CN1215135A - Screw groove end face sealing - Google Patents
Screw groove end face sealing Download PDFInfo
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- CN1215135A CN1215135A CN98120372A CN98120372A CN1215135A CN 1215135 A CN1215135 A CN 1215135A CN 98120372 A CN98120372 A CN 98120372A CN 98120372 A CN98120372 A CN 98120372A CN 1215135 A CN1215135 A CN 1215135A
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- spiral
- face
- downstream
- groove end
- screw groove
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- 238000007789 sealing Methods 0.000 title claims abstract description 43
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 67
- 238000012856 packing Methods 0.000 claims 1
- 239000012530 fluid Substances 0.000 abstract description 19
- 230000000694 effects Effects 0.000 abstract description 8
- 230000003068 static effect Effects 0.000 abstract description 7
- 230000008901 benefit Effects 0.000 abstract description 2
- 238000005086 pumping Methods 0.000 description 21
- 230000009467 reduction Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 4
- 210000002421 cell wall Anatomy 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000013011 mating Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
- F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
- F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
- F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
Abstract
The present invention relates to a spiral fluted end-face sealing structure of rotary shaft, and is characterized by that on the seal end face of rotating ring or static ring or on these two end faces two rows of spiral flutes are set up simultaneusly, one row is positioned at high-pressure side, i.e. epstream, another row is positioned at low-pressure side, i.e. downstream, and the spiral angles of both them are opposite in direction, the radial height of the upstream spiral flute is greater than or equal to that of downstream spiral flute, and the total effect of two rows of spiral flutes is to pump the seal fluid from upstream to downstream. It possesses the advantages of large loading capacity and rigidity of fluid film and strong adaptability for rotating speed, and is applicable to various rotary machinery sealing, specially to dry gas lock system.
Description
The invention belongs to the end face seal of running shaft, particularly a kind of screw groove end face sealing, this sealing can be used for the running shaft of machineries such as compressor, decompressor, pump, reactor stirrer.
Chinese patent 90101737.x, U. S. Patent 5,201,531 disclose the end face seal of a kind of Hydrodynamic pressure type double spiral groove.Its common trait is: be positioned at the high pressure side, promptly the spiral fluted radial height of upstream is less than being positioned at low voltage side, i.e. the spiral fluted radial height in downstream.Under given rotation direction, upstream one row spiral chute is with fluid-encapsulated pumping downstream, and downstream one row spiral chute is then with fluid-encapsulated pumping upstream.Downstream one row spiral fluted radial height must be enough greatly, the pump that is produced to make it draws pump that pressure reduction should be able to balance upstream one row spiral chute be produced and draws both sides fluid pressure difference sum inside and outside pressure reduction and the seal face.That is to say that the pump that this two row spiral chute is produced draws pressure reduction and must balance each other with both sides fluid pressure difference inside and outside the seal face, guarantee that therefore fluid-encapsulated theoretically leakage rate is zero.But it is less that the sealing of this class is only applicable to the pressure reduction of seal face two side liquids, and under the higher operating mode of fluid-encapsulated viscosity.
The common screw groove end face sealing that utilizes the dynamic and static pressure combined type of fluid all is single-row screw groove end face sealing.In this row spiral fluted downstream the plane endless belt is arranged, play throttling action, promptly " stop " effect, as U. S. Patent 4,212,475 is disclosed.
The objective of the invention is to propose the downstream pumping double spiral groove end face seal of the dynamic and static pressure combined type of a kind of fluid, it has bigger fluid film thickness than above-mentioned sealing under identical condition, perhaps have bigger fluid film rigidity under identical fluid film thickness.
