CN205388050U - High pressure resistant rinse -system with many sets of mechanical seal - Google Patents
High pressure resistant rinse -system with many sets of mechanical seal Download PDFInfo
- Publication number
- CN205388050U CN205388050U CN201620202200.XU CN201620202200U CN205388050U CN 205388050 U CN205388050 U CN 205388050U CN 201620202200 U CN201620202200 U CN 201620202200U CN 205388050 U CN205388050 U CN 205388050U
- Authority
- CN
- China
- Prior art keywords
- mechanical seal
- pressure
- pump case
- pump
- sealing gland
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Landscapes
- Sealing Devices (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The utility model provides a high pressure resistant rinse -system with many sets of mechanical seal, by the pump case, the centrifugal pump that impeller and pump shaft constitute, the pump case is stretched out through high -pressure side mechanical seal to pump shaft one end, and through the coupling joint motor, this end that the shaft coupling is connected to the pump shaft is through setting up the bearing position on the bearing frame, the outside cover of pump shaft has the axle sleeve, the axle sleeve passes through axle sleeve sealing washer and pump shaft fixed connection, the axle sleeve lie in between pump case and the bearing the outside through by first to a N sealing gland from beginning to end sealed link to each other be formed with first to a N buffer solution cavity, each sealing gland high -pressure side all sets up a set ofly and mechanical seal axle sleeve sealing connection, each sealing gland's inlet is equipped with the liquid outlet of the accumulator of buffer solution through feed liquor tube coupling inside, the inlet of accumulator is connected to each sealing gland's liquid outlet through a liquid outlet pipe, the bottom and pump case sealing connection that are close to the sealing gland of pump case. The utility model discloses can increase substantially the high pressure resistant ability of present centrifugal pump.
Description
Technical field
This utility model relates to the axle envelope rinse-system of a kind of centrifugal pump.What particularly relate to that a kind of multistage many sets form pressure decline step by step along the close series connection of installation tool has the high pressure resistant rinse-system overlapping mechanical seal more.
Background technology
API682 standard Appendix D Plays at centrifugal pump and impeller pump gland seal system seals the pressure of 52,53 flushing scheme internal system circulation of fluids and has nothing in common with each other, being the prior art of 52 flushing scheme as depicted in figs. 1 and 2, two sets are without pressure and the buffer that can circulate towards the liquid between back of the body configuration mechanical seal.Wherein,
Fig. 1 and Fig. 2 is the prior art 2CW-CW collection wet sealing of dress double-contact with buffer, it is that media end mechanical sealing friction pairs is mainly cooled down by its effect without pressure (with atmosphere) and wash buffer system principle sketch (Fig. 1) that can circulate and internal construction details schematic diagram (Fig. 2).In the API682 standard of 2004 editions in the 115th page ' A.4 the explanation to Sealing selection flow sheet 7-table 9 ' the 117th page ' A.4.11 scheme 52 ' content:
Scheme 52 or layout 2 are not pressurized double; two envelope system for not allowing the operating mode to atmospheric side leakage occur.Scheme 52 system is injected wherein buffer fluid by double containment and is formed.Sealing storage tank built with buffer fluid, the outlet of hermetically sealed can communicates with exhaust apparatus, thus keeping the pressures near atmospheric power of buffer fluid.The result of inner seal leakage is that dielectric leakage is in buffer.Actually always have certain leakage to occur.
Scheme 52 Use Limitation fruit in vapour pressure is higher than the non-polymeric clean medium of buffer fluid pressure is best.There is flash distillation in this kind of medium, steam escapes into exhaust apparatus in hermetically sealed can.If the steam pressure of medium is lower than buffer fluid or seals pressure of storage tank, the fluid leaked out is by maintenance liquid and can pollute buffer fluid.
If inner seal leakage can not find in time, then a large amount of process fluids will replace buffer fluid, be completely filled with medium between making two to seal.In this case, outer side seal leakage can cause medium effusion air.
Scheme 52 should not be used in dirty or easy polymerisation medium.It is considered as selection scheme 53 in this case.
