CN204739222U - Gas lubrication helicla flute terminal surface mechanical seal structure tied in a bundle - Google Patents
Gas lubrication helicla flute terminal surface mechanical seal structure tied in a bundle Download PDFInfo
- Publication number
- CN204739222U CN204739222U CN201520342928.8U CN201520342928U CN204739222U CN 204739222 U CN204739222 U CN 204739222U CN 201520342928 U CN201520342928 U CN 201520342928U CN 204739222 U CN204739222 U CN 204739222U
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- China
- Prior art keywords
- spiral
- microminiature
- boundling
- spiral chute
- terminal surface
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- 238000005461 lubrication Methods 0.000 title claims abstract description 7
- 238000007789 sealing Methods 0.000 claims abstract description 26
- 238000011144 upstream manufacturing Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 10
- 230000000694 effects Effects 0.000 abstract description 6
- 230000006835 compression Effects 0.000 abstract description 5
- 238000007906 compression Methods 0.000 abstract description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract 1
- 238000000034 method Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
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- Mechanical Sealing (AREA)
Abstract
The utility model provides a gas lubrication helicla flute terminal surface mechanical seal structure tied in a bundle, it includes mechanical seal's rotating ring and quiet ring, one side of rotating ring and quiet ring terminal surface is the upper reaches for the high -pressure side, the opposite side of rotating ring and quiet ring terminal surface is low reaches for the low tension side, be equipped with a plurality of helicla flutes tied in a bundle along terminal surface circumference symmetric distribution in rotating ring or the quiet ring on the terminal surface of at least one sealing ring, helicla flute tied in a bundle is formed along the combination of terminal surface circumference by the unequal microminiature helicla flute of a plurality of helical angles, and each the microminiature helicla flute that is arranged in same tied in a bundle helicla flute cuts off by not grooved sealed weir at the high -pressure side, its groove root of low tension side superpose each other link up as an organic whole, the low reaches of helicla flute tied in a bundle are equipped with sealed dam. Through the convergence configuration of bionical high -speed flying bird wing and the alula structure of flying bird wing leading edge, the utility model discloses have strong water conservancy diversion effect and compression to fluid medium, can improve sealed low -speed and open and stop characteristic, high -speed operating stability and leakproofness, improved sealed high -speed anti -interference kinetic energy power, prevent the end wear.
Description
Technical field:
The utility model relates to a kind of gas end surface mechanical sealing structure of rotary type fluid machine, in particular to a kind of gas lubrication boundling spiral groove end face mechanical sealing structure, can be used for the shaft end seal of the rotating machineries such as various centrifugal compressor, decompressor, pump, reactor.
Background technique:
Dry gas seals is widely applied, as centrifugal compressor, decompressor, blower fan etc. with the superiority of its uniqueness on various high speed rotating machinery.Dry gas seals is by offering various fluid sound die mould groove on seal face, when rotating ring rotates, utilize the active and static pressure effect of type groove that gas medium is pumped into seal face, therefore the flowing medium entering end face produces certain opening force in type groove root constricted flow and pushes end face open, thus the non-contact realizing dynamic and static ring runs, wherein current most popular face type groove is spiral chute.The report of spiral chute and derivative type groove gas face seals thereof has a lot, as Chinese patent 20154747236U and 96216242.6, European patent EP 0470406A1, EP0564153A1 etc., particularly double helix angle three-dimensional spiral groove end face seal, its fluid film rigidity and reliability are with the obvious advantage compared to the two-dimensional helical groove end face seal that is dark, equal helix angle such as common.But, it is not good that these spiral chutes and derivative type groove dry gas seals thereof still also exist low speed start and stop characteristic, during high speed operation, gas film stiffness is large not, the deficiencies such as leak-down rate exceeds standard, cause dry gas seals on high-speed rotating machine, in using process, occur being difficult to quick unlatching, high speed operation stability and sealing not good, seal face easily produces the problems such as contact wear, is difficult to meet the service condition of mechanical seal under the contour Parameter Conditions of high speed.
