CN102162529A - Spiral seal structure in dynamic and static gaps of rotary machine - Google Patents
Spiral seal structure in dynamic and static gaps of rotary machine Download PDFInfo
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- CN102162529A CN102162529A CN2011100915543A CN201110091554A CN102162529A CN 102162529 A CN102162529 A CN 102162529A CN 2011100915543 A CN2011100915543 A CN 2011100915543A CN 201110091554 A CN201110091554 A CN 201110091554A CN 102162529 A CN102162529 A CN 102162529A
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- 230000003068 static effect Effects 0.000 title claims abstract description 21
- 238000007789 sealing Methods 0.000 claims description 22
- 230000009194 climbing Effects 0.000 claims description 2
- 239000012530 fluid Substances 0.000 abstract description 24
- 230000000694 effects Effects 0.000 abstract description 9
- 230000002093 peripheral effect Effects 0.000 abstract 1
- 238000005086 pumping Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 4
- 230000008676 import Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
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- 238000006243 chemical reaction Methods 0.000 description 1
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Abstract
The invention relates to a spiral seal structure arranged in the dynamic and static gaps of a rotary machine, wherein a seal ring is installed on the static component of the rotary machine; spiral seal teeth are arranged on the inner surface of the seal ring; the seal teeth surround and climb on the inner surface of the seal ring according to the peripheral direction opposite to the rotation direction of a rotor; the windward, leeward and top surface of the seal teeth adopt concave curved surfaces; and the front and rear edges at the top of the seal teeth form two sharp angle ends. The spiral seal structure provided by the invention is used for controlling a high-temperature and high-pressure fluid to leak along the dynamic and static gaps and avoids the large-flow leakage from influencing the stable operation and safe operation of the next stage of components. The spiral seal structure provided by the invention is used under the working medium conditions of high pressure, high temperature, high speed and large flow of a nuclear main pump, can temporarily and stably control the leakage quantity under the extreme working medium condition of backflow, is safe and durable and has the advantage of good throttling effect.
Description
Technical field
The application belongs to the non-contact technical field of sealing technology, relates to a kind of spiral seal structure that is used for dynamic and static gaps of rotating machine.
Background technique
The non-contact sealing technique is applied to control the rotary component of rotating machinery and the dielectric leakage of static part.For guaranteeing the safe and stable operation of rotating machinery, rotary component and static part should keep enough gaps, therefore select non-contact sealing control gap leakage flow.For compressible fluid, sealing medium is through the spiral seal tip clearance, and throttling is quickened, and in the sealed chamber behind the spiral seal tooth, the kinetic energy of fluid is converted into heat energy, and working medium is through Seal cage, and pressure reduces gradually, with the control escape of liquid.
The normal little clearance seal of level and smooth dynamic and static ring that adopts of pump dynamic and static gaps between impeller outlet and stator dynamic and static gaps and impeller eye wheel cap place and import honeycomb duct, the dissipation effect of this kind sealed inside medium is not obvious, the control leakage effect is poor, and the spiral seal groove of the application's sealing configuration produces the pumping pressure head to the sealing inner fluid, the pumping pressure head is opposite with sealed medium pressure, stops the leakage of sealing medium; By the spiral seal toothing is set, to increase the complexity of media flow passage, strengthening fluid kinetic energy is to the heat energy conversion process, with the control leakage rate; The more important thing is that the clearance seal of pump especially examines the clearance seal of main pump, should consider this extreme operating condition that flows backwards, the structural design of refluence is not controlled in most sealing, and the application's sealing configuration is the interior reverse leakage flow of control pump effectively.
Summary of the invention
The technical problem that the application will solve provides a kind of spiral seal structure that is used for dynamic and static gaps of rotating machine, can effectively control the leakage of incompressible fluid, guarantee stable operation under the working medium of big flow, even under the refluence extreme operating condition, also can keep the stable of leakage rate, long service life.
