time, and the self-flushing of the seal is realized; the centrifugal force is used for increasing the power of the fluid flowing to the outer side of the sealing surface of the moving ring 10 and reducing the leakage rate of the fluid flowing to the inner side of the sealing surface of the moving ring 10; in particular, the centrifugal force causes the solid particles-containing choked fluid entering the backward curved fluid groove 39 to separate from the matrix, wherein the dense solid particles acquire a larger centrifugal force and are pumped out with the fluid to be re-delivered into the outer sealing space without entering the sealing dam 37 area, thereby avoiding abrasive wear between the sealing surfaces.
As a further improvement, a working medium cavity is enclosed by the O-shaped ring 17 for the shaft sleeve, the shaft sleeve 1, the static ring 12 at the lower part, the O-shaped ring 13 for the static ring, the moving ring 10, the shell of the sodium pump and the pump shaft 2, the lower part in the working medium cavity is high-temperature metal sodium liquid, and the upper part is protective argon; the blocking fluid in the outer sealing space is also argon, and the pressure of the blocking fluid is not less than the pressure of the argon in the working medium cavity. Because the pressure of the blocking fluid is not less than the pressure of the argon in the working medium cavity, the argon in the working medium cavity cannot enter the outer sealing space through the leakage of the sealing end face between the static ring and the dynamic ring. Even if the dynamic and static rings are separated instantly under the action of earthquake load, the blocking fluid can enter the working medium cavity only by leaking through the sealing end face between the static ring and the dynamic ring, but the blocking fluid is the same as the upper medium in the working medium cavity, so that the influence on the work of the nuclear main pump can not be caused even if the blocking fluid enters the working medium cavity.
As a further improvement, the number and the structure of springs supporting the two static rings are the same, the spring stiffness is K, the structures of the two static rings are the same, the weight is GJ, the compression length △ x2 of the spring supporting the static ring positioned at the lower part of the dynamic ring and the compression length △ x1 of the spring supporting the static ring positioned at the upper part of the dynamic ring meet the requirement that △ x2- △ x1 are 2GJ/K, so that the pressure between the sealing end surfaces at the two ends of the dynamic ring and the two static rings is the same.
When the double-end-face fluid dynamic-static pressure mechanical seal works, a shaft sleeve is fixed on a pump shaft 2 through a set screw 3, and a moving ring is axially and circumferentially positioned on the shaft sleeve through a pin 11, so that the position of the moving ring relative to the pump shaft 2 is fixed.
Because the static ring on the upper part of the rotating ring stretches the spring by the gravity thereof, and the static ring on the lower part of the rotating ring compresses the spring by the gravity thereof, the pressure of the upper static ring and the lower static ring on the sealing end surface of the rotating ring is different under the same spring compression amount, the abrasion loss of 2 sealing pairs (the contact surface of the rotating ring and the static ring) in the working process is different, the sealing service life of the double end surfaces is shortened, and the elasticity (or the compression length) of the upper spring and the lower spring for supporting the upper static ring and the lower static ring is required to be adjusted.
For the movable ring, the pressure Y1 of the upper static ring on the movable ring, the pressure Y2 of the lower static ring on the movable ring, the gravity GD of the movable ring and the supporting force ZD of the pin on the movable ring are received; y1+ GD ═ Y2+ ZD. If the pressure Y1 of the upper static ring to the dynamic ring is equal to the pressure Y2 of the lower static ring to the dynamic ring, the supporting force ZD of the pin to the dynamic ring should be equal to the gravity GD of the dynamic ring.
for the upper stationary ring, Y1 ═ K △ x1+ GJ, and for the lower stationary ring, K △ x1 ═ Y2+ GJ., Y1 ═ Y2, i.e., K △ x1+ GJ ═ K △ x2-GJ, △ x2- △ x1 ═ 2 GJ/K.
The molded lines of the two side groove walls of the backward bending type fluid groove 39 are helical lines.
The spiral lines of the molded lines of the groove walls on the two sides of the backward bending type fluid groove 39 have the same spiral angle.
The spiral angles of the spiral lines of the groove wall molded lines on the two sides of the backward bending type fluid groove 39 are different, and the spiral angle of the working surface 34 is smaller than that of the non-working surface 35.
