CN101806362A - Mechanical sealing device of middle rotating ring - Google Patents
Mechanical sealing device of middle rotating ring Download PDFInfo
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- CN101806362A CN101806362A CN201010144528A CN201010144528A CN101806362A CN 101806362 A CN101806362 A CN 101806362A CN 201010144528 A CN201010144528 A CN 201010144528A CN 201010144528 A CN201010144528 A CN 201010144528A CN 101806362 A CN101806362 A CN 101806362A
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- rotating ring
- mechanical seal
- face
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Abstract
The invention relates to a mechanical sealing device of a middle rotating ring. The mechanical sealing device of the middle rotating ring is characterized in that the middle rotating ring (2) is added between a mechanical sealing stationary ring (1) and a rotating ring (4); the rotating speed of the middle rotating ring (2) can be adjusted and controlled by a driving part (3) of the middle rotating ring, and can be higher or lower than that of a rotating shaft of a sealed unit; and the two side surfaces of the middle rotating ring (2) are sealing end surfaces. The mechanical sealing device has the advantages that: compared with the traditional mechanical sealing, the rotating speed of the rotating shaft of the sealed unit does not determines the relative rotating speed of the mechanical sealing end surfaces, can lead the low (high) rotating speed unit sealing end surfaces have higher (lower) relative rotating speed, and lead the units with different rotating speed to be capable of maintaining a reasonable relative rotating speed of the end surfaces. The mechanical sealing device is applicable to shaft-end sealing devices of various rotating machines, especially sealing devices of low-rotating-speed units and high-rotating-speed unit.
Description
Technical field
The invention belongs to the shaft end seal of rotating machinery, be particularly related to a kind of in the middle of the rotating ring mechanical seal device, rotating ring mechanical seal device can be used for the shaft end seal of the rotation class machines such as compressor, decompressor, seperator, pump, reactor of various types in the middle of this.
Background technique
Mechanical seal is widely used in numerous rotating machinery axle heads, complexity because of its working condition, further investigation to mechanical seal will be long-term, arduous and must constantly an advance process, particularly the stability of high speed and low speed unit shaft end seal is two difficult point problems of puzzlement researcher all the time.Be in particular in: contact-type mechanical seal relative rotation speed between the fast state lower sealing surface is too high, causes phenomenons such as sealing surface friction, wearing and tearing, heating, distortion serious, and sealability descends rapidly, even cisco unity malfunction; And contactless mechanical seal fluid film between the low speed state lower end surface can not generate enough opening forces and rigidity, can't guarantee the normal separation of sealing surface and the stability in gap.Therefore, the regulatable mechanical sealing technology of a kind of sealing surface relative rotation speed of necessary research, reduce the relative rotation speed of high speed contact-type mechanical seal end surface on the one hand, improve the relative rotation speed of low speed non-contact mechanical seal end face on the other hand, different mechanical seal can both be operated in the rational speed range, thereby increase the stability of sealing, prolong its working life.
For the mechanical seal of high rotating speed contact-type, in order to reduce serious phenomenon such as sealing surface friction, wearing and tearing, heating, distortion, mainly by following counter-measures are arranged:
(1) friction pair material research
The hard anchor ring material of friction pair commonly used has: cemented carbide, pottery, special steel, these several big classes of cast metal, and wherein use with cemented carbide and ceramic-like materials more, in the majority in the practicality with silicon carbide, silicon nitride, Tungsten carbite.Specifically, the application of research report diamond in sealing arranged in recent years, fewer companies has planned to develop super nanocrystal diamond technology seal face.The soft anchor ring of friction pair commonly used has: carbon graphite, Cuprum alloy, resin, its medium-carbon graphite with its good self lubricity, corrosion resistance, workability and preferably heat transfer property become the highest soft anchor ring material commonly used of utilization rate.