The present invention is achieved in that a kind of screw groove end face sealing, comprise: rotating ring with seal face, stationary ring with seal face, the seal face of its seal face and described rotating ring fits and can slide relative, seal face is a ring, it is characterized in that: at least one of the seal face of described rotating ring and described stationary ring, two row spiral chutes are set, wherein, one row are positioned at the high pressure side, it is the upstream, another row are positioned at low voltage side, it is the downstream, the direction of two row spiral fluted helix angles is opposite, the effective radial height of spiral fluted that is positioned at the upstream is greater than the spiral fluted radial height that is positioned at the downstream, and one row spiral fluted downstream also has a plane endless belt in the downstream.
The high pressure side is defined as " upstream " in the present invention, and low voltage side is defined as " downstream "." downstream pumping " is meant by upstream pumping downstream." a spiral fluted radial height " is meant the height of a spiral chute in the seal face scope that rotating ring and stationary ring are fitted each other, i.e. effective height.In addition, " spiral chute " of the present invention is meant, the overall trend of groove is a spirality roughly, and is not the accurate spirality of indication on the mathematics.
Compare with the end face seal of pure Hydrodynamic pressure type double spiral groove, a row spiral fluted radial height that is positioned at the upstream in the present invention is always greater than a row spiral fluted radial height that is positioned at the downstream.So under given rotation direction, the total effect of two row spiral chutes be with fluid-encapsulated by the high side to low side pumping, promptly realize downstream of the present invention pumping.This pumping meeting produces slight leakage, still, has exchanged bigger fluid film thickness and fluid film rigidity between two seal faces for as cost.Therefore, it is fluid-encapsulated that sealing of the present invention more adapts to low viscosity than the end face seal of pure Hydrodynamic pressure type double spiral groove, as gas; Also be applicable to simultaneously the higher operating mode of pressure reduction of seal face two side liquids.
Compare with the single-row screw groove end face sealing of downstream pumping of the dynamic and static pressure combined type of fluid, in screw groove end face sealing of the present invention, increased by one and be listed as the spiral chute that is positioned at the downstream, the direction of its helix angle is opposite with the spiral fluted helix angle direction that is positioned at the upstream, under given rotation direction, downstream one row spiral chute draws fluid-encapsulated pump upstream, play " push and block " effect initiatively, and the plane endless belt in the single-row screw groove end face sealing has been passive " stopping " effect.So sealing effect of the present invention is better.Therefore, in pumping double spiral groove in downstream of the present invention end face seal, bigger fluid film thickness is arranged between the seal face, perhaps under identical fluid film thickness, have bigger fluid film rigidity.In the present invention, one row spiral fluted downstream still keeps the less plane endless belt of a width in the downstream, and it also has been throttling action under rotary state, under static state then plays the parking seal action.
Description of drawings:
Fig. 1 is the figure that spiral chute is arranged on the downstream pumping double spiral groove end face seal on the rotating ring, and wherein the outside of seal face is the high pressure side.
Fig. 2 is the figure that spiral chute is arranged on the downstream pumping double spiral groove end face seal on the stationary ring, and wherein the outside of seal face is the high pressure side.
Fig. 3 be spiral chute be arranged on simultaneously on the rotating ring and stationary ring on the figure of downstream pumping double spiral groove end face seal, wherein the outside of seal face is the high pressure side.
Fig. 4 is the schematic representation of spiral chute molded lines.
Fig. 5 is the planimetric map of seal face.Wherein the outside of seal face is the high pressure side, and all there is the plane endless belt in the spiral fluted outside, between the two row spiral chutes and upstream.
Fig. 6 is the planimetric map of seal face.Wherein the outside of seal face is the high pressure side, between the two row spiral chutes plane endless belt is arranged, and the spiral fluted outside in upstream does not have the plane endless belt.
Fig. 7 is the planimetric map of seal face.Wherein the outside of seal face is the high pressure side, does not have the plane endless belt between the two row spiral chutes, and there is the plane endless belt in the spiral chute outside in upstream.
Fig. 8 is the planimetric map of seal face.Wherein the outside of seal face is the high pressure side, and the spiral fluted outside, between the two row spiral chutes and upstream does not all have the plane endless belt.