The spiral lines of the molded lines of the groove walls at the two sides of the backward bending type fluid groove 39 are tangent to the circular hole of the inlet 31.
The cross section of the joint of the axial and radial combined pore passage 30 on the rotating ring 10 and the outer circular surface of the rotating ring 10 is a wedge-shaped opening. In the above double-end-face fluid dynamic-static pressure mechanical seal, the inlet 31 of the backward-bending fluid type groove 39 is communicated with the outer sealing space through the axial and radial combined pore passage 30 on the moving ring 10; when the moving ring rotates, the blocking fluid in the outer sealing space flows into the backward-bent fluid groove 39 through the axial and radial combined pore passage 30 communicated with the outer sealing space on the moving ring 10 under the action of pressure difference, and a one-time self-pumping cycle is formed.
As another technical solution of the present invention, the inlet 31 of the backward-curved fluid-type groove 39 is communicated with a circular ring groove 36 disposed in the middle of the sealing surface of the rotating ring 10 or the stationary ring 8, 12, and the circular ring groove 36 is communicated with the outer sealing space through being located on the rotating ring or the stationary ring; when the moving ring rotates, blocking fluid in the outer sealing space flows into the backward-bending fluid groove 39 through the axial and radial combined pore passage 30 and the circular ring groove 36 which are communicated with the outer sealing space on the static ring under the action of pressure difference, and a primary self-pumping circulation is formed.
The circular ring groove 36 has the functions of collecting self-lubricating and self-flushing media and preventing the non-uniformity of pumped media and the occurrence of cavitation due to untimely fluid replenishment at the inlet 31 of the backward curved fluid groove 39.
The groove areas on the sealing end faces of the movable ring at the upper end and the lower end of the movable ring 10 and the sealing dams 37 are symmetrically arranged with the middle section M-M of the movable ring, so that the structures of 2 sealing pairs (the contact surfaces of the movable ring and the static ring) are the same, the abrasion loss of the two sealing pairs is the same, and the service life is prolonged. The section M-M of the movable ring refers to a cross section which is perpendicular to the axis of the movable ring and divides the movable ring into equal parts in the axial direction.
The invention has the beneficial effects.
The self-pumping fluid dynamic pressure type mechanical seal has the following advantages:
the working medium cavity argon gas self-pumping device has the advantages that the sealing performance is excellent, zero leakage is realized, and the device is suitable for sealing a sodium-cooled fast reactor nuclear main pump, the leakage of argon gas in the working medium cavity is prevented by the O-shaped ring 9 for the movable ring, the O-shaped rings 7 and 13 for the static ring and the O-shaped ring 17 for the shaft sleeve, and the leakage of the sealing end face between the argon gas driven ring and the static ring in the working medium cavity is effectively prevented because the blocking fluid pressure is not less than the pressure of the argon gas in the working medium cavity and the self-pumping circulation of the blocking fluid is performed for one time and.
and when the movable ring rotates, different mass particles generate different centrifugal forces, so that the mechanical seal has the function of automatically removing solid particles, and can avoid abrasive wear of the sealing dam, thereby avoiding the need of providing an additional filtering auxiliary system.
and thirdly, the application range is wide, and the sealing device can be used for sealing gas and liquid.
the unique self-lubricating and self-cooling flushing functions ensure the stability and durability of the sealing work.
and fifthly, blocking fluid in a static state and directly injecting the fluid between the sealing surfaces of the dynamic ring and the static ring, eliminating solid friction between the sealing surfaces of the dynamic ring and the static ring at the moment of starting and rapidly forming a fluid film at the moment of starting.
the invention has a detachable limiter 4, so that the product (the sealing shell 16, the moving ring 10, the static rings 8 and 12, the spring seats 5 and 14, the shaft sleeve 1, the pin 11, the set screw 3 and the like) can be assembled and molded before being installed and used to form a 'packaging' mechanical seal, when being installed, the one is sleeved on the pump shaft in a penetrating way, the spring seat 15 at the lower part is fixed with the shell of the sodium pump, the set screw 3 is screwed on the pump shaft, and then the limiter 4 is detached.
