CA2319607C - A roto-dynamic high pressure machine - Google Patents
A roto-dynamic high pressure machine Download PDFInfo
- Publication number
- CA2319607C CA2319607C CA002319607A CA2319607A CA2319607C CA 2319607 C CA2319607 C CA 2319607C CA 002319607 A CA002319607 A CA 002319607A CA 2319607 A CA2319607 A CA 2319607A CA 2319607 C CA2319607 C CA 2319607C
- Authority
- CA
- Canada
- Prior art keywords
- vanes
- pressure
- pump
- inlet
- pressure step
- 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.)
- Expired - Fee Related
Links
Classifications
-
- 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2211—More than one set of flow passages
-
- 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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
An improved pump or compressor of the centrifugal type is provided, which has an impeller surrounded by a housing and having a disk, a first plurality of vanes provided near the disk, cover disks provided about the edges of the vanes, and a second plurality of vanes provided on the outwardly directed sides of the cover disks. Two pressure steps are created by the first plurality of vanes, each side of the disk and the cover disks. Two additional pressure steps are created by the second plurality of vanes, the cover disks, and pump housing walls that are located adjacently to the second plurality of vanes. Single or multiple flow conduits are arranged among the various inlets and outlets of the pressure steps, such that a fluid flows through the various pressure steps, with the last pressure step being closest to a motor unit and an outlet connected to the last pressure step being on the same side and facing in the same direction as an inlet. Demands for higher efficiencies, improved compactness and a simpler, more symmetrical design are met by this configuration.
Description
A ROTO-DYNAMIC HIGH-PRESSURE MACHINE.
FIELD OF THE INVENTION
The invention relates to a high-pressure machine, and more particularly, to a pump for liquids or a compressor for obtaining a media transport, including gaseous media, under high pressure.
BACKGROUND OF THE INVENTION
When pumping liquids to high levels where consequent high pressures are required, a pump of the centrifugal type is preferred. Such a pump comprises a pump impeller on a rotating shaft, such an impeller being designed with a hub and a circular disk provided with one or several impeller vanes. The liquid enters in an axial direction in the center and leaves the impeller at the periphery. A pump housing surrounding the impeller transforms the kinetic energy to pressure energy, thereby raising the transport to a higher level.
At higher heads, it is common to use pumps with high rotation speeds and relatively small diameters. It is also possible to connect a number of pumps in series by connecting the outlet from a first step to the inlet in a second step and so on. An example is shown in EP-A-355781, where five steps are connected in series.
When a certain operation point at a certain rotation speed is chosen, it can be an advantage to use several steps, as the pump impellers can operate at rotation speeds which are superior in terms of efficiency. This increase of efficiency is mainly related to the fact that the friction losses at the back sides of the impeller hubs, as a part of the total losses, decrease. However, linking losses between the steps are added. A further disadvantage is that the relatively complicated design means that service and maintenance become complicated and in addition, long shafts bring about increased mechanical stress.
Another way to obtain high pump heads is to connect two identical pressure steps in series as is shown in US-A-958 765 and DE-353 698. The pump impellers are here arranged mirror-inverted, but have in other respects conventional designs. US-A-2 136 939 discloses a pump with two pressure steps having a common hub disk, thereby obtaining a reduction of the disk losses. Both of these solutions, however, have in common the problem that they only allow two pressure steps. Therefore, these conventional solutions are not always sufficient in terms of obtaining the desired pump head.
What is needed, therefore, is a pump or compressor having more than two pressure steps that can achieve a high efficiency, while minimizing linking losses and avoiding complicated designs.
2 0 SUI~iARY OF THE INVENTION
According to the invention there is provided a pump or compressor of a centrifugal type for providing high pressures, comprising: a rotary shaft; a motor connected to the shaft; an impeller connected to the shaft and surrounded by a housing, where the impeller comprises a circular disk connected to a hub; a first set of two or more vanes provided on each side of the circular disk; cover disks provided on the edges of the first set of vanes; and a second set of two or more vanes provided on the outwardly directed sides of the cover disks, where two pressure steps are formed by the first set of vanes, each side of the circular disk and the cover disks, and an additional two pressure steps are formed by the second set of vanes, the cover disks, and a set of pump housing walls located adjacently to the second set of vanes, with single or multiple flow conduits arranged between the outlet of a first pressure step and the inlet of a second pressure step, between the outlet of the second pressure step and the inlet of a third pressure step and between the outlet of the third pressure step and the inlet of a fourth pressure step, and where a last pressure step, which has a highest output pressure, is closer to the motor than any other pressure step and is connected with an outlet, which is located on the same side of the pump or compressor as an inlet and faces in the same direction as the inlet.
In accordance with the invention, a pump or a compressor having more than two pressure steps is provided, which has a very high efficiency due to the minimization of disk losses. The device according to the invention also provides a design that is very compact, easy to mount and adaptable with regard to axial forces and seal pressures.
The present invention, by allowing more than two pressure steps, permits the achievement of higher pump heads. By having a common hub disk, disk losses are minimized and the use of multiple steps results in higher efficiencies, as described above. Additionally, by having a compact, easy to mount design, conventional problems such as complicated service and maintenance, linking losses between steps, and increased mechanical stresses due to long shafts are minimized or avoided.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 shows a sectional view of the pump of an embodiment of the subject invention; and Figure 2 shows the sectional view of Figure 1 inserted in a sectional view of a submersible pump.