Fig. 3 and Fig. 4 is the 3CW-FB configuration of 53 flushing scheme, between two set mechanical seals with higher than the pressure of pump chamber material and can circulate intercept liquid sealflush system principle sketch (Fig. 3) and internal construction details schematic diagram (Fig. 4) towards back of the body collection dress double-contact is wet, this system has two effects, one effect is that media end mechanical sealing friction pairs is cooled down, another effect is once media end mechanical seal leakage, the direction of leakage must be intercept in the material that liquid leaks into pump chamber, it will not be the environment that depollutes in the air outside material from leakage then leaks into atmosphere end mechanical seal in obstruct liquid.117th page of ' A.4.12 scheme 53a, 53b, 53c ' content in 115th page ' A.4 the explanation to Sealing selection flow sheet 7-table 9 ' in the API682 standard of 2004 editions:
Scheme 53 or the 3 double; two envelope systems of pressurization of arranging are not for allowing the operating mode to atmospheric side leakage.Scheme 53a system is by double; two envelopes and injects obstruction fluid therein and forms.Blocking fluid in sealing storage tank, the pressure of this storage tank is higher than the pressure about 1.5 bar (23psi) in pump seal chamber.The result of inner seal leakage is to block fluid to leak in medium, in actual applications, always certain leakage occurs.If the change of annular seal space pressure is obvious or more than 500psig, utilizes differential pressure regulator to make external seal pressure more than pressure of seal cavity of pump 20-25psi, can reduce external seal stress.
Scheme 53b is also the double; two envelope of pressurization, and it and scheme 53a are the difference is that the pressure utilizing air pocket type accumulator to produce is to maintain the circulation of sealing.
Scheme 53c is also the double; two envelope of pressurization, and it is on the annular seal space pressure adopting piston accumulator to make pressure maintain.
Compared with scheme 52, scheme 53 be more used in dirty, there is abrasion or easily in polymerisation medium.In this environment, if selecting scheme 52, it is possible to seal face can be damaged or bring problem to cushioning fluid systems.Two shortcomings of scheme 53 must take into: first, always has certain obstruction fluid and leak in medium time actually used.Generally, this leakage is small, and its leakage rate can be monitored by observation hermetically sealed can liquid level.Therefore medium must be able to allow that blocking fluid produces a small amount of pollution to it.Second, scheme 53 system depends on the convenient pressure of hermetically sealed can.If hermetically sealed can pressure declines, there is the scheme that is similar to 52 by starting or is not pressurized the working condition of double; two envelope in system, it is impossible to realize fully sealing.Particular with the passage of time, the leakage direction of inner seal will occur reversely, block fluid and is polluted by process fluid, problem occur then, including the seal failure being likely to occur.
No matter being select single end face or double mechanical seal, no matter be also adopt any flushing scheme in API682 standard, the gross pressure of centrifugal pump is all individually completed by a set of mechanical seal.There is nothing but following three situation:
1, single mechanical end face seal: high-pressure material end and low pressure atmosphere end only have unique a set of mechanical seal to intercept (layout 1 in API682), so only this set mechanical seal undertakes the total pressure difference of whole centrifugal pump.
2,52 flushing scheme in API682 standard are adopted: owing to two overlap mechanical seal (such as Fig. 2, media end mechanical seal and atmosphere end mechanical seal) between buffer fluid without pressure (with atmosphere), so the media end mechanical seal of only single set undertakes the total pressure difference (layout 2 in API682) of whole centrifugal pump.
3,53 flushing scheme in API682 standard are adopted: owing to two overlap mechanical seal (such as Fig. 4, media end mechanical seal and atmosphere end mechanical seal) between the pressure of barrier fluid higher than the pressure (layout 3 in API682) of high-pressure side pump chamber material, so what media end mechanical seal bore is the pressure differential between barrier fluid and high-pressure side pump chamber material；Owing to the pressure of barrier fluid is higher than the pressure of pump chamber material, and only have a set of atmosphere end mechanical seal between the barrier fluid of high pressure and the air of low pressure and intercept, so this set of mechanical seal carries the pressure differential bigger than the gross pressure of whole centrifugal pump.