Fig. 9 is the figure that spiral chute is arranged on the downstream pumping double spiral groove end face seal on the rotating ring.The inboard of seal face is the high pressure side.
Figure 10 is the figure that spiral chute is arranged on the downstream pumping double spiral groove end face seal on the stationary ring.The inboard of seal face is the high pressure side.
Figure 11 be spiral chute be arranged on simultaneously on the rotating ring and stationary ring on the figure of downstream pumping double spiral groove end face seal.The inboard of seal face is the high pressure side.
Figure 12 is the planimetric map of seal face.The inboard of seal face is the high pressure side, and all there is the plane endless belt between the two row spiral chutes and spiral fluted inboard, upstream.
Figure 13 is the planimetric map of seal face.The inboard of seal face is the high pressure side, between the two row spiral chutes plane endless belt is arranged, and spiral chute inboard, upstream does not have the plane endless belt.
Figure 14 is the planimetric map of seal face.The inboard of seal face is the high pressure side, does not have the plane endless belt between the two row spiral chutes, and there is the plane endless belt spiral chute inboard, upstream.
Figure 15 is the planimetric map of seal face.The inboard of seal face is the high pressure side, and between the two row spiral chutes and spiral fluted inboard, upstream does not all have the plane endless belt.
Figure 16 is a upstream spiral chute and the downstream spiral fluted enlarged view among Fig. 6.
Figure 17 is a upstream spiral chute and the downstream spiral fluted enlarged view among Fig. 8.
The inside and outside circle of the seal face that rotating ring and stationary ring fit is represented in double dot dash line among Figure 16, Figure 17.
In the above accompanying drawing, the symbol implication is as follows:
R
b-equilibrium radius
The alpha-helix angle
The h-spiral chute degree of depth
S
1-upstream spiral chute normal direction width
S
2The normal direction width on weir ,-upstream
S
3-downstream spiral fluted normal direction width
S
4The normal direction width on weir ,-downstream
H-high pressure side, i.e. upstream
L-low voltage side, i.e. downstream
The total pump of G-two row spiral chutes draws direction
In Fig. 1 to Fig. 8:
R
0The inside radius of seal face between-rotating ring and the stationary ring
R
1-downstream spiral fluted inside radius
R
2-downstream spiral fluted outer radius
R
3-upstream spiral fluted inside radius
R
4-upstream spiral fluted outer radius
R
5The outer radius of seal face between-rotating ring and the stationary ring
In Fig. 9 to Figure 15:
R
10The outer radius of seal face between-rotating ring and the stationary ring
R
11-downstream spiral fluted outer radius
R
12-downstream spiral fluted inside radius
R
13-upstream spiral fluted outer radius
R
14-upstream spiral fluted inside radius
R
15The inside radius of seal face between-rotating ring and the stationary ring
Now represented in conjunction with the accompanying drawings embodiment is elaborated.
In accompanying drawing of the present invention, the spiral fluted radius R shown in Fig. 1-3 and Fig. 9-11 especially
1-R
4, R
11-R
14, their essence implications in specification of the present invention are meant spiral fluted maximum or least radius.The position that sectional view dissects when dissecing may not be spiral fluted maximum diameter place or minimum diameter place.But such mark can make the reader pass through these accompanying drawings, can very fast understanding to the present invention.
In addition, in accompanying drawing of the present invention, spiral chute appears to by three or four cell walls to be formed, but, in fact a spiral chute is to be made of two major trough walls and one or two transition cell wall between two major trough walls, the actual molded lines that refers to those two major trough walls of mentioned in this manual spiral chute molded lines is seen 21,22,23,24 among Figure 16 and Figure 17.
Fig. 1 is arranged on the figure of the downstream pumping double spiral groove end face seal on the rotating ring for spiral chute.The sealing device comprises rotating ring 1, stationary ring 2, secondary seal ring 3, throw-out collar 4, spring 5, stop pin 6, housing 7, axle sleeve 8, axle 9, static seal circle 10.
