US20070212238A1 - Rotodynamic Fluid Machine - Google Patents
Rotodynamic Fluid Machine Download PDFInfo
- Publication number
- US20070212238A1 US20070212238A1 US11/660,680 US66068005A US2007212238A1 US 20070212238 A1 US20070212238 A1 US 20070212238A1 US 66068005 A US66068005 A US 66068005A US 2007212238 A1 US2007212238 A1 US 2007212238A1
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- US
- United States
- Prior art keywords
- motor
- shaft
- rotodynamic
- machine according
- fluid
- 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.)
- Abandoned
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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
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/058—Bearings magnetic; electromagnetic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D1/06—Multi-stage pumps
- F04D1/063—Multi-stage pumps of the vertically split casing type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/0606—Canned motor pumps
- F04D13/0633—Details of the bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/048—Bearings magnetic; electromagnetic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
Definitions
- the present invention relates to rotodynamic fluid machines and in particular to high power multistage units having a plurality of impeller stages. These are often used, for example, as high pressure pumps, particularly in the oil industry.
- Multistage rotodynamic fluid machines can offer an increased output pressure over a single stage unit.
- the provision of additional impeller stages necessarily increases the overall size of the unit.
- a rotodynamic fluid machine comprising a motor arranged for directly driving a shaft, a pressurised motor housing having end walls through which the shaft passes via dry seals to enclose the motor, means for maintaining the pressure within the motor housing different from the pressure outside the motor housing, a first impeller directly connected to one end of the motor driven shaft, arranged to move process fluid from an inlet to an outlet in a first direction relative to the shaft axis, a second impeller directly connected to the opposite end of the shaft, arranged to move process fluid from a second inlet to a second outlet in an opposite direction to the first direction relative to the shaft axis such that suction is created at both ends of the shaft, and a process fluid conduit connecting the first outlet to the second inlet.
- the pressure within the motor housing is different to the pressure of the process fluid in particular of the input process fluid, before it is pressurised or pumped up to discharge pressure.
- the pressure in the motor housing is preferably maintained high, i.e. higher than the process fluid or other adjacent fluids so as to ensure no leakage of fluids into the motor, for example if a seal fails.
- Another aspect of the invention provides a pump comprising a rotodynamic fluid machine of the first aspect.
- each of the first and second impellers are arranged to pump fluid generally towards the motor and the machine comprises a closed loop pressurised gas circulation system in fluid communication with a rotor part of the motor.
- the rotodynamic fluid machine may comprise a magnetic bearing supporting the shaft in a motor housing.
- the shaft is integral with a rotor part of the motor.
- the first impeller comprises a plurality of impeller stages and the second impeller comprises a plurality of impeller stages, and the first and second impellers may each comprise a diffuser unit.
- the diameter of the shaft may be larger in the region of the motor and smaller in the region of the or each impeller.
- the motor is preferably an electric motor.
- a rotodynamic fluid machine according to the present invention is particularly advantageous because mounting impellers directly onto the motor shaft eliminates the need for a coupling between a motor shaft and an impeller shaft. Thus the shaft length and the total length of the machine can be reduced. Axial thrust is also decreased and so thrust bearings can be reduced in size due to the back to back arrangement of the first and second impellers.
- the number of radial bearings may also be reduced since bearings need not be provided on either side of a coupling (i.e. one for each of the motor and impeller shafts). Without a coupling, there is no need for advanced in-field alignment procedures and the rotor dynamics of the machine are simplified with vibration levels reduced. Furthermore the use of balancing discs is not required.
- the motor housing is sealed to enclose the motor to maintain the different pressures and this advantageously provides a clean and dry air internal environment for the motor.
- this inventive machine particularly when combined with magnetic bearings, this provides the possibility of a dry, oil-free machine.
- the back-to-back arrangement ensures that the axial forces are controlled without using large balance pistons which have hitherto been required in known motors.
- FIG. 1 is a representation of a rotodynamic fluid machine according the present invention.
- the figure shows a rotodynamic fluid machine 10 with an electric motor 12 enclosed in a pressurised housing 14 with end walls 16 and 18 .
- the arrangement can be mounted vertically or horizontally.
- a shaft 20 is integrated with the rotor of the motor 12 and extends from each end of the motor through the end walls 16 , 18 .
- the diameter of shaft 20 decreases towards its free ends.