These above-mentioned problems govern centrifugal pump all the time and bear incessantly high pressure, because mechanical seal in the prior art is the link that in centrifugal pump, all parts are the weakest, if not improving the bearing capacity of mechanical seal, pump case is made thick again, it is also of no avail that the intensity of other part is made high again, once the material pressure in centrifugal pump has exceeded the bearing capacity of single set mechanical seal, this centrifugal pump is just leakage at once, if centrifugal pump have leaked just cannot normal operation, cause even stopping production.
Summary of the invention
Technical problem to be solved in the utility model be to provide a kind of can be greatly improved centrifugal pump bear pressure ability there is the high pressure resistant rinse-system overlapping mechanical seal more.
nullThis utility model be the technical scheme is that a kind of high pressure resistant rinse-system with the mechanical seal of many sets，Include by pump case、It is arranged on the impeller in pump case and one end connects the centrifugal pump that the pump shaft of described impeller is constituted，The other end of described pump shaft stretches out pump case by the high-pressure side mechanical seal being arranged on described pump case shaft outlet hole，Termination connects the motor for driving impeller to rotate by shaft coupling，Described pump shaft connects this end of shaft coupling the bearing location by being arranged on bearing block，And the outside of described pump shaft is cased with axle sleeve，Described axle sleeve is connected by sleeve sealing circle and described pump shaft are fixing，Described axle sleeve passes through in the outside between described pump case and bearing to be sealed by the first to n-th sealing gland head and the tail to be connected to form the first to n-th buffer cavity，Each sealing gland on high-tension side axis hole place is both provided with one group of mechanical seal being connected with described sleeve sealing，The inlet of each sealing gland connects the inside liquid outlet equipped with the accumulator of buffer by a water influent pipeline correspondence，The liquid outlet of each sealing gland connects the inlet of described accumulator by a drain pipe road correspondence，It is tightly connected with described pump case near the bottom of this sealing gland of pump case.
Pressure in described N number of buffer cavity by the highest the 1st buffer cavity of the minimum N buffer cavity of the pressure being close to bearing to the pressure closing on pump case for increase successively.
In described N number of buffer cavity, often pressure reduction between adjacent two buffer cavitys is:
PAdjacent=PThing÷N
PAdjacent: the pressure differential between adjacent two accumulators, is also the pressure differential born of every suit mechanical seal.
The described stationary ring in the on high-tension side mechanical seal of each sealing gland constitutes friction pair with rotating ring, and wherein, described stationary ring is fixing with corresponding sealing gland to be connected, and described rotating ring is fixing with described axle sleeve to be connected.
Pressure medium in described pump case is less than the pressure of buffer in the first buffer cavity adjacent with pump case.
Pressure medium in described pump case is more than the pressure of buffer in the first buffer cavity adjacent with pump case.
Described N is the integer more than 2.
Of the present utility model have the high pressure resistant rinse-system overlapping mechanical seal more, it is possible to increases substantially the high voltage bearing ability of present centrifugal pump.Have the effect that
1, (P is annular seal space pressure to the PV value of effective reduction mechanical sealing friction pairs, V is the relative linear velocity between the dynamic and static ring of mechanical seal, PV value is both products, and its value is more low for more high service life, is the important indicator weighing mechanical seal service life).
2, in API682, the element such as accumulator in 52 and 53 flushing scheme is all the basic configuration of international standard, so any prior art equipment need not be changed, adjust the pressure of accumulator only in accordance with this utility model and just can allow the pressure bearing power increase one times of existing centrifugal pump.
3, theoretically, if pump shaft long enough, say, that have enough spaces can arrange the mechanical seal of abundant quantity, then, no matter how high the pressure of material have, as long as we increase the quantity of mechanical seal just can meet the requirement of chemical process high-pressure material.
4, using bearing housing as a certain annular seal space (such as Fig. 5), can not only make bearing housing one chamber dual-purpose, and can also effectively shorten the distance of the strong point and stress point.
