CN102124227A - Ring seals for screw pump rotors - Google Patents
Ring seals for screw pump rotors Download PDFInfo
- Publication number
- CN102124227A CN102124227A CN2009801324611A CN200980132461A CN102124227A CN 102124227 A CN102124227 A CN 102124227A CN 2009801324611 A CN2009801324611 A CN 2009801324611A CN 200980132461 A CN200980132461 A CN 200980132461A CN 102124227 A CN102124227 A CN 102124227A
- Authority
- CN
- China
- Prior art keywords
- lip ring
- groove
- pump
- rotor
- pump rotor
- 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.)
- Pending
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0007—Radial sealings for working fluid
- F04C15/0011—Radial sealings for working fluid of rigid material
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/24—Fluid mixed, e.g. two-phase fluid
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
A pump rotor for a screw pump, comprises a shaft (42), a thread (44) on the shaft, the thread comprising a groove (48) disposed on an outer surface thereof, and a seal (50) disposed in the groove. The seal and the groove are configured to retain the seal in the groove while allowing radial displacement of the seal with respect to the thread as the pump rotor is deflected.
Description
Technical field
Theme relate generally to screw pump disclosed herein, and more particularly, relate to the lip ring that is used for screw pump rotor.
Background technique
In the exploration for oil gas, it is fine understanding that fluid (Oil, Water, Gas body and external solid) is transported to teleprocessing or the demand (be not near well source construction new facility) of storage the facility from Jing Yuan.Two screw pump is used to help the production of these well source fluid just day by day.The use of two screw pump makes it possible to improve the level of production by the pressure that reduces the Jing Yuan outlet port, and obtains bigger overall recovery by allowing lower final storage tank pressure from storage tank before abandoning producing.
Fig. 1 illustrates a kind of traditional two screw pump 10.This figure presents the main member with the diagram two screw pump simply, and should not be considered to limit by any way the present invention disclosed herein.As shown in the figure, two screw pump 10 typically has two rotors 12 and 14 that are arranged in the rotor bushing 19.Each rotor all has axle 18, and axle 18 has one or more groups the outward extending screw thread 20 at least a portion that is arranged on axle 18 length.Axle 18 axially extends in rotor bushing 19.Two rotors 12,14 are not in contact with one another, but their relative separately screw threads 20 be mutually around.Pump 10 will often be driven by the motor (not shown), and this motor makes rotor 12 and 14 rotations.Typically, second gear that the driving gear 22 on one of them engages on another makes that when pump motor made rotor 12 rotations, rotor 14 was with identical speed, but rotation in the opposite direction.In operation, the well source fluid that comprises granular material is sucked in the pump 10 at inlet 24 places.When rotor 12 and 14 rotations, the rotor chamber 26 that between adjacent screw thread 20, forms make the well source fluid along rotor shaft 18 towards the room of outlet 28 and move, this room of outlet 28 is points of rotor center place pressure maximum, and the well source fluid is finally discharged from the outlet 30 of pump 10 from this point.Rotor chamber 26 does not seal fully, but under normal operating conditions, is present between the rotor 12,14 and the normal clearance space between each rotor and rotor bushing 19 is transferred fluid filled.The liquid of the conveyance fluid in these clearance spaces partly is used to limit the leakage of fluid between adjacent chamber that is pumped.The quantity of the fluid that escapes back from the outlet side entrance of rotor is represented the slip-stream of pump, and known this slip-stream meeting reduces pump volumetric efficiency.As shown in Figure 2 with top explain such, can generating pump slip-stream (shown in the arrow among Fig. 2) between each rotor and rotor bushing 19.Other sliding path comprises between screw tip and the adjacent rotors and the slip between the face of screw thread 20.
Traditional twin-screw multiphase pump is current to face some challenges.At first, suppose that every grade of fixed pressure rises, along with total pressure rising increase in demand, rotor length increases, and causes the rotor displacement that increases under the pressure load of forcing.This skew causes the eccentric more aligning of rotor 12,14 in the rotor bushing 19, and this causes slip or contact excessive between rotor 12,14 and rotor bushing 19 often, and between rotor 12,14 or against the friction of rotor bushing 19.In addition, along with the increase of pump slip-stream, the sand grains that is collected in the slip-stream can cause interior erosion or the wearing and tearing that increase of pump owing to the phenomenon that is called as water-jet, particularly at the apex rotor place.This erosion or wearing and tearing can cause the deterioration of gap profile and the further increase of pump slip-stream.