(2) the particularly dynamic and static ring heat dissipating state research of seal
Mainly take: select measures such as the good material of thermal diffusivity, the washing condition that improves sealing, optimal design sealing configuration for use.Because of being sealed the restriction of associated media flow (flushing dose) size, heat can't be taken away by significantly increasing fluid flow in most sealings, and the constraint of other conditions such as friction pair is corrosion-resistant because of being subjected to, low abrasion, be difficult to find simultaneously all extraordinary material pairing of dynamic and static ring thermal diffusivity, therefore, the research of this direction can only improve the stability of sealing to a certain extent, is difficult to break away from high-revolving essence influence
Friction pair material research is subjected to the restriction of material technology, still can not improve the stability of high speed conditions sealing at present at all, but its effect is along with the continuous propelling that is embedded in of research.
For non-contact mechanical seal, the most typical with equivalent gullet depth spiral chute and "T"-shaped groove end face seal.How to strengthen end face hydrodynamic effect, to increase end face fluid film bearing capacity and fluid film rigidity, thereby the lift-off seal operation stability increases the service life, and expanding the sealing application occasion is a main direction of contactless mechanical seal research and future development.And the relative rotational between the seal face of pairing is a key factor that influences end face fluid film bearing capacity and fluid film rigidity, and relative rotational is the linear proportional relation variation between the basic heel end face of end face fluid film bearing capacity and fluid film rigidity.All the time because the influence of thinking set and the restriction of machine set condition, research report and the practical product that sealed generating unit speed is sought suitable seal face relative rotational do not appear breaking away from, this significantly reduces some rotating speeds shaft end seal stability and life-span higher and low unit, particularly slow-speed of revolution unit.Present research still mainly concentrates on seal face grooved and the Parameter Optimization thereof.
Chinese patent 02146449.9 discloses a kind of double helix angle three-dimensional spiral groove face seals, as shown in Figure 1.It is characterized in that: the spiral fluted upstream is that the high pressure side is wideer, the downstream is that low voltage side is narrower, and the spiral fluted degree of depth is that the high pressure side is that low voltage side shoals gradually to the downstream from the upstream, thereby forms a kind of three-dimensional convergent contour spiral chute.This double helix angle three-dimensional spiral groove face seals can obtain bigger fluid film rigidity, but the processing of the bottom land of its inclination is very difficult.
Chinese patent 02132978.8 discloses a kind of spiral chute end surface mechanical sealing by the angular microflute group composition, as shown in Figure 2.This angular microflute trend is consistent with the spiral chute direction, and sealing end face shallow slot structure seems and more complicated because of this angular microflute moves towards to distribute along spiral chute, and do not have tangible collapsed shape, is difficult to significantly promote end face fluid film rigidity.
According to present seal face grooved, spiral chute is a kind of trench structure with maximum fluid film bearing capacity and fluid film rigidity, but for the lower unit of rotating speed, because of its low excessively end face relative rotational, become to influence the bottleneck of its end face hydrodynamic effect power, the optimization of end face grooved has been difficult to fundamentally improve the formation of hydrodynamic.
Reason in sum, design a kind of middle rotating ring mechanical seal device, this centre rotating ring mechanical seal device can make different rotating speeds unit seal face can both obtain a suitable relative rotational, thereby break away from of the influence of sealed generating unit speed, promote the working life of higher (low) rotating speed unit sealing sealability.
Summary of the invention
The purpose of this invention is to provide a kind of middle rotating ring mechanical seal device, this mechanical seal device can adapt to the unit of bigger speed range, particularly high (low) rotating speed unit.
The object of the present invention is achieved like this: rotating ring mechanical seal device in the middle of a kind of, form by the stationary ring 1 that has seal face, the middle rotating ring 2 that has seal face, the rotating ring 4 that has seal face and other correlated parts, stationary ring 1 is face-to-face installation with middle rotating ring 2, middle rotating ring 2 with the seal face of rotating ring 4, can directly fit between the sealing surface, also can separate in a very little gap.It is characterized in that: the middle rotating ring 2 that between stationary ring 1 and rotating ring 4, is placed with the rotating speed adjustable control.
The present invention mainly adopts following technical measures to realize:
The sealing surface relative rotation speed of rotating ring mechanical seal device is regulatable in the middle of described, and the rotating speed of sealed unit does not directly determine the rotating speed of seal face.