5, the accumulator adopted is standard component, so facilitating implementation.
6, simple in construction, takes up room little, it is simple to operation, production cost is low.
7, there is this utility model, the function of the never reduction pressure differential of mistake that from then on rinse-system of axle envelope is just many before.
8, there is this utility model just to have design, manufactured the means of high pressure centrifugal pump, there has also been the artificial effective means improving mechanical seal service life by reducing PV value simultaneously.
As long as 9, application this utility model can be changed reaching arranging 2 and arranging the purpose of 3 in API682 standard at the media end of high-pressure material while the high-voltage resistance capability and prolonged mechanical that improve centrifugal pump seal service life.
As long as 10 are changed, at the media end of high-pressure material, each location that just can accomplish in API682 standard.
Accompanying drawing explanation
Fig. 1 is prior art 52 standard flush scenario-frame schematic diagram；
Fig. 2 is the internal structure of prior art 52 standard flush scheme
Fig. 3 is prior art 53 standard flush scenario-frame schematic diagram；
Fig. 4 is the internal structure schematic diagram of prior art 53 standard flush scheme；
Fig. 5 is high pressure resistant flushing scheme structural representation of the present utility model；
Fig. 6: be the internal structure schematic diagram of high pressure resistant flushing scheme of the present utility model.
In figure
A: the pressure position B at high-pressure material end place: the pressure position at air low-pressure end place
1: pump shaft 2: axle sleeve
31～3N: the first sealing gland～the N sealing gland 4: high-pressure side mechanical seal
5: mechanical seal 6: impeller
7: pump case 8: bearing block
9: shaft coupling 10: motor
11: bearing the 121～12N: the first buffer cavity～the N buffer cavity
13: drain pipe road 14: water influent pipeline
15: accumulator
Detailed description of the invention
Below in conjunction with embodiment and accompanying drawing, the high pressure resistant rinse-system with the mechanical seal of many sets of the present utility model is described in detail.
nullSuch as Fig. 5、Shown in Fig. 6，Of the present utility model have the high pressure resistant rinse-system overlapping mechanical seal more，Include by pump case 7、It is arranged on the impeller 6 in pump case 7 and one end connects the centrifugal pump that the pump shaft 1 of described impeller 6 is constituted，The other end of described pump shaft 1 stretches out pump case 7 by the high-pressure side mechanical seal 4 being arranged on described pump case 7 shaft outlet hole，Termination connects the motor 10 for driving impeller 6 to rotate by shaft coupling 9，Described pump shaft 1 is connected this end of shaft coupling 9 and is positioned by the bearing 11 being arranged on bearing block 8，And the outside of described pump shaft 1 is cased with axle sleeve 2，Described axle sleeve 2 is connected by sleeve sealing circle 3 is fixing with described pump shaft 1，Described axle sleeve 2 passes through by the first to n-th sealing gland 31 in the periphery between described pump case 7 and bearing 11、32、…、3N head and the tail seal and have been connected to form the first to n-th buffer cavity 121、122、…12N，Described N is the integer more than 2.Each sealing gland on high-tension side axis hole place is both provided with one group of mechanical seal 5 being tightly connected with described axle sleeve 2, the inlet of each sealing gland connects the inside liquid outlet equipped with the accumulator 15 of buffer by a water influent pipeline 14 is corresponding, the liquid outlet of each sealing gland, by the corresponding inlet connecting described accumulator 15 in a drain pipe road 13, is tightly connected with described pump case 7 near the bottom of this sealing gland 31 of pump case 7.
Pressure in described N number of buffer cavity 121,122 ... 12N by the 1st the highest for the minimum N buffer cavity 12N of the pressure being close to bearing 11 to the pressure closing on pump case 7 buffer cavity 121 for increase successively.In described N number of buffer cavity 121,122 ... 12N, often pressure reduction between adjacent two buffer cavitys is: PAdjacent=PThing÷ N, wherein
PAdjacent: the pressure differential between adjacent two accumulators, is also the pressure differential born of every suit mechanical seal.