Therefore need a kind of pump rotor of development, it minimizes or eliminates the pump slip-stream, causes a kind of multiphase pump with high pressure-charging difference of compact rotor length.In addition, improved sealing also will guarantee to reduce solid particle erosion or wearing and tearing in the gap between the edge of rotor and pump case.Also need to provide a kind of sealing system, it is durable, has improved pump performance, even and also can not cause any damage to pump after the sealing system wearing and tearing.
Summary of the invention
According to an embodiment disclosed herein, the pump rotor that is used for screw pump comprises axle, and screw thread on the axle and Sealing, this screw thread comprise setting groove on its outer surface, and Sealing is arranged in the groove.Sealing is from the starting point of screw thread of the end that the is arranged in axle screw thread that spirals.Groove and Sealing are sized to have the gap between them, and Sealing can radially be moved with respect to screw thread when pump rotor is offset.Groove and Sealing have formed mutual interlocking gear, so that Sealing is remained in the groove, allow that simultaneously Sealing moves radially with respect to screw thread when pump rotor is offset.
According to another embodiment disclosed herein, a kind of method that reduces the slip-stream in the screw pump is provided, screw pump have band low-pressure inlet and high-pressure outlet shell, be arranged on the lining of enclosure and be arranged on the rotor of bush inside, rotor have the axle and be arranged on the axle outer surface on screw thread, this method is included on the outer surface of screw thread and forms groove, and lip ring is set in groove, make lip ring outwards outstanding from groove, and lean against on the internal surface of lining of screw pump, thereby reduce from the slip-stream of high-pressure outlet to low-pressure inlet.Lip ring becomes with recess configurations Sealing is remained in the groove, allows Sealing moving radially with respect to screw thread when pump rotor is offset simultaneously.
According to another embodiment disclosed herein, two screw pump comprises shell with entrance and exit, be arranged on the lining of enclosure and be arranged on two rotors of bush inside.Each rotor includes axle, be arranged on screw thread on the part of outer surface of axle, be arranged in the groove on the outer surface of screw thread and the lip ring of groove, lip ring is configured to rotate with the axis, and outwards outstanding from groove, so that lean against on the internal surface of lining.Lip ring becomes with recess configurations Sealing is remained in the groove, allows Sealing moving radially with respect to screw thread when pump rotor is offset simultaneously.
Description of drawings
When the reference accompanying drawing is read following detailed description, will understand these and further feature, aspect and advantage of the present invention better, wherein similar label is represented similar parts in institute's drawings attached.
Fig. 1 illustrates traditional two screw pump.
Fig. 2 illustrates the pump slip-stream path between apex rotor and lining.
Fig. 3 illustrates the perspective view according to the screw pump rotor of aspect disclosed herein.
Fig. 4 illustrates the rectangular cross section lip ring in the groove of apex rotor.
Fig. 5 illustrates the close-up perspective view of apex rotor according to an embodiment of the invention.
Fig. 6 illustrates the cross-sectional view of apex rotor according to an embodiment of the invention.
Fig. 7 illustrates the cross-sectional view of apex rotor according to another embodiment of the present invention.
Fig. 8 illustrates the cross-sectional view of apex rotor according to another embodiment of the present invention.
Fig. 9 illustrates the cross-sectional view of apex rotor according to another embodiment of the present invention.
Figure 10 illustrates the screw thread that has groove according to another embodiment of the present invention, and groove has the degree of depth of variation.
Specific embodiment
Embodiment disclosed herein comprises screw pump rotor and is used for the lip ring of screw pump rotor.Pump rotor comprises screw thread and the lip ring on axle, the axle.Screw thread comprises the groove on the outer surface that is arranged on screw thread, and lip ring is arranged in the groove.Groove and Sealing are sized to have the gap between them, thereby Sealing can radially be moved with respect to screw thread when pump rotor is offset.As reference Fig. 3, Fig. 4 and Fig. 5 discussed, Sealing became to make Sealing to remain in the groove with recess configurations, allows Sealing moving radially with respect to screw thread simultaneously.Unless spell out in the context, otherwise singulative used herein " ", " one " and " being somebody's turn to do " comprise the referent of plural form.