The technological scheme that the application adopts is:
A kind of spiral seal structure that is used for dynamic and static gaps of rotating machine is equipped with seal ring on the rotating machinery static part, and the seal ring internal surface is provided with the spiral seal tooth, the spiral seal tooth by the opposite direction circumferencial direction of rotor rotation around climbing in the seal ring internal surface; Spiral seal tooth windward side, lee face and end face all adopt concave curved surface, and spiral seal tooth top front and rear edge forms two closed angle ends.
The helix angle of spiral seal tooth can be 5 °～45 ° angles, and the seal groove Elongation between the spiral seal tooth can be 0.5～2.
Because the viscous force effect of medium, the rotor rotation drives the fluid rotation, and working medium enters the spiral seal groove, forms with leakage flow is rightabout to flow, and the pressure head of this part fluid has reduced the pressure head of leakage flow, has hindered flowing of leakage flow.
The helix structure of sealing can stop the leakage rate of two direction incoming flows, under the extreme operating condition that flows backwards, if impeller counter-rotating, it is the rotary component counter-rotating, form retrograde fluid and suppress leakage flow, along with the change of rotating speed is big, this resistance can be all the more obvious, and rationally being provided with of lead angle and spiral seal tooth axial distance and helix structure length is beneficial to gain leakage flow resistance.
Leakage flow flows into helical trajectory in the spiral seal groove, leakage flow circumferential speed component is big, this has just increased the waiting time of leakage flow in Seal cage, the leakage flow flow path is longer than common labyrinth seal, thereby increased linear loss, working medium produces more multipotency dissipation in helical flow, kinetic energy is converted into heat energy, and pressure reduces gradually.
Spiral seal tooth leading edge wedge angle can produce tangible throttle effect, in spiral seal tooth top concave curved surface, form high velocity turbulent flow, this fluid through the trailing edge wedge angle once more by throttling, form than the higher tubulence energy fluid of conventional seals through twice throttling, energy dissipation in entering chamber, more kinetic energy are converted into heat energy, consume more multiple pressure power energy.
The concave surface of spiral seal tooth top forms the resistance of little whirlpool leakage flow axial flow; Fluid was up along the tooth wall before the concave curved surface of windward side helped drawing the part tooth, introduced stagnation region or upper strata chamber, made it stop more time before tooth or in the tooth cavity, to reduce leakage.
Sealed chamber facings the wind and helps the formation of the circumferential helical flow form of leakage flow with leeward concave surface, helps energy dissipation, reduces the leakage flow pressure head.
The pumping pressure head of the many more spiral seals of spiral number of rings of spiral seal tooth is big more, and the pumping effect is obvious more, more helps controlling leakage flow.
The spiral seal tooth of sealing configuration rationally is provided with spiral seal tooth Elongation under the condition of limited of space, to adapt to high pressure, high-velocity fluid, prevent the fracture of spiral seal tooth tooth root, increases its working life, prolongs the repair cycle, guarantees Security.
The application's beneficial effect is as follows:
(1) the application's sealing configuration has good control leakage effect.The noncontact seal leakage rate depends on the size of seal clearance to a great extent, and under the prerequisite that guarantees equipment safety operation, seal clearance can be set to minimum.The impeller rotary component drives the part medium along the reverse flow of spiral seal chamber, produces and the rightabout pumping pressure head of leakage flow, stops leakage flow.This kind form control incompressible fluid leakage ability is better than relying on the labyrinth seal of dissipation of vorticity kinetic energy.Through the sealing of numerical simulation study incompressible medium, the application's sealing reduces 25% leakage rate than the common straight-tooth sealing in identical gap.
(2) the two wedge angle throttling meetings of spiral seal tooth produce tangible throttle effect, form than the higher tubulence energy fluid of conventional seals, and energy dissipation in entering chamber, more kinetic energy are converted into heat energy, consume more multiple pressure power energy.Chamber structure is should not be too complicated, and fluid needs the dissipation space of big volume, is converted into heat energy with the form kinetic energy of vortex.Consider manufacture difficulty and processing cost, the application's simplicity of design makes fluid have enough dimensional energy to dissipate.