Drawings
Fig. 1 is a schematic diagram of a primary loop sodium pump of a sodium-cooled fast reactor prototype reactor (PFBR).
Fig. 2 is a schematic structural view of an axial section of a self-pumping fluid dynamic pressure type mechanical seal before installation, wherein a backward bending type fluid groove and an axial and radial combined pore passage are formed in a movable ring.
Fig. 3 is a schematic structural view of the cross section of a self-pumping fluid dynamic pressure type mechanical seal with a backward-curved fluid groove and an axial and radial combined pore passage arranged on a moving ring.
Fig. 4 is a schematic structural view of an axial section of a self-pumping hydrodynamic mechanical seal before installation, wherein a backward-bending fluid groove is formed in a moving ring, and an axial and radial combined pore passage is formed in a stationary ring. (the circular ring groove can be opened on the movable ring and also can be opened on the static ring)
Fig. 5 is a schematic structural view of a shaft section of a self-pumping hydrodynamic mechanical seal with a backward-curved fluid groove on a moving ring and an axial-radial combined hole on a stationary ring. (the circular ring groove can be opened on the movable ring and also can be opened on the static ring)
Fig. 6 is a schematic end view of the moving ring with backward-curved fluid grooves and axial and radial combined ducts.
Fig. 7 is a schematic end view of the rotating ring with the backward-curved fluid-type groove and the circular ring groove.
Fig. 8 is a schematic end view of a stationary ring with axially and radially combined ports, which is similar to fig. 7.
Fig. 9 is a schematic end view of the movable ring with the backward-bending fluid-type groove.
Fig. 10 is a schematic end view of a stationary ring with circular ring grooves and axial and radial combined ducts, which is matched with fig. 9.
Wherein,
r1-inner radius of sealing end face between the dynamic ring and the static ring;
r2-the outer radius of the sealing end face where the moving ring and the static ring are mutually attached;
radius of Rp-shaped groove step
Radius of Ro-shaped groove inlet hole
Radius of Rk-groove inlet hole
R3-groove inlet ring groove inner radius
R4-groove inlet ring groove external radius
G-pumping direction of fluid type groove
w-rotation direction of moving ring
The pump comprises a shaft sleeve 1, a pump shaft 2, a set screw 3, a limiter 4, a spring seat 5, a spring 6, a static ring O-shaped ring 7, a static ring 8, a dynamic ring O-shaped ring 9, a dynamic ring 10, a pin 11, a static ring 12, a static ring O-shaped ring 13, a spring seat 14, a spring 15, a sealing shell 16, a shaft sleeve O-shaped ring 17, an axial and radial combined duct 30, an inlet 31, a slope groove 32, a flat groove 33, a working surface 34, a non-working surface 35, a circular ring groove 36, a sealing dam 37, a backward bent fluid groove 39, a mechanical seal 40, a thrust bearing 41, a pump shaft 42, a guide bearing 43, an impeller 44 and a dynamic ring middle section M-M.
Detailed Description
The following describes embodiments of the present invention in detail with reference to the drawings and three examples.
The same construction of the three embodiments will be explained.
Referring to fig. 2 and 3 or fig. 4 and 5, the three embodiments are double-end-face fluid dynamic and static pressure mechanical seals for a sodium-cooled fast reactor nuclear main pump, and are composed of a movable ring 10, an O-shaped ring 9 for the movable ring, stationary rings 8 and 12, O-shaped rings 7 and 13 for the stationary rings, springs 6 and 15, spring seats 5 and 14, a seal housing 16, a shaft sleeve 1, an O-shaped ring 17 for the shaft sleeve, a stopper 4, a pin 11, a set screw 3 and the like.