Stationary ring in the on high-tension side mechanical seal 5 of each described sealing gland constitutes friction pair with rotating ring, and wherein, described stationary ring is fixing with corresponding sealing gland to be connected, and described rotating ring is fixing with described axle sleeve 2 to be connected.
Pressure medium in described pump case 7 is less than the pressure of buffer in the first buffer cavity 121 adjacent with pump case 7, and now this buffer reforms into obstruct liquid.Or, the pressure medium in described pump case 7 is more than the pressure of buffer in the first buffer cavity 121 adjacent with pump case 7.
Of the present utility model have the high pressure resistant rinse-system overlapping mechanical seal more, can make in pump case and namely two sets of contiguous bearing are different from, towards the fluid between back of the body configuration mechanical seal, the no pressure rinsing 52 schemes in API682 standard, also different from 53 schemes of rinsing in API682 standard with the pressure more than material.But between back of the body configuration mechanical seal, it is serially connected with the mechanical seal towards back of the body configuration of many sets at two sets, form multiple closing chamber, many sets are adjusted to marginal meansigma methods towards the pressure between back of the body configuration mechanical seal, if what install is double mechanical seal, two friction pairs allowing for mechanical seal each undertake the half pressure of gross pressure, two friction pairs allowing mechanical seal each share total pressure differential, reduce the purpose of mechanical seal load.
Of the present utility model have the high pressure resistant rinse-system overlapping mechanical seal more, each buffer cavity 121～N configures an accumulator 15, allow the direction along high-pressure material end towards low pressure atmosphere end, in each independent buffer cavity, the pressure of the buffer fluid of 121～N successively decreases successively so that often set mechanical seal 5 can undertake the Pressure Drop of each of which.Pressure Drop total for centrifugal pump just can be resolved into the Pressure Drop of some local, say, that the Pressure Drop sum of these local is exactly the total pressure drop of this centrifugal pump.
If pump shaft long enough, say, that have enough spaces can arrange the mechanical seal of abundant quantity, then, no matter how high the pressure of material have, as long as the quantity increasing mechanical seal just can meet the requirement of chemical process high-pressure material.
Then just have: N (quantity of mechanical seal) >=P (material pressure Mpa)/10 (the limiting pressure Mpa that often set mechanical seal should be born).
The quantity that install mechanical seal just can be calculated, such that it is able to reserve the installing space of necessity by above formula.
Do not allow often set mechanical seal reality all utmost carrying ability pressure the service life in order to ensure mechanical seal, so it is also contemplated that the safety factor of necessity during design.
How to configure the quantity of mechanical seal according to material pressure, this utility model just can draw equation below:
PThing=(PGo out+PEnter)÷2
PGo out: the outlet pressure (Mpa) of centrifugal pump.
PEnter: the inlet pressure (Mpa) of centrifugal pump.
PThing: the annular seal space pressure (Mpa) of the carried material of centrifugal pump.
If the inlet pressure of centrifugal pump is more than 3Mpa, the material pressure of annular seal space just can be estimated with above formula, otherwise needs one piece of Pressure gauge of installation that the force value in mechanical seal chamber is carried out actual measurement, and this method is more reliable.
The quantity that should configure mechanical seal is:
N=PThing(Mpa) ÷ 10 (Mpa) × k (set)
K: safety factor, span: 0.5 < k < 1, generally take 0.7
N: should configure the quantity of mechanical seal, takes the positive integer more than value of calculation.Such as: value of calculation is 2.1 or 2.9 all to take 3.
The quantity that configure accumulator can be calculated by equation below:
M=N-1
M: the quantity that accumulator should configure, is also the quantity of the quantity of buffer blood circulation and mechanical seal cover.
The pressure that each accumulator should set can be calculated by equation below:
Pxi=PAdjacent× i=(PThing÷N)×i
Wherein: PAdjacent=PThing÷N
PAdjacent: the pressure differential between adjacent two accumulators；Also it is the pressure differential (Mpa) born of every suit mechanical seal.
I: the sequence number that any one accumulator, any a set of mechanical seal, any one sealing gland, any one buffer flow to.