- a first set of impellers 22 is mounted on one end of shaft 20 on one side of the motor 12 and a second set of impellers 24 is mounted on the opposite end of shaft 20 on the other side of the motor 12 .
- the shaft 20 and the impellers 22 , 24 are rotatable about a common axis 26 .
- the impellers 22 , 24 are arranged in a back-to-back configuration such that the first impeller set 22 is oriented 180° compared to the second impeller set 24 , and so that the first and second impellers move fluid in diametrically opposed directions relative to the axis 26 of the shaft 20 .
- the direction of fluid flow as referred to here is the global overall flow: naturally the local direction of flow at the outlet from the impeller blades will be radial or radial/axial mixed flow compared to the shaft, but the overall flow from impeller inlet to impeller outlet will be axial.
- the impellers 22 and 24 also comprise diffuser units. The fluid is moved towards the motor 12 from each impeller 22 , 24 .
- the fluid flows into each impeller 22 , 24 from the free ends of the shaft 20 and thus creates end suction which is advantageous.
- the fluid flows into the machine through a primary inlet conduit 34 in the direction of arrow A towards a free end of the shaft 20 and enters the first set of impellers 22 at first inlet 42 . It exits the first set of impellers 22 at first outlet 52 .
- a fluid conduit 28 provides a fluid connection between the first set of impellers 22 , and the second set of impellers 24 . This runs generally parallel to the motor 12 as a crossover line and connects the first outlet 52 to the inlet 44 of the second set of impellers 24 at the other free end of the shaft 20 , and exits the second set of impellers 24 at second outlet 54 .
- a dry gas seal 30 of known construction is located on shaft 20 at each side of the motor 12 to isolate the fluid from the motor.
- the inner surfaces of each seal 30 are shaped to maintain a gas seal with the outer surface of the rotating shaft 20 .
- Magnetic bearings 32 are interposed on each side of the motor 12 between the respective end walls 16 , 18 of the motor housing and the shaft 20 .
- the electric motor 12 drives both sets of impellers 22 and 24 directly via the shaft 20 .
- Process fluid enters in the direction of arrow A through the inlet 34 and is pumped along the fluid conduit 28 by the first set of impellers 22 .
- the conduit 28 is shaped to alter the direction of the fluid flow such that the fluid flows in substantially the opposite direction to arrow A as it enters the second set of impellers 24 , at the other free end of the shaft 20 .
- An alternative outlet conduit 38 is shown which is oriented substantially at right angles to the outlet conduit 36 .
- the work done on the fluid by the first set of impellers 22 causes a resultant tensile force in shaft 20 which acts in the opposite direction to the tensile force caused by the second impeller 24 .
- the overall resultant force within the system during normal operation is effectively cancelled and thus substantially reduced, ideally to zero.
- the magnetic bearings 32 act as radial and thrust bearings, by imparting a magnetic force on the shaft 20 and maintaining an air gap between the shaft 20 and the bearings 32 .
- Sensor feedback systems of known construction are used to maintain the gap spacing so that there is no contact between the shaft 20 and the bearings 32 . Hence there is virtually no friction or wear between these parts and the need for lubricating oil or any hydraulic fluid is avoided.
- the motor stator is externally cooled by liquid 40 , disposed around the motor stator, within the motor housing.
- the motor rotor is cooled by a closed loop pressurised gas circulation. During operation, the motor housing is maintained at a pressure greater than that of the surrounding environment. This provides compact cooling and, for a rotodynamic machine running at high speeds (typically from 4,000 up to 12,000 rpm), allows the overall dimensions of the pump to be further reduced.
- the rotodynamic machine of the present invention may be provided with more impellers positioned on each side of the motor, for example two impellers may be provided on each side.
- the present invention is applicable to rotodynamic machines such as, for example, axial or centrifugal pumps, particularly to high-power (>1 MW) pumps.
Abstract
A rotodynamic fluid machine includes a motor arranged for directly driving a shaft, a pressurized motor housing having end walls through which the shaft passes via dry gas seals to enclose the motor, elements for maintaining the pressure within the motor housing which pressure is different from the pressure outside the motor housing, a first impeller directly connected to one end of the motor driven shaft, arranged to move process fluid from an inlet to an outlet in a first direction relative to the shaft axis, a second impeller directly connected to the opposite end of the shaft, arranged to move process fluid from a second inlet to a second outlet in an opposite direction to the first direction relative to the shaft axis such that suction is created at both ends of the shaft, and a process fluid conduit connecting the first outlet to the second inlet.