The regulation and control of the sealing surface relative rotation speed of rotating ring mechanical seal device are to realize by the rotational speed of adjusting middle rotating ring 2 in the middle of described.
The layout of rotating ring mechanical seal device can be the single-stage sealing of rotating ring 2 in the middle of having only in the middle of described, also tandem seal or the double seals that can be made up of the ring body of rotating ring 2 in the middle of more than two and pairing thereof.
The rotating ring mechanical seal device can be a contact-type or contactless in the middle of described.
On the end face of rotating ring mechanical seal device fluid dynamic pressure groove can be set as required in the middle of described.
The present invention has following characteristics:
1. the seal face relative rotation speed is adjustable;
2. sealed generating unit speed does not directly determine the seal face relative rotation speed;
3. make mechanical seal of high speed contact-type and low speed non-contact mechanical seal have higher stability.
Description of drawings
Fig. 1 is Chinese patent 02146449.9 disclosed a kind of double helix angle three-dimensional spiral groove end-face structure schematic representation.
Fig. 2 is Chinese patent 02132978.8 disclosed a kind of spiral chute end-face structure schematic representation by the angular microflute group composition.
Fig. 3 is that the rotating ring driving mode is a contact-type in the middle of the present invention, and activation point is positioned at a kind of structural representation of ring body outside diameter.
Fig. 4 is that the rotating ring driving mode is a contact-type in the middle of the present invention, and activation point is positioned at a kind of structural representation of ring body internal side diameter.
Fig. 5 is that the rotating ring driving mode is contactless a kind of structural representation in the middle of the present invention.
Fig. 6 is a kind of structural representation on the end face of rotating ring both sides in the middle of end face shallow slot of the present invention is positioned at.
Fig. 7 is a kind of structural representation that end face shallow slot of the present invention is positioned at.
Fig. 8 is a rotating ring and with a kind of structural representation on the anchor ring of middle rotating ring one side end face pairing in the middle of end face shallow slot of the present invention is positioned at.
The symbol implication is as follows in the accompanying drawing:
R
1---end face fluid dynamic pressure groove inside radius.
R
2---end face fluid dynamic pressure groove outer radius.
h
1---end face fluid dynamic pressure groove high pressure side groove depth.
h
2---end face fluid dynamic pressure groove low voltage side groove depth.
S
A1---end face fluid dynamic pressure groove major trough wall molded lines.
S
A2---the secondary cell wall molded lines of end face fluid dynamic pressure groove.
A---end face has the groove district.
B---sealing weir.
C---sealing dam.
ω
1---the rotating ring angular velocity of rotation.
H---upstream (high pressure side).
L---downstream (low voltage side).
Embodiment
Below in conjunction with embodiment the present invention is analyzed.
The concrete enforcement of the present invention is of a great variety, at this different analyzing examples explanations in position of fluid dynamic pressure groove is set according to central ring driving mode, activation point and end face.
Embodiment 1: consult Fig. 3
Fig. 3 is the structural representation of the embodiment of the invention 1.This centre rotating ring mechanical seal device comprises stationary ring 1, middle rotating ring 2, middle rotating ring actuator 3, rotating ring 4, round section joint ring 5, axle sleeve 6, tolerance ring 7, clamping sleeve 8, throw-out collar 9, spring 10, stop pin 11, stationary seat 12 etc.The characteristics of present embodiment are: middle rotating ring directly contacts with actuator 3, and is driven, and activation point is in the outside diameter of seal face.