Specifically, the dynamic ring 10, the static rings 8 and 12 at the two ends of the dynamic ring, and the spring seats 5 and 14 are sleeved on the shaft sleeve 1 in a penetrating way; the movable ring 10 is hermetically connected with the shaft sleeve 1 by an O-shaped ring 9; the upper end and the lower end of the moving ring 10 are moving ring sealing end faces, each moving ring sealing end face is matched with 1 static ring, and the outer circular faces of the static rings 8 and 12 are in sealing connection with the sealing shell 16 through O-shaped rings 7 and 13; more than 3 springs are respectively supported on the other end face of the static ring, the other ends of the springs act on the spring seats 5 and 14, the spring seats 5 and 14 are fixedly connected to the upper part and the lower part of the sealing shell through bolts, and a certain end face specific pressure is obtained between the sealing end face of the dynamic ring and the end face of the static ring; the movable ring 10 is matched with a pin 11 on the shaft sleeve through a pin hole which is positioned at the lower part of the movable ring and is radially closed and axially opened, so that the circumferential positioning of the movable ring 10 is realized, and the pin 11 is kept in contact with the bottom of the pin hole and the axial positioning of the movable ring 10 is realized at the same time; the set screw 3 is arranged on the shaft sleeve.
The two static rings have the same structure, and the weight is GJ. The number of the springs 15 supporting the static ring positioned at the lower part of the dynamic ring is the same as that of the springs 6 supporting the static ring positioned at the upper part of the dynamic ring, the rigidity is K, and the springs are uniformly distributed in the circumferential direction of the static ring.
the limiter 4 is a split limiting ring consisting of two semicircular limiting half rings, the limiting ring is detachably connected with the upper surface of the upper spring seat 5 through a screw, the inner side of the limiting ring extends into a limiting groove formed in the shaft sleeve 1, so that the shaft sleeve 1, the sealing shell 16 and the spring seats 5 and 14 are axially kept at a certain position, and in the position, the compression length △ x2 of the spring 15 and the compression length △ x1 of the spring 6 supporting the upper static ring of the movable ring meet the requirement that △ x2- △ x1 are 2GJ/K, and thus the pressure between the sealing end surfaces at two ends of the movable ring and the two static rings is the same.
The static ring is enclosed by the O-shaped rings 7 and 13, the dynamic ring 10 and the sealing shell 16 to form an external sealing space, and argon serving as blocking fluid is filled in the external sealing space.
Referring to fig. 6, 7 and 9, the sealing end surface of the moving ring, which is matched with the stationary rings 8 and 12, is divided into a groove area and a sealing dam 37, the groove area is distributed on the outer side part of the end surface, and the sealing dam 37 is distributed on the inner side part of the end surface; more than 3 groups of backward bending type fluid grooves 39 are arranged in the groove area, and sealing end faces between the backward bending type fluid grooves 39 form a sealing weir; the groove areas on the sealing end faces of the movable ring at the upper end and the lower end of the movable ring 10 and the sealing dam 37 are symmetrically arranged in a middle section M-M of the movable ring, which is perpendicular to the axis of the movable ring and passes through the middle position of the movable ring.
The backward bending type fluid type groove 39 comprises a slope groove 32 and a flat groove 33, wherein the slope groove 32 is positioned at the large radius part of the end surface of the moving ring, and the flat groove 33 is positioned at the small radius part of the end surface of the moving ring;
the outlet of the backward bent fluid type groove 39 is positioned at the outer diameter of the sealing end face of the moving ring, the inlet 31 is positioned in the middle of the sealing surface of the moving ring 10, and the inlet 31 of the backward bent fluid type groove 39 is communicated with the outer sealing space through the axial and radial combined pore passage 30 on the moving ring 10;
two side groove walls of the backward bending type fluid groove 39 are provided, one side is a working surface 34, and the other side is a non-working surface 35;
when the moving ring rotates, the blocking fluid in the backward-bent fluid type groove 39 is accelerated into high-speed fluid by the working surface of the backward-bent fluid type groove 39, the high-speed fluid flows along the non-working surface 35 to the outer diameter side of the moving ring 10 under the action of centrifugal force and is pumped into the outer sealing space, a low-pressure area is formed at the inlet 31 of the backward-bent fluid type groove 39, and the blocking fluid in the outer sealing space flows into the backward-bent fluid type groove 39 through flow channels such as the axial and radial combined pore channels 30 communicated with the outer sealing space on the moving ring 10 or the static rings 8 and 12 under the action of differential pressure, so that a primary self-pumping circulation is formed;
the working surface 34 of the backward-bent fluid groove 39 is accelerated to be high-speed blocking fluid, and in the process of being pumped out of the backward-bent fluid groove 39, along with the gradual increase of the flow cross-sectional area of the backward-bent fluid groove 39, the flow speed is reduced, the pressure is increased, and the opening force for separating the movable ring 10 and the static rings 8 and 12 is formed.