Description
- The present invention relates to rotodynamic fluid machines and in particular to high power multistage units having a plurality of impeller stages. These are often used, for example, as high pressure pumps, particularly in the oil industry.
- Multistage rotodynamic fluid machines can offer an increased output pressure over a single stage unit. However the provision of additional impeller stages necessarily increases the overall size of the unit.
- Also, in known machines a coupling is required between the driving shaft extending from a motor and the driven shaft connected to one or more impeller stages, and this adds to the overall length of the machine. Furthermore couplings are a source of vibrational problems in rotating shafts and can greatly complicate a machine's rotor dynamics.
- Traditional mechanical bearings become worn with use and require lubrication in order to ensure correct operation. The use of oil to lubricate rotating parts causes a decrease in efficiency and the oil may leak contaminating other parts.
- Traditional high power multistage machines require high capacity thrust bearings and balancing discs to take up the resultant axial load created by the driving force of the impeller stages acting on the fluid. Seals are also required between the shafts and the housing to isolate the motor. Such parts also require lubrication and cause further losses in efficiency.
- According to one aspect of the present invention there is provided a rotodynamic fluid machine comprising a motor arranged for directly driving a shaft, a pressurised motor housing having end walls through which the shaft passes via dry seals to enclose the motor, means for maintaining the pressure within the motor housing different from the pressure outside the motor housing, a first impeller directly connected to one end of the motor driven shaft, arranged to move process fluid from an inlet to an outlet in a first direction relative to the shaft axis, a second impeller directly connected to the opposite end of the shaft, arranged to move process fluid from a second inlet to a second outlet in an opposite direction to the first direction relative to the shaft axis such that suction is created at both ends of the shaft, and a process fluid conduit connecting the first outlet to the second inlet.
- Preferably the pressure within the motor housing is different to the pressure of the process fluid in particular of the input process fluid, before it is pressurised or pumped up to discharge pressure. The pressure in the motor housing is preferably maintained high, i.e. higher than the process fluid or other adjacent fluids so as to ensure no leakage of fluids into the motor, for example if a seal fails.
- Another aspect of the invention provides a pump comprising a rotodynamic fluid machine of the first aspect.
- Preferably each of the first and second impellers are arranged to pump fluid generally towards the motor and the machine comprises a closed loop pressurised gas circulation system in fluid communication with a rotor part of the motor.
- The rotodynamic fluid machine may comprise a magnetic bearing supporting the shaft in a motor housing.
- According to a preferred embodiment, the shaft is integral with a rotor part of the motor.
- Advantageously the first impeller comprises a plurality of impeller stages and the second impeller comprises a plurality of impeller stages, and the first and second impellers may each comprise a diffuser unit.
- The diameter of the shaft may be larger in the region of the motor and smaller in the region of the or each impeller.
- The motor is preferably an electric motor.
- A rotodynamic fluid machine according to the present invention is particularly advantageous because mounting impellers directly onto the motor shaft eliminates the need for a coupling between a motor shaft and an impeller shaft. Thus the shaft length and the total length of the machine can be reduced. Axial thrust is also decreased and so thrust bearings can be reduced in size due to the back to back arrangement of the first and second impellers.
- The number of radial bearings may also be reduced since bearings need not be provided on either side of a coupling (i.e. one for each of the motor and impeller shafts). Without a coupling, there is no need for advanced in-field alignment procedures and the rotor dynamics of the machine are simplified with vibration levels reduced. Furthermore the use of balancing discs is not required.
- The use of magnetic bearings and dry gas seals advantageously allows for a rotodynamic machine which does not require the use of lubricating oil or hydraulic fluid. Thus the parasitic power losses caused by oil shear and drag are avoided. Furthermore the problem of oil leakage is eliminated and the overall machine is simplified. Maintenance is reduced as well as the number of auxiliary systems.
- The motor housing is sealed to enclose the motor to maintain the different pressures and this advantageously provides a clean and dry air internal environment for the motor. In combination with the back-to-back arrangement of this inventive machine, particularly when combined with magnetic bearings, this provides the possibility of a dry, oil-free machine.