(3) leakage flow flows into helical trajectory in the spiral seal groove, leakage flow circumferential speed component is big, and this has just increased the waiting time of leakage flow in Seal cage, thereby has increased linear loss, working medium produces more multipotency dissipation in helical flow, pressure reduces gradually.
(4) the application's spiral seal toothing can stop the leakage rate of two direction incoming flows, and under the extreme operating condition that flows backwards, if the impeller counter-rotating, i.e. rotary component counter-rotating forms retrograde fluid and suppresses leakage flow, has played the effect of stable refluence leakage flow.
(5) fluid was up along the tooth wall before the part tooth was drawn in the arc windward side, introduced stagnation region or upper strata chamber, made medium stop more time before tooth or in the tooth cavity, to reduce leakage.
(6) in order to adapt to high pressure, high-velocity fluid, the application adopts the method for reinforcing tooth root, prevents the fracture of spiral seal tooth tooth root, increases working life, prolongs the repair cycle, guarantees Security.
(7) through numerical simulation, under 17～18Mpa hydraulic pressure operating mode, cavitation phenomenon does not take place in the inner minimum pressure above bubble point pressure of the application's Seal cage in the sealed chamber.
Description of drawings
Fig. 1 (a) is that the application seals the three-dimensional structure schematic representation.
Fig. 1 (b) is the application's spiral seal toothing two-dimensional representation.
Fig. 2 is the seal ring overall schematic.
Among the figure: 1 seal ring; 2 spiral seal teeth; 3 seal grooves.
Embodiment
Is that embodiment is described in detail the application below in conjunction with technological scheme with the nuclear main pump.
The application's sealing is made up of two semicircle seal rings, can be installed in impeller outlet and stator dynamic and static gaps and the impeller eye wheel cap place and the import honeycomb duct dynamic and static gaps place of nuclear main pump, perhaps is installed on the gap location of heat shielding and rotating shaft.Seal ring back of the body arc is installed along the conduit of fixed component, and circumferential hoop winds in the direction opposite the rotor sense of rotation.The application's sealing configuration mainly is made up of seal ring 1, spiral seal tooth 2.
The seal ring inner ring can be provided with many ring spiral seal teeth, and is shown in Figure 1, is provided with 6 ring spiral seal teeth, forms sealed chamber between the spiral seal tooth.
Fluid quickens through sealing two pointed tooth throttlings, and pressure reduces, and high-velocity fluid kinetic energy in sealed cavity changes into heat energy, and this pressure can not return to the force value of upper level, so hydrodynamic pressure reduces step by step, the escape of liquid amount reduces.The impeller rotary component drives the part medium along the reverse flow of spiral seal chamber, and spiral chute produces the pumping pressure head to the fluid that is filled in seal clearance, and this pumping pressure head is opposite with sealed pressure medium, stops the leakage of sealing medium.
There is dynamic and static gaps in the outlet of nuclear main pump impeller with the stator place, between impeller eye wheel cap place and import honeycomb duct, also there is dynamic and static gaps, when the nuclear main pump normally moves, there is part to leak along this gap through the high-pressure liquid of impeller outlet, and be back to pump intake again, disturb the main flow field flow moving, reduce effective flow area simultaneously, reduced the flow efficiency and the performance of pump; Have the gap between heat shielding and the rotating shaft, high-temperature, high pressure fluid leaks along this gap, and subordinate's parts are subject to its influence, causes fluctuation of service even damage.In order to ensure each the parts safe operation of nuclear main pump, should reduce these leakages as far as possible, the application's sealing structure is arranged on above-mentioned dynamic and static gaps place.