the double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor main pump is a container type mechanical seal and can be quickly installed on site after being assembled in a factory, when the double-end-face fluid dynamic and static pressure mechanical seal is installed, the shaft sleeve 1 is sleeved on the pump shaft 2 of the sodium pump in a penetrating mode, the lower spring seat 15 is fixed with the shell of the sodium pump in a sealing mode, and the set screw 3 is screwed on the pump shaft.
When in use, the O-shaped ring 17 for the shaft sleeve, the shaft sleeve 1, the static ring 12 at the lower part, the O-shaped ring 13 for the static ring, the moving ring 10, the shell of the sodium pump and the pump shaft 2 enclose a working medium cavity, the lower part in the working medium cavity is high-temperature metal sodium liquid, and the upper part is protective argon; the pressure of the argon in the outer sealing space is not less than that of the argon in the working medium cavity. Because the pressure of the blocking fluid is not less than the pressure of the argon in the working medium cavity, the argon in the working medium cavity cannot enter the outer sealing space through the leakage of the sealing end face between the static ring and the dynamic ring. Even if the dynamic and static rings are separated instantly under the action of earthquake load, the blocking fluid can enter the working medium cavity only by leaking through the sealing end face between the static ring and the dynamic ring, but the blocking fluid is the same as the upper medium in the working medium cavity, so that the influence on the work of the nuclear main pump can not be caused even if the blocking fluid enters the working medium cavity.
The different structures of the embodiments will be described below.
The main differences between the three embodiments are: whether the axial and radial combined pore canal 30 is opened on the moving ring or the static ring, whether a circular ring groove is opened on the moving ring or the static ring. The following are described separately.
Example 1: double-end-face fluid dynamic and static pressure mechanical seal for sodium-cooled fast reactor nuclear main pump with axial and radial combined pore channel on movable ring
Referring to fig. 2, 3 and 6, inlets 31 of backward-bent fluid grooves 39 at the upper end and the lower end of the rotating ring are communicated with the outer sealing space through axial and radial combined ducts 30 formed in the rotating ring 10. When the moving ring rotates, blocking fluid such as argon in the outer sealing space flows into the backward-bending type fluid groove 39 through the axial and radial combined pore passage 30 on the moving ring 10 under the action of pressure difference, and a self-pumping cycle is formed once and again.
Example 2: double-end-face fluid dynamic and static pressure mechanical seal for sodium-cooled fast reactor nuclear main pump with circular ring groove on moving ring and axial and radial combined pore passage on static ring
Referring to fig. 4, 5, 7 and 8, the inlet 31 of the backward-curved fluid groove 39 on the rotating ring is communicated with a circular ring groove 36 arranged in the middle of the sealing surface of the rotating ring 10. One end of the axial and radial combined pore canal 30 opened on the static ring is communicated with the outer sealing space, and the other end is opposite to the circular ring groove 36 in the axial direction.
When the moving ring rotates, blocking fluid such as argon in the outer sealing space flows into the backward-bending type fluid groove 39 through the axial and radial combined pore passage 30 on the static ring and the circular ring groove 36 on the moving ring under the action of pressure difference, and a primary self-pumping circulation is formed.
Example 3: double-end-face fluid dynamic and static pressure mechanical seal for sodium-cooled fast reactor nuclear main pump with circular ring groove and axial and radial combined pore passage on stationary ring
Referring to fig. 9 and 10 (refer to fig. 4 and 5), the inlet 31 of the backward-bent fluid groove 39 on the moving ring is communicated with a circular groove 36 formed in the middle of the sealing surface of the stationary ring, and the circular groove 36 is communicated with the outer sealing space through an axial and radial combined hole passage 30 formed in the stationary ring. When the moving ring rotates, blocking fluid such as argon in the outer sealing space flows into the backward-bending type fluid groove 39 through the axial and radial combined pore passage 30 on the static ring and the circular ring groove 36 on the static ring under the action of pressure difference, and a primary self-pumping circulation is formed.