The seal face of the seal face of rotating ring 1 and stationary ring 2 is fitted mutually and can slide relative, and the faying surface of the two is seal face.In this embodiment, the outside of seal face is the high pressure side, i.e. upstream H.Two row spiral chutes are set on the seal face of rotating ring 1.In the high pressure side one row spiral chute 11 is arranged, one row spiral chute 12 is arranged in low voltage side.Be positioned at the spiral fluted radial height (R of upstream
4-R
3) greater than the spiral chute radial height (R that is positioned at the downstream
2-R
1), referring to shown in Figure 5.Under given rotation direction, because this two row spiral fluted helix angle direction is opposite, a row spiral chute that is positioned at the upstream is fluid-encapsulated pumping downstream, and a row spiral chute that is positioned at the downstream is with fluid-encapsulated pumping upstream.Owing to be positioned at the effective radial height of a row spiral fluted of upstream greater than a row spiral fluted radial height that is positioned at the downstream, thereby the total action effect of two row spiral chutes is with fluid-encapsulated direction pumping downstream from the upstream along arrow G, thereby produces a micro-leakage.In the upstream spiral fluted outside one plane endless belt 13, i.e. (R arranged
5-R
4) between endless belt.One plane endless belt 14, i.e. (R also arranged between the two row spiral chutes
3-R
2) between endless belt.In addition, inboard plane endless belt 15, the i.e. (R in addition of one row spiral fluted in the downstream
1-R
0) between endless belt, play throttling and parking sealer.The molded lines of spiral chute sidewall can be any curve outside the concentric circle of removing the seal face cylindrical shown in Figure 4 or remove by any straight line outside the radial alignment in the seal face center of circle, for example log spiral, circular arc line, oblique broken line.The scope of helix angle be 0 °＜| α |＜90 °, its optimum range is 5 °-30 °, for example 20 °.Upstream and downstream two row spiral fluted degree of depth h can be constant radially and circumferentially, for example 0.02mm.Also can change, its scope is 0.002-0.2mm, and optimum range is 0.005-0.1mm.The spiral fluted width can change, and also can be constant, for example, widens its normal direction width S gradually from interior radial outer diameter
1, S
3Scope be 0.2-20mm, optimum range is 0.5-10mm.The width S on the weir between two adjacent spiral chutes
2, S
4Can be constant, also can change, its normal direction width S
2, S
4With spiral fluted normal direction width S
1, S
3Ratio, i.e. S
2/ S
1And S
4/ S
3Be 0.2-5, optimum range is 0.3-3.
Spiral chute among the present invention also can be arranged on the seal face of stationary ring, sees Fig. 2.Can also be arranged on simultaneously on the seal face of rotating ring and stationary ring, see Fig. 3.
Fig. 4 is the figure of spiral chute molded lines.Spiral chute has two major trough walls, its molded lines can be to remove the concentric circle concentric with seal face (pitch angle alpha will=0 °) or remove radial alignment by the seal face center of circle (pitch angle alpha will=90 °) any curve or straight line in addition, for example: log spiral (equiangular helical spiral), spiral of Archimedes, circular arc line, skew lines, oblique broken line.Wherein helix angle is defined as follows: establish any type of smoothed curve or straight line from the A point of the less inside radius of radius (or A ', A " point) beginning; till the B point at the outer radius place of radius larger part (or B ', B " point), the concentric circle at any radius R place between the inside and outside radius and this curve or straight line intersect at P point (or P ', P " point), promptly are defined as helix angle at the tangent line of this point curve or the angle α between straight line itself and the concentrically ringed tangent line.Curve A B is opposite with the helix angle direction of curve A " B ", if definition the former for just, then the latter is for bearing.In the present invention, the scope of helix angle is: 0 °＜| α |＜90 °, its optimum range is 5 °-30 °.Pitch angle alpha will can be constant, also can change, promptly can form by the various curves of removing outside the concentric circle, and can be that broken line is formed also by straight line or many straight lines of removing outside the radial alignment.