- The back-to-back arrangement ensures that the axial forces are controlled without using large balance pistons which have hitherto been required in known motors.
- In known open motors, the process fluid is in and around the electric motor and this creates problems with motor contamination and bearing lubrication.
- For a better understanding of the present invention, and to show how the same may be carried into effect, reference will now be made, by way of example, to the single
FIG. 1 , which is a representation of a rotodynamic fluid machine according the present invention. - The figure shows a
rotodynamic fluid machine 10 with anelectric motor 12 enclosed in apressurised housing 14 withend walls - A
shaft 20 is integrated with the rotor of themotor 12 and extends from each end of the motor through theend walls shaft 20 decreases towards its free ends. - A first set of
impellers 22 is mounted on one end ofshaft 20 on one side of themotor 12 and a second set ofimpellers 24 is mounted on the opposite end ofshaft 20 on the other side of themotor 12. Theshaft 20 and theimpellers common axis 26. - The
impellers axis 26 of theshaft 20. The direction of fluid flow as referred to here is the global overall flow: naturally the local direction of flow at the outlet from the impeller blades will be radial or radial/axial mixed flow compared to the shaft, but the overall flow from impeller inlet to impeller outlet will be axial. Theimpellers motor 12 from eachimpeller impeller shaft 20 and thus creates end suction which is advantageous. The fluid flows into the machine through a primary inlet conduit 34 in the direction of arrow A towards a free end of theshaft 20 and enters the first set ofimpellers 22 atfirst inlet 42. It exits the first set ofimpellers 22 atfirst outlet 52. Afluid conduit 28 provides a fluid connection between the first set ofimpellers 22, and the second set ofimpellers 24. This runs generally parallel to themotor 12 as a crossover line and connects thefirst outlet 52 to the inlet 44 of the second set ofimpellers 24 at the other free end of theshaft 20, and exits the second set ofimpellers 24 atsecond outlet 54. - A
dry gas seal 30 of known construction is located onshaft 20 at each side of themotor 12 to isolate the fluid from the motor. The inner surfaces of eachseal 30 are shaped to maintain a gas seal with the outer surface of the rotatingshaft 20. -
Magnetic bearings 32 are interposed on each side of themotor 12 between therespective end walls shaft 20. - During operation, the
electric motor 12 drives both sets ofimpellers shaft 20. Process fluid enters in the direction of arrow A through theinlet 34 and is pumped along thefluid conduit 28 by the first set ofimpellers 22. Theconduit 28 is shaped to alter the direction of the fluid flow such that the fluid flows in substantially the opposite direction to arrow A as it enters the second set ofimpellers 24, at the other free end of theshaft 20. - The fluid exits the second set of
impellers 24 viasecond outlet 54 and exits the machine via anoutlet conduit 36, which is shaped such that the fluid exits themachine 10 in the direction of arrow A. Analternative outlet conduit 38 is shown which is oriented substantially at right angles to theoutlet conduit 36. - The work done on the fluid by the first set of
impellers 22 causes a resultant tensile force inshaft 20 which acts in the opposite direction to the tensile force caused by thesecond impeller 24. Thus the overall resultant force within the system during normal operation is effectively cancelled and thus substantially reduced, ideally to zero. - The
magnetic bearings 32 act as radial and thrust bearings, by imparting a magnetic force on theshaft 20 and maintaining an air gap between theshaft 20 and thebearings 32. Sensor feedback systems of known construction (but not shown) are used to maintain the gap spacing so that there is no contact between theshaft 20 and thebearings 32. Hence there is virtually no friction or wear between these parts and the need for lubricating oil or any hydraulic fluid is avoided. - The motor stator is externally cooled by
liquid 40, disposed around the motor stator, within the motor housing. - The motor rotor is cooled by a closed loop pressurised gas circulation. During operation, the motor housing is maintained at a pressure greater than that of the surrounding environment. This provides compact cooling and, for a rotodynamic machine running at high speeds (typically from 4,000 up to 12,000 rpm), allows the overall dimensions of the pump to be further reduced.
- The use of magnetic bearings and dry gas seals in combination with overpressure of the motor provides for an oil-free rotodynamic unit and motor with no leakage of lubricating oil or hydraulic fluid. This increases efficiency, typically in the region of 2 to 3%, compared to a machine with lubricated parts and normal bearings and seals. In some cases, process lubricated bearings, which also exclude external lubrication supply, can be applied.