Fig. 3 illustrates an embodiment's of corresponding screw pump rotor 40 perspective view.Screw thread 44 is spiral, and at least a portion of axle 42.Groove 48 is located on the outer surface or top 46 of the screw thread 44 of pump bushing.During lip ring 50 typically spirals screw thread 44 from the starting point of the screw thread of axle 42 1 ends.Lip ring 50 structurally is spiral, and can have the length of any specific circumferential displacement amount of the helical thread 44 that covers rotor 40.In one embodiment, lip ring 50 covers a whole circle of screw thread 44.
As top the argumentation, lip ring 50 is very important for the overall performance of screw pump.Gap between rotor and lining need allow to rotate dynamic vibration, make misalignment and rotor thermal expansion and because the rotor displacement that pressure causes.Lip ring 50 is outstanding from screw thread 44, and is configured to contact with pump bushing, thereby fills the gap between rotor and the lining.Lip ring 50 of the present invention provides improved sealing between rotor and pump bushing.The solid particle erosion in the gap or the minimizing of wearing and tearing aspect have been guaranteed in improved sealing.
Sometimes lip ring wears up to the degree that they can break away from groove.For example, as shown in Figure 4, the lip ring that has rectangular cross section does not have any restriction, and may be after some wearing and tearing and break away from groove, and this understands cause hard friction or damage to rotor or lining.
Fig. 5 illustrates the perspective view of apex rotor, has shown the starting point of screw thread 44 especially.As explained above, lip ring 50 is typically from the starting point of screw thread is spiraled screw thread 44.
In one embodiment, as shown in Fig. 5 and Fig. 6, groove 48 and lip ring 50 comprise the T shape cross section of reversing.Groove 48 and lip ring 50 are sized to have the gap between them.This gap provides the space of radially moving with respect to screw thread 44 when pump rotor is offset for lip ring 50.As explained below, the T shape cross section of the reversing of groove 48 and lip ring 50 has formed a kind of mutual interlocking gear, and it has limited the scope that moves radially of lip ring 50.
The T shape cross section of the reversing of lip ring 50 can be described to have the first portion 82 substantially parallel with the axis 80 of rotor and with the axis 80 and the vertical substantially second portion 84 of first portion 82 of rotor.Similarly, the T shape cross section of the reversing of groove 48 can be described to have the first portion 86 substantially parallel with the axis 80 of rotor and with rotor axis 80 and the vertical substantially second portion 88 of first portion 86.When being mounted and being under the normal conditions, shown in the best among Fig. 6, lip ring is designed to outside ejection, so that lean on the internal surface 52 of last or close pump bushing 54.Typically, the second portion 84 contact pump bushings 54 of lip ring.When the second portion 84 of lip ring wore and tore, the lip ring radially outward moved, so that keep in touch with pump bushing 54.When the second portion 84 of lip ring wore and tore, first portion's 82 radially outwards of lip ring moved.The first portion 86 that the second portion 84 of lip ring can may wear to until groove prevents the degree that first portion's 82 radially outwards of lip ring move.Therefore, the T shape cross section of groove 48 and lip ring 50 is beneficial to the scope that moves radially of restriction lip ring 50, and prevents that therefore lip ring 50 breaks away from groove 48.
Before in being installed to screw thread, lip ring 50 has free diameter.During being installed to lip ring 50 in the screw thread, the diameter of lip ring is changed, and the diameter of change is called as the assembling diameter.Be subjected to the free diameter of lip ring and the influence of the difference between the assembling diameter in the contact pressure between lip ring and the lining.If the free diameter of lip ring 50 greater than the diameter of lining 54, need so during installation to compress lip ring 50, and contact pressure will remain on high level.If the free diameter of lip ring 50 just reduces contact pressure less than the diameter of lining 54, perhaps can ignore contact pressure, cause lip ring 50 outwards to be offset until the combination of centrifugal force and pressure.Contact pressure will descend along with the wearing and tearing of lip ring 50 usually, thereby prolongs the life-span of lip ring 50.