Fig. 5 to Fig. 8 is alternative spiral fluted shape and position on the seal face, and wherein, the outside of seal face is the high pressure side, i.e. upstream H, and the inboard of seal face is a low voltage side, i.e. downstream L.
Fig. 5 has the view of the seal face of plane endless belt for the spiral fluted outside, between the spiral chute of both sides and upstream.One plane endless belt 14, i.e. (R arranged between the two row spiral chutes
3-R
2) between endless belt.Two row spiral chutes do not join, and are " eight " font.
There is plane endless belt 13, i.e. (a R in the outside of upstream one row spiral chute 11
5-R
4) between the plane endless belt.Also have plane endless belt 15, i.e. (a R in the inboard of downstream spiral chute 12
1-R
0) between the plane endless belt.If spiral chute processing is on rotating ring the time, the sense of rotation of this ring be C to; If spiral chute processing is on stationary ring the time, the sense of rotation of the rotating ring relative with it be D to.
The inside and outside circle of seal face between rotating ring and the stationary ring is represented in double dot dash line among this figure and the following figure.Spiral fluted radial height in upstream is (R in the figure
4-R
3), downstream spiral fluted radial height is (R
2-R
1).
Fig. 6 has plane endless belt 14 between the two row spiral chutes, and the outside of upstream threaded groove 11 does not have the figure of the seal face of plane endless belt.In the figure, spiral fluted radial height in upstream is (R
5-R
3), there are plane endless belt 15, i.e. (R in the downstream of downstream spiral chute 12
1-R
0) between endless belt.
Fig. 7 does not have the plane endless belt between the two row spiral chutes, and there is the figure of the seal face of plane endless belt 13 in the outside of upstream spiral chute 11.Two row spiral chutes overlap R
2=R
3, being " people " font, there are plane endless belt 15, i.e. (R in the downstream of downstream spiral chute 12
1-R
0) between endless belt.
Fig. 8 is the figure that does not have the seal face of plane endless belt between the two row spiral chutes with the upstream spiral fluted outside.Among this figure, the radial height of upstream spiral chute 11 is (R
5-R
3), two row spiral chutes intersect, R
2=R
3, there are plane endless belt 15, i.e. (R in the downstream of downstream spiral chute 12
1-R
0) between endless belt.
Sense of rotation among each figure below Fig. 6 is consistent with the explanation of Fig. 5.
According to the present invention, the effective radial height of spiral fluted that is positioned at the upstream must be greater than the spiral fluted radial height that is positioned at the downstream, 1＜(R in Fig. 5 and Fig. 7
4-R
3)/(R
2-R
1)≤5; 1＜(R in Fig. 6 and Fig. 8
5-R
3)/(R
2-R
1)≤5.
In above embodiment, the outside of all supposing seal face is the high pressure side, i.e. upstream H, and its inboard is a low voltage side, i.e. downstream L.If the inboard of seal face is the high pressure side, i.e. upstream H, its outside is a low voltage side, i.e. downstream L, embodiment is seen Fig. 9-Figure 15, in these figure, according to the present invention, the effective radial height (R of upstream spiral fluted
13-R
14) (seeing Figure 12,14) or (R
13-R
15) (seeing Figure 13,15) must be greater than downstream spiral fluted radial height (R
11-R
12).
The inboard of its seal face of sealing shown in Figure 9 is the high pressure side, i.e. upstream H, and the outside of seal face is a low voltage side, promptly downstream L only processes spiral chute on the seal face of rotating ring 1.
The inboard of its seal face of sealing shown in Figure 10 is the high pressure side, i.e. upstream H, and the outside of seal face is a low voltage side, promptly downstream L only processes spiral chute on the seal face of stationary ring 2.