Summary of the invention:
In order to overcome above shortcomings in dry gas seals prior art, the utility model uses for reference the convergence configuration of high-speed flight birds wing and the excellent specific property of pinion leading edge alula structure, provides a kind of at low-voltage high speed or high-voltage high-speed operating mode lower end surface hydrodynamic effect is strong, gas film stiffness is large, sealing is good and low speed start and stop characteristic good boundling spiral groove end face mechanical sealing structure.
The technical solution of the utility model is:
A kind of gas lubrication boundling spiral groove end face mechanical sealing structure, it comprises rotating ring and the stationary ring of mechanical seal, the side of described rotating ring and stationary ring end face is high pressure side and upstream, the opposite side of described rotating ring and stationary ring end face is low voltage side and downstream, in described rotating ring or stationary ring, the end face of at least one seal ring is provided with multiple boundling spiral chute symmetrical along end face circumference, the microminiature spiral chute that described boundling spiral chute is not waited by multiple helix angle combines along end face circumference, and each microminiature spiral chute being arranged in same boundling spiral chute is cut off by the sealing weir of not slotting in high pressure side, through being integrated mutually is superposed at its groove root of low voltage side, described boundling spiral fluted downstream is provided with sealing dam.
Further, microminiature spiral fluted number N in described same boundling spiral chute
wchoosing value scope be: 2≤N
w≤ 20, preferred value scope is 3≤N
w≤ 8;
In described boundling spiral chute, single microminiature spiral chute is at external diameter r
othe circular arc angle theta at place
1sealing weir between two microminiature spiral chutes adjacent with same boundling spiral chute mesohigh side is at external diameter r
othe circular arc angle theta at place
2ratio θ
1/ θ
2choosing value scope be θ
1/ θ
2=0.1 ~ 1.0, preferred value scope is θ
1/ θ
2=0.3 ~ 0.6;
In described same boundling spiral chute, each microminiature spiral fluted helix angle reduces gradually along rotary speed direction, namely meets β
n< β
i(1<i<N
w) < β
1, wherein β
1for suitable rotary speed direction first microminiature spiral fluted helix angle, β
nfor suitable last microminiature spiral fluted helix angle of rotary speed direction, β
ifor centre any microminiature spiral fluted helix angle;
The radial groove width l of described boundling spiral fluted
1=(r
o-r
g) with the radial width l on downstream seal dam
2=(r
g-r
i) ratio l
1/ l
2choosing value scope be l
1/ l
2=0.2 ~ 4, preferred value scope is l
1/ l
2=0.5 ~ 1.5;
Described boundling spiral fluted groove depth choosing value scope is 0.1 ~ 30 μm, and preferred value scope is 2 ~ 10 μm, and in described same boundling spiral chute, each microminiature spiral chute shoals against rotary speed direction gradually in the degree of depth at same radius place.Working principle of the present utility model is:
Use for reference the convergence configuration being applicable to high-speed flight birds (as swift, frigate bird etc.) wing, imitate the wing configuration design face type channel profiles of this type of bird; Use for reference the alula structure of flying bird wing leading edge, imitate the structure of alula structural design type groove entrance.The wing leading edge that occurring in nature is applicable to high-speed flight birds has alula structure, one or multi-channel slot is defined between alula and top airfoil, it has good guide functions to wing front incoming flow, air-flow can be made to pass through top airfoil smoothly, there is suitable vent flow, weaken the effect of eddy current, effectively ensure that the stability of lift in Bird Flight process and high-speed flight; The wing being applicable to high-speed flight birds is generally convergence configuration, and this convergence configuration can weaken the tip vortex of flying bird in high-speed flight, keeps flight stability.When face type groove is the operation of boundling Spiral Groove Dry Gas Seals by Use, type groove entrance is divided into multiple drainage channel by the sealing weir being similar to pinion leading edge alula structure, its fluid medium has good guide functions, and air flow energy enters seal face equably from multiple drainage spiral chute, the type groove fluid medium of convergence configuration has stronger compression, conflux at groove root place superposition and groove depth against rotary speed direction microminiature spiral chute race of flowing medium in each drainage spiral chute shoals gradually, these structure characteristics all further enhance the compression of fluid medium, each microminiature spiral chute race can be made to act synergistically by optimal design, fluid medium produces stronger pinch effect and pump draws effect, therefore under identical air-film thickness, there is large opening force and gas film stiffness, when rotating machinery start and stop, there is excellent opening feature, there is when rotating machinery runs up the ability of stronger opposing high speed disturbance.