In operation, shown in the best among Fig. 6, when rotor rotates, formed the section of boost pressure across pump.Occurring in the elimination of the pump slip-stream between rotor 40 and the pump bushing 54 or minimizing is to bear against on the internal surface 52 of pump bushing by the outer surface with lip ring 50 to realize.The spring action of lip ring 50 and promote lip ring at the centrifugal load on the lip ring 50 and be resisted against on the internal surface 52 of pump bushing owing to what the rotation of rotor 40 caused.Also the side surface 56 of lip ring 50 is born against on the internal surface 58 of groove 48 by pressure difference from a side of lip ring 50 to opposite side.Gap between lip ring 50 and groove 48 can be flowed slip-stream 90 along spiral groove below lip ring 50.Wash gravel or other sediments that is deposited in groove 48 bottoms from this slip-stream 90 below the lip ring.
Gap between lip ring 50 and groove 40 can be flowed and be held slip-stream 90 below lip ring 50, thereby the space of deposit-free is provided below lip ring, and does not allow excessive slip-stream.Sediments is removed in slip-stream 90, and allows that lip ring shrinks, thereby reduces the contact pressure between lip ring 50 and lining 54.In addition, in one embodiment, be arranged on pin 60 on multi-turn or the circle segment and can be suitable for interrupting slip-stream 90 below the lip ring, with control or restriction slip-stream 90.
As described in the early time, the scope that moves radially of lip ring 50 is limited.The form that this machinery suppresses will only allow that lip ring 50 may wear to a point, and the remainder of the lip ring groove of can not overflowing.Thereby lip ring 50 remains in the groove 48.
In another embodiment shown in Fig. 7, lip ring 62 and groove 64 are included as the cross section of the mirror image of L shaped cross section.In another embodiment shown in Fig. 8, lip ring 66 and groove 68 have dovetail cross-sectional shape.In the above among two embodiments, lip ring all spirals in the groove, and the scope that moves radially of lip ring 62,66 is limited, keeps the gap between groove and lip ring, and prevents that lip ring 62,66 breaks away from grooves 64,68.
Another embodiment who has shown lip ring 70 among Fig. 9.In this embodiment, the low voltage side 72 of lip ring 70 and towards the corresponding side 74 of the groove 76 of lip ring low voltage side 72 towards the high pressure side 78 of lip ring 70 and tilt.This structure has reduced the contact pressure between the internal surface 52 of lip ring 70 and pump bushing 54, thereby has reduced the rate of depreciation of lip ring 70.
Also can reduce the rate of depreciation of lip ring, thereby minimize the axial pressure drive components of lip ring compressing on lining 52 by the pressure of size below the reduction lip ring of customization groove.Because the high pressure fluid that leaks below lip ring forces lip ring outwards to move, so produced clean outward pressure.Yet,, make groove extend to low-pressure inlet and make groove termination or stop discharging outside pressure before it is connected to the high-pressure outlet of pump because groove forms continuous helical around rotor.Groove can cut and have the degree of depth of variation, centers on the leakage of some lip rings to consider combination, and still provides suitable pressure to discharge, and as shown in Figure 10, the degree of depth of groove 48 is from the degree of depth " d herein
1" be reduced to the degree of depth " d
2".In one embodiment, the degree of depth " d
1" to the degree of depth " d
2" reduce with constant speed.
When lip ring 50,62,66 and 70 when being new, they in addition under skew fully the also gap between canned rotor 40 and the lining 54 basically, and after some wearing and tearing, continue like this.On some points, lip ring may wear to their degree of seal clearance fully.At this some place, pump performance begins to descend.Can monitor performance, and available new lip ring is changed the lip ring of wearing and tearing.If do not change lip ring in this stage, they finally may may wear to its point that flushes with rotor 40 so, and this depends on the degree of eccentricity that is experienced between rotor and the lining.If rotor and lining are concentric all the time, excessive wear will be minimum so.Though the sealing benefit minimum that lip ring provides at this some place, they rest in the groove, and can not cause any problem to system.