The inboard of its seal face of sealing shown in Figure 11 is the high pressure side, i.e. upstream H, and the outside of seal face is a low voltage side, promptly downstream L is processed with spiral chute simultaneously on the seal face of rotating ring 1 and stationary ring 2.
Figure 12 to Figure 15 represents alternative spiral fluted shape and position on the seal face.
Figure 12 is the seal face view that the plane endless belt is arranged with the inboard of upstream spiral chute 11 between the two row spiral chutes.One plane endless belt 17, i.e. (R arranged between the two row spiral chutes
12-R
13) between endless belt.Two row spiral chute divergence are " eight " font.There is plane endless belt 16, i.e. (a R inboard of upstream one row spiral chute 11
14-R
15) between the plane endless belt.Also have plane endless belt 18, i.e. (a R in the downstream of downstream spiral chute 12
10-R
11) between the plane endless belt.Spiral fluted effective radial height in upstream is (R in the figure
13-R
14).The inside and outside circle of seal face between rotating ring and the stationary ring is represented in double dot dash line among this figure and following each figure.
Figure 13 has plane endless belt 17 between the two row spiral chutes, and the inboard of upstream spiral chute 11 does not have the figure of the seal face of plane endless belt.Figure middle and upper reaches spiral fluted radial height is (R
13-R
15), there are plane endless belt 18, i.e. (R in the downstream of downstream spiral chute 12
10-R
11) between endless belt.
Figure 14 does not have the plane endless belt between the two row spiral chutes, and there is the figure of the seal face of plane endless belt 16 inboard of upstream spiral chute 11.Two row spiral chutes are connected to each other R
12=R
13, being " people " font, there are plane endless belt 18, i.e. (R in the downstream of downstream spiral chute 12
10-R
11) between endless belt.
Figure 15 is the figure that does not have the seal face of plane endless belt between the two row spiral chutes with the inboard of upstream spiral chute 11.In the figure, the radial height of upstream spiral chute 11 is (R
13-R
15), two row spiral chutes intersect, R
12=R
13, there are plane endless belt 18, i.e. (R in the downstream of downstream spiral chute 12
10-R
14) between endless belt.
According to the present invention, the effective radial height of spiral fluted that is positioned at the upstream must be greater than the spiral fluted radial height that is positioned at the downstream, 1＜(R in Figure 12 and Figure 14
13-R
14)/(R
11-R
12)≤5; 1＜(R in Figure 13 and Figure 15
13-R
15)/(R
11-R
12)≤5.
In Fig. 9-Figure 15, identical with the explanation of the ratio of spiral fluted width with the explanation among Fig. 1-Fig. 8 about spiral fluted molded lines, helix angle, the degree of depth, width and weir
Two row spiral chutes are connected to each other R in Fig. 7 and Fig. 8
2=R
3, two row spiral chutes interconnect R in Figure 14 and Figure 15
12=R
13, still, R when two row grooves stagger several angle
2Also can be not equal to R
3, R
12Also can be not equal to R
13
In a word, the essential characteristic that the present invention is different from existing Hydrodynamic pressure type double spiral groove end face seal in the document is: a row spiral fluted radial height that is positioned at the high pressure side and is the upstream is greater than being positioned at the row spiral fluted radial height that low voltage side is the downstream, therefore, the total effect of two row spiral chutes is with the fluid-encapsulated pumping downstream from the upstream, thereby is that cost has exchanged bigger fluid film thickness and fluid film rigidity for the leakage of trace.
Implement sealing total arrangement of the present invention various ways can be arranged: single sealing, double-sealing, double-sealing, two-stage series connection sealing, the sealing of three grades of series seals, double-sealing and single seal combination etc. of formula back-to-back of formula face-to-face.