Advantage of the present utility model and beneficial effect:
(1) compared with the general two-dimensional helical groove end face seal waiting dark, equal helix angle, the convergence type groove that the helix that macroscopical configuration is not waited by two helix angles in the utility model forms has stronger convergence property, and the groove depth of each microminiature spiral chute race also can be shoal gradually against rotary speed direction, stronger compression can be produced to fluid-encapsulated medium, therefore larger opening force and gas film stiffness can be produced under identical thickness condition, operation stability when being conducive to the start and stop characteristic of raising low-speed conditions lower seal and running up.
(2) type groove entrance is separated into the structure with the drainage of multiple microminiature spiral chute by the sealing weir being similar to pinion leading edge alula structure, multiple elongated spiral chute flow guiding structure can make flowing medium evenly enter seal face, fluid medium has stronger guide functions, the generation of eddy current in face type groove when seal ring runs up can be weakened, thus be conducive to the stability strengthening sealing high speed operation; Flowing medium in multiple drainage spiral chute converges extruding at groove root place, enhances the compression of fluid medium, and make the bearing capacity of seal face and gas film stiffness larger, end face is easy to open at low speeds, and Ability of Resisting Disturbance is strong when high speed operation.
(3) the utility model uses for reference the convergence configuration of high-speed flight birds wing and the alula structure of pinion leading edge, by sealing the circumferential width etc. on weir between the change type groove macroscopic view degree of convergence of configuration and microminiature spiral chute race, the stable operation under different working condition of boundling spiral chute can be realized, be namely applicable to wider operating range.
Accompanying drawing illustrates:
Fig. 1 is the fluting end view of the utility model case study on implementation one;
Fig. 2 is the fluting end face geometrical structure parameter unified definition schematic diagram of the utility model case study on implementation one;
Fig. 3 is the fluting end view that the circumferential ladder of the utility model case study on implementation two deepens type groove;
Fig. 4 is along the boundling spiral chute bottom land cross section structural representation along the circumferential direction that 1-1 line in accompanying drawing 3 is got in the utility model case study on implementation two;
Fig. 5 is the fluting end view of the utility model case study on implementation three;
Fig. 6 is the fluting end view of the utility model case study on implementation four;
Fig. 7 is the fluting end view of the through annular groove of downstream belt circumference of the utility model case study on implementation five.
Embodiment
By reference to the accompanying drawings enforcement of the present utility model is described in further detail.
Embodiment one
See Fig. 1, 2, a kind of gas lubrication boundling screw groove end face sealing structure, it comprises rotating ring and the stationary ring of mechanical seal, it is characterized in that: the side of described rotating ring and stationary ring end face is high pressure side and upstream, the opposite side of described rotating ring and stationary ring end face is low voltage side and downstream, in described rotating ring or stationary ring, the end face of at least one seal ring is provided with multiple boundling spiral chute symmetrical along end face circumference, the microminiature spiral chute 1 that described boundling spiral chute is not waited by multiple helix angle, 2 and 3 combine along end face circumference, described each microminiature spiral chute 1, 2 and 3 are cut off by the sealing weir 4 and 5 of not slotting in high pressure side, through being integrated mutually is superposed at its groove root of low voltage side, described boundling spiral fluted downstream is provided with sealing dam 6.