Claims (9)
1. The utility model provides a two terminal surface fluid dynamic and static pressure mechanical seal for sodium-cooled fast reactor nuclear main pump sets up between casing and pump shaft (2) of sodium pump, by rotating ring (10), O shape circle (9) for the rotating ring, quiet ring (8, 12), O shape circle (7, 13) for the quiet ring, spring (6, 15), spring holder (5, 14), seal housing (16), axle sleeve (1), O shape circle (17) for the axle sleeve, stopper (4), pin (11) and holding screw (3) etc. constitute characterized by:
the movable ring (10) and the static rings (8, 12) and the spring seats (5, 14) on the two sides of the movable ring are sleeved on the shaft sleeve (1) in a penetrating way; the movable ring (10) is hermetically connected with the shaft sleeve (1) by an O-shaped ring (9); the upper end and the lower end of the movable ring (10) are movable ring sealing end faces, each movable ring sealing end face is matched with 1 static ring, and the outer circular faces of the static rings (8 and 12) are hermetically connected with the sealing shell (16) through O-shaped rings (7 and 13); more than 3 springs are respectively supported on the other end face of the static ring, the other ends of the springs act on spring seats (5 and 14), the spring seats (5 and 14) are connected with the sealing shell, and a certain end face specific pressure is obtained between the sealing end face of the movable ring and the end face of the static ring; the movable ring (10) is matched with a pin (11) on the shaft sleeve through a pin hole which is positioned at the lower part of the movable ring and is radially closed and axially opened, so that the circumferential positioning of the movable ring (10) is realized, and the pin (11) is kept in contact with the bottom of the pin hole while the axial positioning of the movable ring (10) is realized; the set screw (3) arranged on the shaft sleeve is used for fixing the relative position of the shaft sleeve (1) and the pump shaft (2); the limiter (4) is detachably arranged between the sealing shell (16) or the spring seats (5 and 14) and the shaft sleeve (1) and is used for limiting the axial relative position of the shaft sleeve (1) and the sealing shell (16) or the spring seats (5 and 14) so as to change the elastic force of the springs supporting the two static rings, so that the pressure between the sealing end surfaces at the two ends of the movable ring and the pressure between the two static rings are the same;
the static ring is enclosed into an outer sealing space by the O-shaped rings (7, 13), the dynamic ring (10) and the sealing shell (16), and a blocking fluid is filled into the outer sealing space;
the sealing end face of the movable ring matched with the static rings (8 and 12) is divided into a groove area and a sealing dam (37), the groove area is distributed on the outer side part of the end face, and the sealing dam (37) is distributed on the inner side part of the end face; more than 3 groups of backward bending type fluid grooves (39) are arranged in the groove area, and sealing end faces between the backward bending type fluid grooves (39) form a sealing weir; the groove areas on the sealing end surfaces of the movable ring at the upper end and the lower end of the movable ring (10) and the sealing dam (37) are symmetrically arranged by the middle section (M-M) of the movable ring;
the backward bending type fluid type groove (39) comprises a slope groove (32) and a flat groove (33), the slope groove (32) is positioned at the large radius part of the end surface of the moving ring, and the flat groove (33) is positioned at the small radius part of the end surface of the moving ring;
the outlet of the backward bent fluid type groove (39) is positioned at the outer diameter of the sealing end face of the moving ring, the inlet (31) is positioned in the middle of the sealing surface of the moving ring (10), and the inlet (31) of the backward bent fluid type groove (39) is communicated with the outer sealing space through an axial and radial combined pore passage (30) on the moving ring (10);
two side groove walls of the backward bending type fluid type groove (39), one side is a working surface (34), and the other side is a non-working surface (35);
when the moving ring rotates, the blocking fluid in the backward-bent fluid type groove (39) is accelerated into high-speed fluid by the working surface of the backward-bent fluid type groove (39), flows to the outer diameter side of the moving ring (10) along the non-working surface (35) under the action of centrifugal force and is pumped into the outer sealing space, a low-pressure area is formed at the inlet (31) of the backward-bent fluid type groove (39), and the blocking fluid in the outer sealing space flows into the backward-bent fluid type groove (39) through an axial and radial combined pore passage (30) which is arranged on the moving ring (10) and is communicated with the outer sealing space under the action of differential pressure, so that a primary self-pumping circulation is formed;
the working surface (34) accelerated by the backward-bent fluid groove (39) is high-speed blocked fluid, and in the process of being pumped out of the backward-bent fluid groove (39), along with the gradual increase of the flow cross section area of the backward-bent fluid groove (39), the flow speed is reduced, the pressure is increased, and the opening force for separating the movable ring (10) and the static rings (8 and 12) is formed.
2. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 1, which is characterized in that: the shaft sleeve is provided with an O-shaped ring (17), the shaft sleeve (1), a static ring (12) at the lower part and a working medium cavity enclosed by the O-shaped ring (13), a moving ring (10), a shell of the sodium pump and a pump shaft (2) for the static ring, the lower part in the working medium cavity is high-temperature metal sodium liquid, and the upper part in the working medium cavity is protective argon; the blocking fluid in the outer sealing space is also argon, and the pressure of the blocking fluid is not less than the pressure of the argon in the working medium cavity.
3. the double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump is characterized in that the number and the structure of springs supporting two static rings are the same, the spring stiffness is K, the structures of the two static rings are the same, the weight is GJ, the compression length △ x2 of the spring supporting the static ring positioned at the lower part of the dynamic ring and the compression length △ x1 of the spring supporting the static ring positioned at the upper part of the dynamic ring meet the requirement that △ x2- △ x1 is 2GJ/K, so that the pressure between the sealing end faces at the two ends of the dynamic ring and the two static rings is the same.
4. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 1, which is characterized in that: the molded lines of the groove walls on the two sides of the backward bending type fluid groove (39) are helical lines.
5. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 4, which is characterized in that: the spiral lines of the molded lines of the groove walls on the two sides of the backward bending type fluid groove (39) have the same spiral angle.
6. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 4, which is characterized in that: the spiral angles of the spiral lines of the groove wall molded lines on the two sides of the backward bending type fluid groove (39) are different, and the spiral angle of the working surface (34) is smaller than that of the non-working surface (35).
7. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 4, which is characterized in that: the spiral lines of the molded lines of the groove walls at the two sides of the backward bending type fluid groove (39) are tangent to the round hole of the inlet (31).
8. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 5, which is characterized in that: the cross section of the joint of the axial and radial combined pore canal (30) on the moving ring (10) and the outer circular surface of the moving ring (10) is a wedge-shaped opening (38).
9. The double-end-face fluid dynamic and static pressure mechanical seal for the sodium-cooled fast reactor nuclear main pump as claimed in claim 1, which is characterized in that: an inlet (31) of the backward bending type fluid groove (39) is communicated with a circular ring groove (36) arranged in the middle of the sealing surface of the moving ring (10) or the static rings (8, 12), and the circular ring groove (36) is at least communicated with the outer sealing space through the circular ring groove positioned on the static ring; when the rotating ring rotates, blocking fluid in the outer sealing space flows into the backward-bent fluid groove (39) through the axial and radial combined pore canal (30) and the circular ring groove (36) which are arranged on the static ring and communicated with the outer sealing space under the action of pressure difference, and a primary and secondary self-pumping circulation is formed.
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| CN201611047370.6A CN106640740B (en) | 2016-11-22 | 2016-11-22 | The Double End fluid dynamic and static pressure mechanical seal of sodium-cooled fast reactor core main pump |
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| CN110005817A (en) * | 2019-03-15 | 2019-07-12 | 中广核工程有限公司 | A kind of containment heat derives mechanical seal for pump and auxiliary system devices |
| CN111706405B (en) * | 2020-05-12 | 2021-11-30 | 中国核动力研究设计院 | Dry gas sealing self-cooling structure and method |
| CN112096873B (en) * | 2020-07-31 | 2024-08-09 | 中核核电运行管理有限公司 | Floating sealing device for mechanical seal of hydrodynamic pressure type main pump of nuclear power station |
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