About top description, should be realized that optimum size relation for parts of the present invention, the variation that comprises aspects such as size, shape, function and mode of operation, assembling and use all is comprehensible and conspicuous for those of skill in the art, therefore for shown in the figure and all equivalence relations described in the specification only all be intended to contain by the scope of claims.
Though this paper only illustrates and described some feature of the present invention, those of skill in the art will expect many remodeling and variant.Should understand that the claims intention covers all these and drops on true spirit scope of the present invention interior remodeling and variant.
Claims (21)
1. pump rotor that is used for screw pump comprises:
Axle;
Spiral screw thread on the described axle, described screw thread comprises setting groove on its outer surface; With
Be arranged on the Sealing in the described groove, wherein said Sealing becomes with described recess configurations described Sealing is remained in the described groove, allows described Sealing moving radially with respect to described screw thread when described pump rotor skew simultaneously.
2. pump rotor according to claim 1 is characterized in that described Sealing is a lip ring.
3. pump rotor according to claim 2 is characterized in that, described lip ring is configured to from described groove outwards outstanding, and leans against on the internal surface of lining of described screw pump.
4. pump rotor according to claim 3 is characterized in that, described lip ring becomes to make slip-stream to flow below described lip ring with described recess configurations.
5. pump rotor according to claim 3 is characterized in that, described lip ring is configured to rotate along with described axle.
6. pump rotor according to claim 5 is characterized in that, described pump rotor also comprises: be arranged on the pin of first in the described groove and second pin, wherein said lip ring is arranged between described first pin and described second pin.
7. pump rotor according to claim 6 is characterized in that, described lip ring and described screw thread are spiral.
8. pump rotor according to claim 1, it is characterized in that, described pump rotor also comprises a plurality of pins that are arranged in the described groove, and described Sealing comprises a plurality of lip rings, and wherein said a plurality of lip rings respectively are arranged between a pair of continuous pin.
9. pump rotor according to claim 3, it is characterized in that, described lip ring is the sacrificial wear component of described pump rotor, and described lip ring becomes with described recess configurations even prevent that also described lip ring breaks away from described groove after described lip ring wearing and tearing.
10. pump rotor according to claim 3 is characterized in that, described groove and described lip ring comprise the T shape cross section of reversing.
11. pump rotor according to claim 3 is characterized in that, described lip ring and described groove are included as the cross section of the mirror image of L shaped cross section.
12. pump rotor according to claim 3 is characterized in that, described lip ring and described groove have dovetail cross-sectional shape.
13. pump rotor according to claim 3, it is characterized in that the low voltage side of described lip ring and become to be reduced in contact pressure between the internal surface of lining of described lip ring and described screw pump towards the corresponding side surface configurations of the described groove of the low voltage side of described lip ring.
14. method that reduces the slip-stream in the screw pump, described screw pump has the shell of band low-pressure inlet and high-pressure outlet, the lining of inside that is arranged on described shell and the rotor that is arranged on the inside of described lining, described rotor has axle and is arranged on screw thread on the outer surface of described axle, and described method comprises:
On the outer surface of described screw thread, form groove; With
Lip ring is arranged in the described groove, make described lip ring outwards outstanding from described groove, and lean against on the internal surface of lining of described screw pump, thereby reduce slip-stream from described high-pressure outlet to described low-pressure inlet, described lip ring becomes with described recess configurations described Sealing is remained in the described groove, allows described Sealing moving radially with respect to described screw thread when described pump rotor skew simultaneously.
15. method according to claim 14 is characterized in that, described lip ring becomes to make slip-stream to flow below described lip ring with described recess configurations.
16. method according to claim 14 is characterized in that, described groove shaped becomes on the degree of depth and changes.
17. method according to claim 14 is characterized in that, described method also comprises can rotate described lip ring along with described axle rotation.
18. a two screw pump comprises:
Shell, it has entrance and exit;
Be arranged on the lining of described enclosure; With
Be arranged at least two rotors of described bush inside, each rotor includes:
Axle;
Be arranged on the screw thread on the part of outer surface of described axle;
Groove on the outer surface of described screw thread; With
Lip ring, it is in described groove, and be configured to described axle rotation and outwards outstanding from described groove, wherein said lip ring becomes with described recess configurations described Sealing is remained in the described groove, allows described Sealing moving radially with respect to described screw thread when described pump rotor skew simultaneously.