The number N of microminiature spiral chute 1,2 and 3 in described same boundling spiral chute
w=3, preferred value scope is 3≤N
w≤ 8.
In described boundling spiral chute, single microminiature spiral chute 1,2 and 3 is at external diameter r
othe circular arc angle theta at place
1two microminiature spiral chutes 1 and 2 adjacent with same boundling spiral chute mesohigh side, or the sealing weir between 2 and 3 is at external diameter r
othe circular arc angle theta at place
2ratio θ
1/ θ
2choosing value scope be θ
1/ θ
2=0.1 ~ 1.0, preferred value scope is θ
1/ θ
2=0.3 ~ 0.6.
In described same boundling spiral chute, the helix angle of each microminiature spiral chute 1,2 and 3 reduces gradually along rotary speed direction, namely meets β
n< β
i(1<i<N
w) < β
1, wherein β
1for the helix angle of microminiature spiral chute 1, β
nfor the helix angle of microminiature spiral chute 3, β
ifor the helix angle of microminiature spiral chute 2.
The radial groove width l of described boundling spiral fluted
1=(r
o-r
g) with the radial width l on downstream seal dam 6
2=(r
g-r
i) ratio l
1/ l
2choosing value scope be l
1/ l
2=0.2 ~ 4, preferred value scope is l
1/ l
2=0.5 ~ 1.5.
Described boundling spiral fluted groove depth choosing value scope is 0.1 ~ 30 μm, and preferred value scope is 2 ~ 10 μm, and the deep equality of each microminiature spiral chute 1,2 and 3 at same radius place in described same boundling spiral chute.
Embodiment two
With reference to Fig. 3,4, the difference of the present embodiment and embodiment one is, in described same boundling spiral chute, each microminiature spiral chute 1,2 and 3 shoals against rotary speed direction gradually in the degree of depth at same radius place, i.e. h
1<h
i<h
n, wherein h
nfor the groove depth against rotary speed direction first microminiature spiral chute 3, h
1for the groove depth against last microminiature spiral chute 1 of rotary speed direction, h
ifor the groove depth of middle microminiature spiral chute 2, all the other structures are identical with embodiment one with mode of execution.
Embodiment three
With reference to Fig. 5, the difference of the present embodiment and embodiment one is, the helixangleβ of middle microminiature spiral chute 2
iwith the helixangleβ along last microminiature spiral chute 3 of rotary speed direction
nequal, or the helixangleβ of middle microminiature spiral chute 2
iwith the helixangleβ along rotary speed direction first microminiature spiral chute 1
1equal, all the other structures are identical with embodiment one with mode of execution.
Embodiment four
With reference to Fig. 6, the difference of the present embodiment and embodiment one is, in same boundling spiral chute, each microminiature spiral chute 1,2 and 3 is intersected in a bit in low voltage side, and all the other structures are identical with embodiment one with mode of execution.
Embodiment five
With reference to Fig. 7, the difference of the present embodiment and embodiment one is, circumferential through annular groove 7 is offered in described boundling spiral fluted downstream, and the through annular groove of described circumference 7 is through with boundling spiral fluted groove root place, and all the other structures are identical with embodiment one with mode of execution.
Content described in this specification embodiment is only enumerating the way of realization that model utility is conceived; protection domain of the present utility model should not be regarded as being only limitted to the concrete form that embodiment states, protection domain of the present utility model is also and in those skilled in the art according to the thinkable equivalent technologies means of the utility model design.