Pxi: sequence number is the pressure (Mpa) that accumulator of i should set.
If two sets mechanical seal (i.e. a set of double mechanical seal), only one of which accumulator, according to this utility model technology, the pressure (ignoring atmospheric pressure) that this accumulator should set:
PX2=PThing(Mpa)÷2
PX2: the pressure (Mpa) that accumulator should set；Also it is this two sets pressure differential (Mpa) of each bearing of mechanical seal.
When the quantity of application this utility model and mechanical seal is overlapped more than three, just the pressure of the accumulator near material side can be adjusted the pressure more than annular seal space material, fluid inside this accumulator just becomes intercepting liquid, its leakage direction can only be leak inside material, it is possible to completes API682 standard lining and puts the purpose of 3.The pressure of other accumulator is set still according to this utility model method, just pressure differential can be reduced step by step, thus just can reduce the pressure load of every grade of mechanical seal, can service life of effective prolonged mechanical sealing, also can complete API682 standard lining and put the task of 3.
If the Pressure Drop that every suit mechanical seal is carried is set to constant, then increase mechanical seal progression (increasing the quantity of mechanical seal and accumulator), just can improve the high-voltage resistance capability of centrifugal pump.
If the pressure differential between material and air is set to constant, then increase mechanical seal progression (increasing the quantity of mechanical seal and accumulator), the service life of effective prolonged mechanical sealing just artificially can be carried out by reducing the PV value of mechanical sealing friction pairs.
Claims (7)
- null1. one kind has the high pressure resistant rinse-system overlapping mechanical seal more，Include by pump case (7)、It is arranged on the impeller (6) in pump case (7) and one end connects the centrifugal pump that the pump shaft (1) of described impeller (6) is constituted，The other end of described pump shaft (1) stretches out pump case (7) by the high-pressure side mechanical seal (4) being arranged on described pump case (7) shaft outlet hole，Termination connects the motor (10) being used for driving impeller (6) to rotate by shaft coupling (9)，Described pump shaft (1) connects this end of shaft coupling (9) bearing (11) location by being arranged on bearing block (8)，And the outside of described pump shaft (1) is cased with axle sleeve (2)，Described axle sleeve (2) is connected by sleeve sealing circle (3) and described pump shaft (1) are fixing，It is characterized in that，Described axle sleeve (2) passes through by the first to n-th sealing gland (31 in the outside being positioned between described pump case (7) and bearing (11)、32、…、3N) head and the tail seal and have been connected to form the first to n-th buffer cavity (121、122、…12N)，Each sealing gland on high-tension side axis hole place is both provided with one group of mechanical seal (5) being tightly connected with described axle sleeve (2)，The inlet of each sealing gland connects the inside liquid outlet equipped with the accumulator (15) of buffer by a water influent pipeline (14) is corresponding，The liquid outlet of each sealing gland is by the corresponding inlet connecting described accumulator (15) of a drain pipe road (13)，It is tightly connected with described pump case (7) near the bottom of this sealing gland (31) of pump case (7).
- 2. according to claim 1 have the high pressure resistant rinse-system overlapping mechanical seal more, it is characterized in that, the pressure in described N number of buffer cavity (121,122 ... 12N) by the 1st the highest for minimum N buffer cavity (12N) of the pressure being close to bearing (11) to the pressure closing on pump case (7) buffer cavity (121) for increase successively.
- 3. according to claim 2 have the high pressure resistant rinse-system overlapping mechanical seal more, it is characterised in that in described N number of buffer cavity (121,122 ... 12N), often pressure reduction between adjacent two buffer cavitys is:PAdjacent=PThing÷NPAdjacent: the pressure differential between adjacent two accumulators, is also the pressure differential born of every suit mechanical seal.
- 4. according to claim 1 have the high pressure resistant rinse-system overlapping mechanical seal more, it is characterized in that, the described stationary ring in the on high-tension side mechanical seal of each sealing gland (5) constitutes friction pair with rotating ring, wherein, described stationary ring is fixing with corresponding sealing gland to be connected, and described rotating ring is fixing with described axle sleeve (2) to be connected.