19. pump according to claim 18 is characterized in that, described lip ring becomes to make slip-stream to flow below described lip ring with described recess configurations.
20. pump according to claim 18, it is characterized in that the low voltage side of described lip ring and become to reduce contact pressure between the internal surface of the lining of described lip ring and described screw pump towards the corresponding side surface configurations of the described groove of described lip ring low voltage side.
21. a rotor that is used for screw pump comprises:
Axle;
Be arranged on the helical thread on the outer surface of described axle, described helical thread defines groove wherein;
Sealing configuration is arranged in the described groove to its locking, and wherein said Sealing and described recess configurations become to allow described Sealing moving radially with respect to described screw thread when described rotor displacement.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US12/191324 | 2008-08-14 | ||
| US12/191,324 US20100040499A1 (en) | 2008-08-14 | 2008-08-14 | Screw pump rotors and ring seals for screw pump rotors |
| PCT/US2009/050613 WO2010019337A1 (en) | 2008-08-14 | 2009-07-15 | Ring seals for screw pump rotors |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102124227A true CN102124227A (en) | 2011-07-13 |
Family
ID=41316654
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801324611A Pending CN102124227A (en) | 2008-08-14 | 2009-07-15 | Ring seals for screw pump rotors |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20100040499A1 (en) |
| EP (1) | EP2324246A1 (en) |
| CN (1) | CN102124227A (en) |
| BR (1) | BRPI0912438A2 (en) |
| WO (1) | WO2010019337A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103089649A (en) * | 2012-10-30 | 2013-05-08 | 徐建涛 | Rotor of Roots type vapor compressor |
| CN106401945A (en) * | 2015-07-29 | 2017-02-15 | 川崎重工业株式会社 | Biomass cake pressure-feeding device |
| CN107044412A (en) * | 2017-03-28 | 2017-08-15 | 四川凯创机电设备有限公司 | It is easily installed the screw rod of detection means in pump |
| CN110725796A (en) * | 2019-11-11 | 2020-01-24 | 浙江思科瑞真空技术有限公司 | Screw pump with multi-section rotor structure |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080193309A1 (en) * | 2007-02-09 | 2008-08-14 | Vasanth Srinivasa Kothnur | Screw pump rotor and method of reducing slip flow |
| US20110158841A1 (en) * | 2009-12-28 | 2011-06-30 | Sunny King Machinery Co., Ltd. | Screw Pump with Anti-Turbulent Structure |
| DE202010012494U1 (en) * | 2010-09-13 | 2011-12-15 | Hugo Vogelsang Maschinenbau Gmbh | Rotary pump and rotary piston |
| CN102220974B (en) * | 2011-07-29 | 2016-06-08 | 四川省机械研究设计院 | Bearing-free Quimby pump |
| US10006340B2 (en) * | 2013-10-16 | 2018-06-26 | John Malcolm Gray | Supercharger |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE455967C (en) * | 1924-04-07 | 1928-02-15 | Carl Oscar Josef Montelius | Pump or motor, especially for fluid gears |
| GB342791A (en) * | 1929-10-12 | 1931-02-12 | Frederick Charles Greenfield | Improvements in and relating to rotary machines for the compression or propulsion of fluids |
| US2195886A (en) * | 1936-12-11 | 1940-04-02 | Reconstruction Finance Corp | Rotary pump |
| DE855946C (en) * | 1944-08-13 | 1952-11-17 | Hoechst Ag | Auger |
| US3282495A (en) * | 1964-04-29 | 1966-11-01 | Dresser Ind | Sealing arrangement for screw-type compressors and similar devices |
| US3806287A (en) * | 1970-11-19 | 1974-04-23 | Lear Siegler Inc | Shaft seal for rotating pumps |