Sealing of the present invention is the end face seal of the dynamic and static pressure mating type of a kind of novel fluid, its advantage be fluid film thickness and Rigidity is bigger, namely is applicable to full-bodied fluid-encapsulated (for example oil), also be applicable to low viscous fluid-encapsulated (for example Water or gas); Namely be applicable to the low pressure operating mode, also be applicable to the high pressure operating mode; Namely be applicable to High Rotation Speed, also be applicable to low The speed rotation. The present invention can be used for the whirlers such as various types compressor, decompressor, seperator, pump, reaction ax agitator The sealing of tool, especially dry gas seal.
Claims (14)
1, a kind of screw groove end face sealing, comprise: rotating ring with seal face, stationary ring with seal face, the seal face of its seal face and described rotating ring fits and can slide relative, seal face is a ring, it is characterized in that: at least one of the seal face of described rotating ring and described stationary ring, two row spiral chutes are set, wherein, one row are positioned at the high pressure side, it is the upstream, another row are positioned at low voltage side, i.e. downstream, and the direction of two row spiral fluted helix angles is opposite, the effective radial height of spiral fluted that is positioned at the upstream is greater than the spiral fluted radial height that is positioned at the downstream, and one row spiral fluted downstream also has a plane endless belt in the downstream.
2, screw groove end face sealing according to claim 1 is characterized in that: the effective radial height of the spiral fluted of upstream is less than or equal to 5 with the ratio of the spiral fluted radial height in downstream greater than 1.
3, screw groove end face sealing according to claim 1 is characterized in that: on the seal face scope of the pitch angle alpha will of spiral chute sidewall molded lines be 0 °＜| α |＜90 °.
4, screw groove end face sealing according to claim 3 is characterized in that: the scope of the pitch angle alpha will of spiral chute sidewall molded lines is 5 °-30 ° on the seal face.
5, screw groove end face sealing according to claim 3 is characterized in that: on the seal face molded lines of spiral chute sidewall be log spiral or for the circular arc line of ring packing end face off-centre.
6, screw groove end face sealing according to claim 3 is characterized in that: the molded lines of spiral chute sidewall is skew lines or broken line on the seal face.
7, screw groove end face sealing according to claim 1 is characterized in that: the spiral fluted degree of depth is constant, and depth bounds is 0.002-0.2mm.
8, screw groove end face sealing according to claim 7 is characterized in that: the spiral fluted depth bounds is 0.005-0.1mm.
9, screw groove end face sealing according to claim 8 is characterized in that: the spiral fluted degree of depth changes.Depth bounds is 0.002-0.2mm.
10, screw groove end face sealing according to claim 9 is characterized in that: the spiral fluted depth bounds is 0.005-0.1mm.
11, screw groove end face sealing according to claim 1 is characterized in that: the scope of spiral chute normal direction width is 0.2-20mm.
12, screw groove end face sealing according to claim 11 is characterized in that: the scope of spiral chute normal direction width is 0.5-10mm.
13, screw groove end face sealing according to claim 1 is characterized in that: the normal direction width on the weir between two adjacent spiral chutes is 0.2-5 with the ratio of spiral fluted normal direction width.