According to Fig. 3, middle rotating ring links to each other with power source, and directly drives middle rotating ring at outside diameter, and the rotating speed of middle rotating ring is influenced by actuator 3 power source speed and its middle gear.Stationary ring 1, middle rotating ring 2 and rotating ring 4 are face-to-face coaxial line and install.Rotating ring circumferentially is fixed together with sealed axle by axle sleeve 6, tolerance ring 7, clamping sleeve 8, and use round section joint ring 5 to prevent the generation of leaking between contact surface, stationary ring is by throw-out collar 9, spring 10, stop pin 11, circumferentially be fixed together with stationary seat 12, middle axial rotary is positioned between rotating ring and the stationary ring, forms one group of seal face F between stationary ring and the middle rotating ring
1, form another group seal face F between middle rotating ring and the rotating ring
2It is ω that sealed set main shaft rotating speed equals the rotating ring rotating speed
1, middle rotating ring rotating speed is ω
2
Between two seal faces or relative rotational can be calculated as follows:
ω
F1=ω
2(1) formula
ω
F2=| ω
1± ω
2| (2) formula
ω
F1, ω
F2Represent seal face F respectively
1, F
2Between relative rotational.
For slow-speed of revolution unit:
Suppose: ω
1=50 (rpm)
Variable because of the rotating speed of middle rotating ring 2, it can be adjusted into: ω
2=10000 (rpm)
Then:
By (1) formula: ω
F1=10000 (rpm)
By (2) formula: ω
F2=10050 (rpm), or ω
F2=9950 (rpm)
As seen, only be the unit of 50 (rpm) for sealed axle rotating speed, the rotating speed by rotating ring 2 in the middle of use and suitable the adjustment can make its seal face F
1, F
2All obtain sufficiently high relative rotational.
For high rotating speed unit:
Suppose: ω
1=16000 (rpm)
Variable because of the rotating speed of middle rotating ring 2, it can be adjusted into: ω
2=8000 (rpm)
Then:
By (1) formula: ω
F1=8000 (rpm)
By (2) formula: ω
F2=8000 (rpm) (get ω
1, ω
2In the same way)
As seen, be the unit of 15000 (rpm) for sealed axle rotating speed, the rotating speed by rotating ring 2 in the middle of use and suitable the adjustment can make its seal face F
1, F
2Relative rotational significantly descend.If the quantity of rotating ring 2 in the middle of increasing, then the relative rotational of seal face will further descend.
In more than calculating, the concrete numerical value of rotating speed does not have certain sense, only is seal face F behind the rotating ring in the middle of the explanation adding
1, F
2Between the variation of relative rotational.
Embodiment 2: consult Fig. 4
Fig. 4 is the structural representation of the embodiment of the invention 2.Its sealing configuration and key technology require with embodiment 1 basic identical, and main difference is in embodiment 2, and the activation point of middle rotating ring 2 is located at internal side diameter, seal face F
1, F
2Between calculating and the situation of change of relative rotational identical with embodiment 1.
Embodiment 3: consult Fig. 5
Fig. 5 is the structural representation of the embodiment of the invention 3.Its key feature is that middle rotating ring 2 does not directly contact with middle rotating ring actuator 3, the driving of rotating ring 2 in the middle of realizing by non-contacting mode.Seal face F
1, F
2Between calculating and the situation of change of relative rotational identical with embodiment 1.
Embodiment 4: consult Fig. 6
Fig. 6 is the structural representation of the embodiment of the invention 4.Its key feature is: on middle rotating ring 2 both sides end faces fluid dynamic pressure groove is set.Seal face F
1, F
2Between calculating and the situation of change of relative rotational identical with embodiment 1.
Embodiment 5: consult Fig. 7
Fig. 7 is the structural representation of the embodiment of the invention 5.Its key feature is: on the sealing surface that cooperates with middle rotating ring 2 both sides end faces fluid dynamic pressure groove is set.Seal face F
1, F
2Between calculating and the situation of change of relative rotational identical with embodiment 1.
Embodiment 6: consult Fig. 8
Fig. 8 is the structural representation of the embodiment of the invention 6.Its key feature is: the fluid dynamic pressure groove of one group of seal face is arranged on the middle rotating ring 2, and fluid dynamic pressure groove of another group seal face is arranged on the sealing surface that cooperates with middle rotating ring 2.Seal face F
1, F
2Between calculating and the situation of change of relative rotational identical with embodiment 1.