| AU547490B2 (en) * | 1980-05-31 | 1985-10-24 | Sanden Corporation | Scroll-type pump |
| JPS62126207A (en) * | 1985-11-27 | 1987-06-08 | Mitsubishi Electric Corp | Scroll hydraulic machine |
| JPS63136283U (en) * | 1987-02-27 | 1988-09-07 | ||
| US5158304A (en) * | 1990-01-23 | 1992-10-27 | Inpro Companies, Inc. | Captured rotor seal |
| US5348453A (en) * | 1990-12-24 | 1994-09-20 | James River Corporation Of Virginia | Positive displacement screw pump having pressure feedback control |
| US5292138A (en) * | 1992-09-21 | 1994-03-08 | General Elecric Company | Rotor to rotor split ring seal |
| US5779451A (en) * | 1995-06-05 | 1998-07-14 | Hatton; Gregory John | Power efficient multi-stage twin screw pump |
| US5833438A (en) * | 1995-07-31 | 1998-11-10 | Coltec Industries Inc | Variable displacement vane pump having cam seal with seal land |
| US5639211A (en) * | 1995-11-30 | 1997-06-17 | United Technology Corporation | Brush seal for stator of a gas turbine engine case |
| JPH1061564A (en) * | 1996-08-20 | 1998-03-03 | Atsushi Imai | Pump utilized spiral seal |
| US6049979A (en) * | 1998-10-20 | 2000-04-18 | General Electric Co. | Methods for shielding a welding gas turbine repair of a damaged turbine rotor wheel dovetail |
| US6007121A (en) * | 1998-12-02 | 1999-12-28 | E. J. Brooks Company | Rotatable seal |
| US6629816B2 (en) * | 2001-08-16 | 2003-10-07 | Honeywell International Inc. | Non-contacting clearance seal for high misalignment applications |
| US20080193309A1 (en) * | 2007-02-09 | 2008-08-14 | Vasanth Srinivasa Kothnur | Screw pump rotor and method of reducing slip flow |
-
2008
- 2008-08-14 US US12/191,324 patent/US20100040499A1/en not_active Abandoned
-
2009
- 2009-07-15 BR BRPI0912438A patent/BRPI0912438A2/en not_active Application Discontinuation
- 2009-07-15 EP EP09790424A patent/EP2324246A1/en not_active Withdrawn
- 2009-07-15 CN CN2009801324611A patent/CN102124227A/en active Pending
- 2009-07-15 WO PCT/US2009/050613 patent/WO2010019337A1/en active Application Filing
Cited By (10)
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| CN103089649A (en) * | 2012-10-30 | 2013-05-08 | 徐建涛 | Rotor of Roots type vapor compressor |
| CN103089649B (en) * | 2012-10-30 | 2016-05-18 | 徐建涛 | Roots-type both vapor compression machine rotor |
| CN106401945A (en) * | 2015-07-29 | 2017-02-15 | 川崎重工业株式会社 | Biomass cake pressure-feeding device |
| AU2016300320B2 (en) * | 2015-07-29 | 2019-04-11 | Kawasaki Jukogyo Kabushiki Kaisha | Biomass cake pressure-feeding device |
| US10322390B2 (en) | 2015-07-29 | 2019-06-18 | Kawasaki Jukogyo Kabushiki Kaisha | Biomass cake pressure-feeding apparatus |
| CN106401945B (en) * | 2015-07-29 | 2019-08-16 | 川崎重工业株式会社 | Biomass briquette forced feed device |
| CN107044412A (en) * | 2017-03-28 | 2017-08-15 | 四川凯创机电设备有限公司 | It is easily installed the screw rod of detection means in pump |
| CN107044412B (en) * | 2017-03-28 | 2019-03-05 | 四川凯创机电设备有限公司 | It is easily installed the screw rod of detection device in pumping |
| CN110725796A (en) * | 2019-11-11 | 2020-01-24 | 浙江思科瑞真空技术有限公司 | Screw pump with multi-section rotor structure |
| CN110725796B (en) * | 2019-11-11 | 2021-08-13 | 浙江思科瑞真空技术有限公司 | Screw pump with multi-section rotor structure |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2010019337A9 (en) | 2010-09-10 |
| BRPI0912438A2 (en) | 2016-01-05 |
| EP2324246A1 (en) | 2011-05-25 |
| US20100040499A1 (en) | 2010-02-18 |
| WO2010019337A1 (en) | 2010-02-18 |
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Application publication date: 20110713 |