Claims (4)
1. a gas lubrication boundling spiral groove end face mechanical sealing structure, it comprises rotating ring and the stationary ring of mechanical seal, it is characterized in that: the side of described rotating ring and stationary ring end face is high pressure side and upstream, the opposite side of described rotating ring and stationary ring end face is low voltage side and downstream, in described rotating ring or stationary ring, the end face of at least one seal ring is provided with multiple boundling spiral chute symmetrical along end face circumference, the microminiature spiral chute that described boundling spiral chute is not waited by multiple helix angle combines along end face circumference, and each microminiature spiral chute being arranged in same boundling spiral chute is cut off by the sealing weir of not slotting in high pressure side, through being integrated mutually is superposed at its groove root of low voltage side, described boundling spiral fluted downstream is provided with sealing dam.
2. sealing configuration according to claim 1, is characterized in that: microminiature spiral fluted number N in described same boundling spiral chute
wchoosing value scope be: 2≤N
w≤ 20.
3. sealing configuration according to claim 2, is characterized in that: in described boundling spiral chute, single microminiature spiral chute is at external diameter r
othe circular arc angle theta at place
1sealing weir between two microminiature spiral chutes adjacent with same boundling spiral chute mesohigh side is at external diameter r
othe circular arc angle theta at place
2ratio θ
1/ θ
2choosing value scope be θ
1/ θ
2=0.1 ~ 1.0; In described same boundling spiral chute, each microminiature spiral fluted helix angle reduces gradually along rotary speed direction, namely meets β
n< β
i(1<i<N
w) < β
1, wherein β
1for suitable rotary speed direction first microminiature spiral fluted helix angle, β
nfor suitable last microminiature spiral fluted helix angle of rotary speed direction, β
ifor centre any microminiature spiral fluted helix angle; The radial groove width l of described boundling spiral fluted
1=(r
o-r
g) with the radial width l on downstream seal dam
2=(r
g-r
i) ratio l
1/ l
2choosing value scope be l
1/ l
2=0.2 ~ 4; Described boundling spiral fluted groove depth choosing value scope is 0.1 ~ 30 μm, and in described same boundling spiral chute, each microminiature spiral chute shoals against rotary speed direction gradually in the degree of depth at same radius place.
4. sealing configuration according to claim 3, is characterized in that: preferred value scope is θ
1/ θ
2=0.3 ~ 0.6, l
1/ l
2=0.5 ~ 1.5, described boundling spiral fluted groove depth preferred value scope is 2 ~ 10 μm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520342928.8U CN204739222U (en) | 2015-05-25 | 2015-05-25 | Gas lubrication helicla flute terminal surface mechanical seal structure tied in a bundle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520342928.8U CN204739222U (en) | 2015-05-25 | 2015-05-25 | Gas lubrication helicla flute terminal surface mechanical seal structure tied in a bundle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204739222U true CN204739222U (en) | 2015-11-04 |
Family
ID=54420959
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520342928.8U Expired - Fee Related CN204739222U (en) | 2015-05-25 | 2015-05-25 | Gas lubrication helicla flute terminal surface mechanical seal structure tied in a bundle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204739222U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104896099A (en) * | 2015-05-25 | 2015-09-09 | 浙江工业大学 | Gas lubrication cluster spiral groove end face mechanical sealing structure |
| CN106439037A (en) * | 2016-11-18 | 2017-02-22 | 西华大学 | Seal ring and mechanical seal device with combination groove end |
| CN109516215A (en) * | 2018-12-03 | 2019-03-26 | 江苏科技大学 | A kind of high pressure air sealed bulk material rotary feeder and its application method |
-
2015
- 2015-05-25 CN CN201520342928.8U patent/CN204739222U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104896099A (en) * | 2015-05-25 | 2015-09-09 | 浙江工业大学 | Gas lubrication cluster spiral groove end face mechanical sealing structure |
| CN106439037A (en) * | 2016-11-18 | 2017-02-22 | 西华大学 | Seal ring and mechanical seal device with combination groove end |
| CN109516215A (en) * | 2018-12-03 | 2019-03-26 | 江苏科技大学 | A kind of high pressure air sealed bulk material rotary feeder and its application method |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20151104 Termination date: 20180525 |