- The rotodynamic machine of the present invention may be provided with more impellers positioned on each side of the motor, for example two impellers may be provided on each side.
- The present invention is applicable to rotodynamic machines such as, for example, axial or centrifugal pumps, particularly to high-power (>1 MW) pumps.
Claims (15)
1. A rotodynamic fluid machine comprising a motor arranged for directly driving a shaft, a pressurised motor housing having end walls through which the shaft passes via dry seals to enclose the motor, means for maintaining the pressure within the motor housing different from the pressure outside the motor housing, a first impeller directly connected to one end of the motor driven shaft, arranged to move process fluid from an inlet to an outlet in a first direction relative to the shaft axis, a second impeller directly connected to the opposite end of the shaft, arranged to move process fluid from a second inlet to a second outlet, in an opposite direction to the first direction relative to the shaft axis, such that suction is created at both ends of the shaft, and a process fluid conduit connecting the first outlet to the second inlet.
2. A rotodynamic fluid machine according to claim 1 in which the pressure within the motor housing is also maintained different from the pressure of the process fluid.
3. A rotodynamic fluid machine according to claim 1 wherein the pressure within the motor housing is maintained higher than the pressure outside the motor housing.
4. A rotodynamic fluid machine according to wherein the pressure within the motor housing is maintained higher than the pressure of the process fluid.
5. A rotodynamic fluid machine according to claim 1 wherein the dry seals are dry gas seals.
6. A rotodynamic machine according to claim 1 claims wherein each of the first and second impellers are arranged to pump process fluid generally towards the motor.
7. A rotodynanic machine according to claim 1 comprising a closed loop pressurised gas circulation system in fluid communication with a rotor part of the motor.
8. A rotodynamic machine according to claim 1 , further comprising a magnetic bearing supporting the shaft in the motor housing.
9. A rotodynamic machine according to claim 1 , wherein the shaft is integral with a rotor part of the motor.
10. A rotodynamic machine according to claim 1 , wherein the first impeller comprises a plurality of impeller stages and the second impeller comprises a plurality of impeller stages.
11. A rotodynamic machine according to claim 1 wherein the first and second impellers each comprise a diffuser unit.
12. A rotodynamic machine according to claim 1 wherein the diameter of the shaft is larger in the region of the motor and smaller in the region of the or each impeller.
13. A rotodynamic machine according to claim 1 wherein the motor is an electric motor.
14. A pump comprising a rotodynamic machine according to claim 1 .
15. A rotodynamic fluid machine according to claim 2 wherein the pressure within the motor housing is maintained higher than the pressure outside the motor housing.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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GB0418775.3 | 2004-08-23 | ||
GB0418775A GB2417523B (en) | 2004-08-23 | 2004-08-23 | Rotodynamic fluid machine |
PCT/EP2005/054139 WO2006021560A1 (en) | 2004-08-23 | 2005-08-23 | Rotodynamic fluid machine |
Publications (1)
Publication Number | Publication Date |
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US20070212238A1 true US20070212238A1 (en) | 2007-09-13 |
Family
ID=33042499
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/660,680 Abandoned US20070212238A1 (en) | 2004-08-23 | 2005-08-23 | Rotodynamic Fluid Machine |
Country Status (7)
Country | Link |
---|---|
US (1) | US20070212238A1 (en) |
EP (1) | EP1787028A1 (en) |
BR (1) | BRPI0514609A (en) |
CA (1) | CA2578295A1 (en) |
GB (1) | GB2417523B (en) |
NO (1) | NO20071520L (en) |
WO (1) | WO2006021560A1 (en) |
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US10018274B2 (en) | 2015-08-10 | 2018-07-10 | Exxonmobil Upstream Research Company | Device and method for magnetically controlled dry gas seal |