14, screw groove end face sealing according to claim 13 is characterized in that: the normal direction width on the weir between two adjacent spiral chutes is 0.3-3 with the ratio of spiral fluted normal direction width.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN98120372A CN1069750C (en) | 1997-10-17 | 1998-10-09 | Screw groove end face sealing |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN971170819 | 1997-10-17 | ||
| CN97117081 | 1997-10-17 | ||
| CN98120372A CN1069750C (en) | 1997-10-17 | 1998-10-09 | Screw groove end face sealing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1215135A true CN1215135A (en) | 1999-04-28 |
| CN1069750C CN1069750C (en) | 2001-08-15 |
Family
ID=25744370
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98120372A Expired - Lifetime CN1069750C (en) | 1997-10-17 | 1998-10-09 | Screw groove end face sealing |
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| Country | Link |
|---|---|
| CN (1) | CN1069750C (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103486268A (en) * | 2013-09-15 | 2014-01-01 | 丹东克隆集团有限责任公司 | Mechanical dry gas sealing device for pumps |
| CN103732958A (en) * | 2011-09-10 | 2014-04-16 | 伊格尔工业股份有限公司 | Sliding component |
| CN103791097A (en) * | 2014-02-28 | 2014-05-14 | 江苏大学 | Combination fluid dynamic pressure groove mechanical seal ring capable of automatically discharging particles |
| CN104265906A (en) * | 2014-08-06 | 2015-01-07 | 浙江工业大学 | Gas lubrication bird-wing-shape-imitation v groove end face sealing structure |
| CN104265900A (en) * | 2014-08-06 | 2015-01-07 | 浙江工业大学 | Two-way rotating gas dynamic/static pressure mechanical seal type bird wing-shaped groove structure |
| CN105793628A (en) * | 2013-12-09 | 2016-07-20 | 伊格尔工业股份有限公司 | Sliding component |
| CN105814346A (en) * | 2013-12-09 | 2016-07-27 | 伊格尔工业股份有限公司 | Sliding component |
| CN107735604A (en) * | 2015-06-15 | 2018-02-23 | 伊格尔工业股份有限公司 | Slide unit |
| 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 |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101469771B (en) * | 2007-12-26 | 2010-12-29 | 丹东克隆集团有限责任公司 | Bidirectionally rotary cascade arc groove mechanical sealing end-face |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB9103217D0 (en) * | 1991-02-15 | 1991-04-03 | Crane John Uk Ltd | Mechanical face seals |
| US5201531A (en) * | 1992-04-02 | 1993-04-13 | John Crane Inc. | Face seal with double spiral grooves |
| JP2563081B2 (en) * | 1994-03-22 | 1996-12-11 | 日本ピラー工業株式会社 | Non-contact type shaft sealing device |
-
1998
- 1998-10-09 CN CN98120372A patent/CN1069750C/en not_active Expired - Lifetime
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| CN103732958B (en) * | 2011-09-10 | 2016-09-21 | 伊格尔工业股份有限公司 | Slide unit |
| CN103732958A (en) * | 2011-09-10 | 2014-04-16 | 伊格尔工业股份有限公司 | Sliding component |
| CN103486268A (en) * | 2013-09-15 | 2014-01-01 | 丹东克隆集团有限责任公司 | Mechanical dry gas sealing device for pumps |
| CN105814346B (en) * | 2013-12-09 | 2017-08-04 | 伊格尔工业股份有限公司 | Slide unit |
| CN105793628A (en) * | 2013-12-09 | 2016-07-20 | 伊格尔工业股份有限公司 | Sliding component |
| CN105814346A (en) * | 2013-12-09 | 2016-07-27 | 伊格尔工业股份有限公司 | Sliding component |
| US9677670B2 (en) | 2013-12-09 | 2017-06-13 | Eagle Industry Co., Ltd. | Sliding parts |
| US9845886B2 (en) | 2013-12-09 | 2017-12-19 | Eagle Industry Co., Ltd. | Sliding parts |
| CN105793628B (en) * | 2013-12-09 | 2018-02-02 | 伊格尔工业股份有限公司 | Slide unit |
| CN103791097A (en) * | 2014-02-28 | 2014-05-14 | 江苏大学 | Combination fluid dynamic pressure groove mechanical seal ring capable of automatically discharging particles |
| CN104265900A (en) * | 2014-08-06 | 2015-01-07 | 浙江工业大学 | Two-way rotating gas dynamic/static pressure mechanical seal type bird wing-shaped groove structure |
| CN104265906A (en) * | 2014-08-06 | 2015-01-07 | 浙江工业大学 | Gas lubrication bird-wing-shape-imitation v groove end face sealing structure |
| CN107735604A (en) * | 2015-06-15 | 2018-02-23 | 伊格尔工业股份有限公司 | Slide unit |
| 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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|---|---|
| CN1069750C (en) | 2001-08-15 |
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