- 5. according to claim 1 have the high pressure resistant rinse-system overlapping mechanical seal more, it is characterized in that, the pressure medium in described pump case (7) is less than the pressure of first buffer cavity (121) the interior buffer adjacent with pump case (7).
- 6. according to claim 1 have the high pressure resistant rinse-system overlapping mechanical seal more, it is characterized in that, the pressure medium in described pump case (7) is more than the pressure of first buffer cavity (121) the interior buffer adjacent with pump case (7).
- 7. according to claim 1 have the high pressure resistant rinse-system overlapping mechanical seal more, it is characterised in that described N is the integer more than 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620202200.XU CN205388050U (en) | 2016-03-16 | 2016-03-16 | High pressure resistant rinse -system with many sets of mechanical seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620202200.XU CN205388050U (en) | 2016-03-16 | 2016-03-16 | High pressure resistant rinse -system with many sets of mechanical seal |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205388050U true CN205388050U (en) | 2016-07-20 |
Family
ID=56376321
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620202200.XU Withdrawn - After Issue CN205388050U (en) | 2016-03-16 | 2016-03-16 | High pressure resistant rinse -system with many sets of mechanical seal |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205388050U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673579A (en) * | 2016-03-16 | 2016-06-15 | 邢宇 | High-pressure-resistant washing system with multiple mechanical seals |
-
2016
- 2016-03-16 CN CN201620202200.XU patent/CN205388050U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105673579A (en) * | 2016-03-16 | 2016-06-15 | 邢宇 | High-pressure-resistant washing system with multiple mechanical seals |
| WO2017156933A1 (en) * | 2016-03-16 | 2017-09-21 | 邢宇 | High pressure resistant flushing system with multiple mechanical seals |
| CN105673579B (en) * | 2016-03-16 | 2018-12-11 | 天津长瑞大通流体控制系统有限公司 | High pressure resistant rinse-system with more set mechanical seals |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105673579B (en) | High pressure resistant rinse-system with more set mechanical seals | |
| CN105485038B (en) | A kind of double mechanical seal monitoring device of centrifugal fluid pump | |
| CN106949269A (en) | The double flexible pipe membrane pump check valves of high pressure and unidirectional valve group | |
| CN205388050U (en) | High pressure resistant rinse -system with many sets of mechanical seal | |
| US8720543B2 (en) | Device for passive pressure sealing | |
| CN203959096U (en) | Gas storage is observed well completion tubular column | |
| CN101737093A (en) | Annular brush sealer for turbine and turbine with the same | |
| CN101900212A (en) | High-pressure large-caliber duplex gathering ball valve | |
| CN102242714A (en) | Compound seal device of claw type dry vacuum pump | |
| CN103244699B (en) | Ultra-high pressure high flow topping up or pouring valve | |
| CN209354701U (en) | Ball-and-seat | |
| CN207470852U (en) | A kind of automatic unidirectional tapping valve | |
| CN208900339U (en) | A kind of plunger type reciprocating booster pump | |
| CN112282690A (en) | Rubber sleeve shoulder has protection architecture and high temperature and high pressure resistant expanding packer | |
| CN105215036A (en) | Bottle cleaning machine water diversion disk anti-rotation structure | |
| CN106337770A (en) | Pipeline power generating station | |
| CN207421341U (en) | A kind of air valve for examining air-tightness | |
| CN206320335U (en) | A kind of balanced three-way governing valve | |
| CN107840300A (en) | The operating method of supporting binary channels gyrator on a kind of fluid assembly and disassembly oil filling riser | |
| CN103352867B (en) | A kind of pump shaft sealing device | |
| CN104265233A (en) | Membrane expansion type packer | |
| CN203730392U (en) | Circulating seawater pump shaft sealing device | |
| CN202611654U (en) | Insertion sealing structure for water injection sand prevention well | |
| CN209278154U (en) | Turbocharging Anticorrosive pollution-discharge pump | |
| CN205714687U (en) | A kind of double flexible pipe membrane pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20160720 Effective date of abandoning: 20181211 |