US20180223869A1 (en) * | 2017-02-06 | 2018-08-09 | Nuovo Pignone Tecnologie Srl | Turbomachine and method of operating a turbomachine |
US10132412B2 (en) | 2016-08-05 | 2018-11-20 | Exxonmobil Upstream Research Company | Device and method for controlling rotating equipment seal without buffer support equipment |
US20190136862A1 (en) * | 2016-06-03 | 2019-05-09 | Vetco Gray Scandinavia As | Modular compressor with gas bearings and system for raising the pressure in production gas |
US10712183B2 (en) * | 2016-03-09 | 2020-07-14 | Onesubsea Ip Uk Limited | Determining flow rates of multiphase fluids |
US11131319B2 (en) * | 2017-08-31 | 2021-09-28 | Mitsubishi Heavy Industries Compressor Corporation | Centrifugal compressor |
US11326607B2 (en) * | 2019-02-05 | 2022-05-10 | Saudi Arabian Oil Company | Balancing axial thrust in submersible well pumps |
US11359472B2 (en) | 2019-02-05 | 2022-06-14 | Saudi Arabian Oil Company | Balancing axial thrust in submersible well pumps |
US11591899B2 (en) | 2021-04-05 | 2023-02-28 | Saudi Arabian Oil Company | Wellbore density meter using a rotor and diffuser |
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GB2469217B (en) * | 2007-10-30 | 2012-01-11 | Richard Julius Gozdawa | Vertical multi-stage gas compressor |
GB2454188B (en) * | 2007-10-30 | 2010-09-29 | Richard Julius Gozdawa | Gas compressor |
CN104712559B (en) * | 2015-03-07 | 2017-01-04 | 烟台龙港泵业股份有限公司 | A kind of Multistage magnetic pump |
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2005
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- 2005-08-23 WO PCT/EP2005/054139 patent/WO2006021560A1/en not_active Application Discontinuation
- 2005-08-23 EP EP05789629A patent/EP1787028A1/en not_active Withdrawn
- 2005-08-23 CA CA002578295A patent/CA2578295A1/en not_active Abandoned
- 2005-08-23 US US11/660,680 patent/US20070212238A1/en not_active Abandoned
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US10018274B2 (en) | 2015-08-10 | 2018-07-10 | Exxonmobil Upstream Research Company | Device and method for magnetically controlled dry gas seal |
WO2017073499A1 (en) * | 2015-10-26 | 2017-05-04 | 株式会社日立製作所 | Turbo machine |
US10712183B2 (en) * | 2016-03-09 | 2020-07-14 | Onesubsea Ip Uk Limited | Determining flow rates of multiphase fluids |
US11098726B2 (en) * | 2016-06-03 | 2021-08-24 | Vetco Gray Scandinavia As | Modular compressor with gas bearings and system for raising the pressure in production gas |
US20190136862A1 (en) * | 2016-06-03 | 2019-05-09 | Vetco Gray Scandinavia As | Modular compressor with gas bearings and system for raising the pressure in production gas |
US10132412B2 (en) | 2016-08-05 | 2018-11-20 | Exxonmobil Upstream Research Company | Device and method for controlling rotating equipment seal without buffer support equipment |
US10808725B2 (en) * | 2017-02-06 | 2020-10-20 | Nuovo Pignone Tecnologie Srl | Turbomachine and method of operating a turbomachine |
US20180223869A1 (en) * | 2017-02-06 | 2018-08-09 | Nuovo Pignone Tecnologie Srl | Turbomachine and method of operating a turbomachine |
US11131319B2 (en) * | 2017-08-31 | 2021-09-28 | Mitsubishi Heavy Industries Compressor Corporation | Centrifugal compressor |
US11326607B2 (en) * | 2019-02-05 | 2022-05-10 | Saudi Arabian Oil Company | Balancing axial thrust in submersible well pumps |
US11359472B2 (en) | 2019-02-05 | 2022-06-14 | Saudi Arabian Oil Company | Balancing axial thrust in submersible well pumps |
US11686312B2 (en) | 2019-02-05 | 2023-06-27 | Saudi Arabian Oil Company | Balancing axial thrust in submersible well pumps |
US11591899B2 (en) | 2021-04-05 | 2023-02-28 | Saudi Arabian Oil Company | Wellbore density meter using a rotor and diffuser |
Also Published As
Publication number | Publication date |
---|---|
NO20071520L (en) | 2007-05-22 |
EP1787028A1 (en) | 2007-05-23 |
WO2006021560A1 (en) | 2006-03-02 |
CA2578295A1 (en) | 2006-03-02 |
GB2417523A (en) | 2006-03-01 |
BRPI0514609A (en) | 2008-06-17 |
GB0418775D0 (en) | 2004-09-22 |
GB2417523B (en) | 2009-07-08 |
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Legal Events
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