Claims (3)
1. the spiral seal structure of a dynamic and static gaps of rotating machine, it is characterized in that, seal ring (1) is housed on the rotating machinery static part, and its internal surface is provided with spiral seal tooth (2), spiral seal tooth (2) by the opposite direction circumferencial direction of rotor rotation around climbing in the seal ring internal surface; Spiral seal tooth (2) windward side, lee face and end face all adopt concave curved surface, and spiral seal tooth (2) top front and rear edge forms two closed angle ends.
2. sealing configuration according to claim 1 is characterized in that, the helix angle of spiral seal tooth (2) becomes 5 °～45 °.
3. sealing configuration according to claim 1 is characterized in that, seal groove (3) Elongation between the described spiral seal tooth (2) is 0.5～2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011100915543A CN102162529A (en) | 2011-04-13 | 2011-04-13 | Spiral seal structure in dynamic and static gaps of rotary machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011100915543A CN102162529A (en) | 2011-04-13 | 2011-04-13 | Spiral seal structure in dynamic and static gaps of rotary machine |
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| CN102162529A true CN102162529A (en) | 2011-08-24 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2011100915543A Pending CN102162529A (en) | 2011-04-13 | 2011-04-13 | Spiral seal structure in dynamic and static gaps of rotary machine |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111720175A (en) * | 2020-06-23 | 2020-09-29 | 中国科学院工程热物理研究所 | Impeller machinery movable vane top seal structure |
| CN112196824A (en) * | 2020-08-25 | 2021-01-08 | 江苏大学 | Labyrinth seal for staggered spiral tooth structure of centrifugal pump |
| CN112984114A (en) * | 2021-02-04 | 2021-06-18 | 同济大学 | Low-temperature medium rotary sealing device of superconducting machinery of hollow shaft parts |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10153186A (en) * | 1996-11-25 | 1998-06-09 | Hitachi Ltd | Scroll compressor |
| US20070069477A1 (en) * | 2003-06-20 | 2007-03-29 | Elliott Company | Stepped labyrinth damper seal |
| CN201554501U (en) * | 2009-10-30 | 2010-08-18 | 华北电力大学（保定） | Non-contact type steam turbine steam seal structure |
| CN101832392A (en) * | 2010-05-19 | 2010-09-15 | 大连理工大学 | Sealing structure for dynamic and static gaps of rotating machine |
| CN202125612U (en) * | 2011-04-13 | 2012-01-25 | 大连理工大学 | Spiral sealing structure for rotary mechanical movable and static clearances |
-
2011
- 2011-04-13 CN CN2011100915543A patent/CN102162529A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10153186A (en) * | 1996-11-25 | 1998-06-09 | Hitachi Ltd | Scroll compressor |
| US20070069477A1 (en) * | 2003-06-20 | 2007-03-29 | Elliott Company | Stepped labyrinth damper seal |
| CN201554501U (en) * | 2009-10-30 | 2010-08-18 | 华北电力大学（保定） | Non-contact type steam turbine steam seal structure |
| CN101832392A (en) * | 2010-05-19 | 2010-09-15 | 大连理工大学 | Sealing structure for dynamic and static gaps of rotating machine |
| CN202125612U (en) * | 2011-04-13 | 2012-01-25 | 大连理工大学 | Spiral sealing structure for rotary mechanical movable and static clearances |
Non-Patent Citations (1)
| Title |
|---|
| 张家杰: "DG480-180型调速给水泵改装螺旋密封", 《华东电力》 * |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111720175A (en) * | 2020-06-23 | 2020-09-29 | 中国科学院工程热物理研究所 | Impeller machinery movable vane top seal structure |
| CN111720175B (en) * | 2020-06-23 | 2022-04-19 | 中国科学院工程热物理研究所 | Impeller machinery movable vane top seal structure |
| CN112196824A (en) * | 2020-08-25 | 2021-01-08 | 江苏大学 | Labyrinth seal for staggered spiral tooth structure of centrifugal pump |
| CN112984114A (en) * | 2021-02-04 | 2021-06-18 | 同济大学 | Low-temperature medium rotary sealing device of superconducting machinery of hollow shaft parts |
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Application publication date: 20110824 |