In above analysis, the driving mode of rotating ring 2 in the middle of focusing on embodying, activation point, to the influence of sealing surface relative rotation speed, this is because the purpose of rotating ring 2 is exactly will adjust the relative rotation speed of seal face to reasonable range in the middle of adding, and breaks traditional situation that sealed axle rotating speed is the sealing surface relative rotation speed.In order more clearly to describe key problem, all only relate to the single-stage sealing configuration among the above embodiment, and in actual use, the sealing total arrangement can have multiple pattern as required as labyrinth (more than the two-stage) in the middle of: mechanical single seal, double seals, tandem seal (more than the two-stage), the series connection band, also can follow other seal style composition combined labyrinth and carbon gland such as floating-ring seal, carbocyclic ring sealing, labyrinth seal.
Claims (15)
1. rotating ring mechanical seal device in the middle of a kind, form by the stationary ring that has seal face (1), the middle rotating ring (2) that has seal face, middle rotating ring actuator (3), the rotating ring (4) and other correlated parts that have a seal face, stationary ring (1) is face-to-face installation with middle rotating ring (2), middle rotating ring (2) with the seal face of rotating ring (4), can directly fit between the seal face, also can separate in a very little gap.It is characterized in that: the middle rotating ring (2) that between stationary ring (1) and rotating ring (4), is placed with the rotating speed adjustable control.
2. rotating ring mechanical seal device in the middle of according to claim 1 is characterized in that: the rotating speed size of middle rotating ring (2) is more than or equal to zero, turns to rotating ring to turn in the same way or oppositely.
3. according to claim 1,2 described in the middle of the rotating ring mechanical seal device, it is characterized in that: the number of middle rotating ring (2) is for more than or equal to arbitrary integer of 1.
4. according to claim 1,2,3 described in the middle of the rotating ring mechanical seal device, it is characterized in that: the power source of middle rotating ring (2) can be sealed unit, also can be other additionaling power source.
5. according to claim 1,2,3,4 described in the middle of the rotating ring mechanical seal device, it is characterized in that: the driving mode of middle rotating ring (2) can be a contact-type, also can be contactless.
6. according to claim 1,2,3,4,5 described in the middle of the rotating ring mechanical seal device, it is characterized in that: the activation point of middle rotating ring (2) can be on inside and outside anchor ring, or any one position of middle rotating ring ring body.
7. according to claim 1,2,3,4,5,6 described middle rotating ring mechanical seal device, it is characterized in that: form one group of seal face between stationary ring (1) and the middle rotating ring (2), form another group seal face between middle rotating ring (2) and the rotating ring (4).
8. according to claim 1,7 described middle rotating ring mechanical seal device is characterized in that: in every group of seal face, can or on two end faces fluid dynamic pressure groove be set simultaneously at one, or two end faces are not provided with fluid dynamic pressure groove.
9. according to claim 1,8 described in the middle of the rotating ring mechanical seal device, it is characterized in that: the groove depth of the fluid dynamic pressure groove that is provided with on the end face can be that deep trouth also can be a shallow slot, and its scope is between 0.1 micron～3 millimeters.
10. according to claim 1,8,9 described in the middle of the rotating ring mechanical seal device, it is characterized in that: the grooved of the fluid dynamic pressure groove that is provided with on the end face can be spiral chute, arc groove, "T"-shaped groove, straight-line groove, also can be the combination of various grooveds.
11. according to claim 1,7 described middle rotating ring mechanical seal device, it is characterized in that: the stationary ring (1) of middle rotating ring (2) and both sides thereof and rotating ring (4) are formed primary seal.
12. according to claim 1,7,11 described middle rotating ring mechanical seal device, it is characterized in that: the layout of sealing can be the single-stage sealing, also can be tandem seal or double seals.
13. according to claim 1,7,11,12 described middle rotating ring mechanical seal device is characterized in that: in the multi-stage sealed layout, can be the combination seal that middle rotating ring sealing forms with other form motive sealing.
14. rotating ring mechanical seal device in the middle of according to claim 1, it is characterized in that: sealed medium and employed obstruction fluid can be that gas also can be liquid.
15. the rotating ring mechanical seal device is characterized in that: can be that mechanical seal with inward leakage also can mechanical seal with outward leakage in the middle of according to claim 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010144528A CN101806362A (en) | 2010-04-12 | 2010-04-12 | Mechanical sealing device of middle rotating ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010144528A CN101806362A (en) | 2010-04-12 | 2010-04-12 | Mechanical sealing device of middle rotating ring |
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| Publication Number | Publication Date |
|---|---|
| CN101806362A true CN101806362A (en) | 2010-08-18 |
Family
ID=42608270
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010144528A Pending CN101806362A (en) | 2010-04-12 | 2010-04-12 | Mechanical sealing device of middle rotating ring |
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|---|---|
| CN (1) | CN101806362A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102174963A (en) * | 2011-02-25 | 2011-09-07 | 西华大学 | Spherical mechanical sealing device |
| CN102829163A (en) * | 2011-06-17 | 2012-12-19 | 哈米尔顿森德斯特兰德公司 | Integrated end face seal removal apparatus |
| CN103375592A (en) * | 2012-04-24 | 2013-10-30 | 西华大学 | External driving type middle rotating ring mechanical seal with speed change gear |
| CN103383003A (en) * | 2012-05-02 | 2013-11-06 | 西华大学 | External drive type mechanical seal of middle rotating ring |
| CN103383004A (en) * | 2012-05-02 | 2013-11-06 | 西华大学 | Self-driven middle rotating ring mechanical seal with speed variator |
| CN103697170A (en) * | 2012-09-28 | 2014-04-02 | 西华大学 | Mechanical sealing device with self supporting type middle differential ring |
| CN104455456A (en) * | 2014-11-05 | 2015-03-25 | 中国航空动力机械研究所 | Fluid power sealing device |
| CN104896099A (en) * | 2015-05-25 | 2015-09-09 | 浙江工业大学 | Gas lubrication cluster spiral groove end face mechanical sealing structure |
| CN106812947A (en) * | 2017-02-14 | 2017-06-09 | 四川日机密封件股份有限公司 | The non-contacting mechanical seal ring of combined fluid dynamic pressure groove |
| CN108916383A (en) * | 2015-12-03 | 2018-11-30 | Nok株式会社 | Axis and seal construction |
| CN109027244A (en) * | 2018-09-20 | 2018-12-18 | 温州市天成密封件制造有限公司 | A kind of mechanically-sealing apparatus |
-
2010
- 2010-04-12 CN CN201010144528A patent/CN101806362A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102174963A (en) * | 2011-02-25 | 2011-09-07 | 西华大学 | Spherical mechanical sealing device |
| CN102829163A (en) * | 2011-06-17 | 2012-12-19 | 哈米尔顿森德斯特兰德公司 | Integrated end face seal removal apparatus |
| CN103375592A (en) * | 2012-04-24 | 2013-10-30 | 西华大学 | External driving type middle rotating ring mechanical seal with speed change gear |
| CN103383003A (en) * | 2012-05-02 | 2013-11-06 | 西华大学 | External drive type mechanical seal of middle rotating ring |
| CN103383004A (en) * | 2012-05-02 | 2013-11-06 | 西华大学 | Self-driven middle rotating ring mechanical seal with speed variator |
| CN103697170A (en) * | 2012-09-28 | 2014-04-02 | 西华大学 | Mechanical sealing device with self supporting type middle differential ring |
| CN104455456A (en) * | 2014-11-05 | 2015-03-25 | 中国航空动力机械研究所 | Fluid power sealing device |
| CN104896099A (en) * | 2015-05-25 | 2015-09-09 | 浙江工业大学 | Gas lubrication cluster spiral groove end face mechanical sealing structure |
| CN108916383A (en) * | 2015-12-03 | 2018-11-30 | Nok株式会社 | Axis and seal construction |
| CN106812947A (en) * | 2017-02-14 | 2017-06-09 | 四川日机密封件股份有限公司 | The non-contacting mechanical seal ring of combined fluid dynamic pressure groove |
| CN109027244A (en) * | 2018-09-20 | 2018-12-18 | 温州市天成密封件制造有限公司 | A kind of mechanically-sealing apparatus |
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Open date: 20100818 |