DETAILED DESCRIPTION OF THE INVENTION
In the drawings, 1 stands for a rotary shaft and 2 is a pump impeller hub having a disk, 3. 4, 5, 6, and 7 are impeller vanes, 8 and 9 are cover disks and l0 is a part of a pump housing comprising walls 11 and 12 opposing the impeller. 13, 14, 15, 16 and 17 symbolize seals, and 18, 19, 20 and 21 stand for inlets to the pressure steps. 22, 23, 24 and 25 stand for diffusers in the pump steps. 26, 27 and 28 stand for flow conduits and 29 and 30 stand for the inlet and the outlet, respectively, for the pump. 31 stands for the motor unit.
According to the invention, the high-pressure pump comprises a pump housing 10 within which a rotating hub 2 with a connected disk 3 is arranged. The disk 3 is on each side provided with vanes 5 and 6 respectively.
Each group of vanes 5 and 6 are provided with a cover disk 8 and 9, respectively, thereby creating a double-2o sided closed pump impeller. The cover disks 8 and 9 are on their respective opposite sides provided with additional vanes which form another double sided pump impeller together with the pump housing walls 11 and 12, respectively. In this way, a four-step pump impeller is created having two closed and two open channels.
The pump operates in the following way: the liquid is sucked in through the inlet 29 and flows to the inlet 18 of the first pressure step. This step is formed by the vanes 4, the cover disk 8 and the pump housing wall 11.
A flow conduit 26 goes from the diffuser 22 of said first pressure step to the inlet 19 of a second pressure step, said second step being formed by the vanes 5, the underside of the hub disk 3 and the cover disk 8. A second flow conduit 27 goes from the diffuser 23 of said second pressure step to the inlet 20 of a third pressure step, said third 5 step being formed by the vanes 6, the upside of the hub disk 3 and the cover disk 9. A third flow conduit 28 goes from the diffuser 24 of said third pressure step to the inlet 21 of a fourth pressure step, said fourth step being formed by the vanes 7, the cover disk 9 and the pump housing wall 12.
Finally, the liquid leaves the pump via the diffuser 25 of the fourth pressure step through the outlet 30.
The pump according to the present invention provides a number of advantages when compared with conventional high-pressure pumps having one or several pressure steps.
The efficiency is very high because multiple pressure steps bring about more favorable specific rotation speeds and considerable reductions in disk losses.
As shown in Figure 1, the last pressure step, having the highest output pressure, is located adjacently to the motor unit 31 and closer to the motor unit 31 than any other pressure step. Additionally, the outlet 30, connected to the last pressure step, is located on the same side of the device as the inlet 29 and faces in the same direction as the inlet 29. This design, where both the inlet 29 and the outlet 30 are located on the same side of the device and also near the motor unit, results in a very compact, substantially symmetrical pump. This highly compact, symmetrical design results in greater opportunities to reduce axial forces, as well as seal pressures, when compared with conventional devices. Problems such as complicated service and maintenance, linking losses between steps, and increased mechanical stresses due to long shafts are also minimized. The simple design also results in a pump that is much easier to mount than conventional multi-step pumps.
In the embodiment of the invention that is described above, the importance of minimizing the pressure difference between two adjacent pressure steps has been stressed. If it is more important to minimize the axial forces, another order between the steps might be preferable.
It is anticipated by the invention that various such mutual orders of the pressure steps may be employed. The scope of the invention also includes an embodiment where all of the channels in the impeller are closed.
As previously mentioned, the invention is not limited to pumps for liquids, but is also applicable for the pressurizing of gaseous media.
FIELD OF THE INVENTION
The invention relates to a high-pressure machine, and more particularly, to a pump for liquids or a compressor for obtaining a media transport, including gaseous media, under high pressure.
BACKGROUND OF THE INVENTION
When pumping liquids to high levels where consequent high pressures are required, a pump of the centrifugal type is preferred. Such a pump comprises a pump impeller on a rotating shaft, such an impeller being designed with a hub and a circular disk provided with one or several impeller vanes. The liquid enters in an axial direction in the center and leaves the impeller at the periphery. A pump housing surrounding the impeller transforms the kinetic energy to pressure energy, thereby raising the transport to a higher level.
At higher heads, it is common to use pumps with high rotation speeds and relatively small diameters. It is also possible to connect a number of pumps in series by connecting the outlet from a first step to the inlet in a second step and so on. An example is shown in EP-A-355781, where five steps are connected in series.
When a certain operation point at a certain rotation speed is chosen, it can be an advantage to use several steps, as the pump impellers can operate at rotation speeds which are superior in terms of efficiency. This increase of efficiency is mainly related to the fact that the friction losses at the back sides of the impeller hubs, as a part of the total losses, decrease. However, linking losses between the steps are added. A further disadvantage is that the relatively complicated design means that service and maintenance become complicated and in addition, long shafts bring about increased mechanical stress.
Another way to obtain high pump heads is to connect two identical pressure steps in series as is shown in US-A-958 765 and DE-353 698. The pump impellers are here arranged mirror-inverted, but have in other respects conventional designs. US-A-2 136 939 discloses a pump with two pressure steps having a common hub disk, thereby obtaining a reduction of the disk losses. Both of these solutions, however, have in common the problem that they only allow two pressure steps. Therefore, these conventional solutions are not always sufficient in terms of obtaining the desired pump head.
What is needed, therefore, is a pump or compressor having more than two pressure steps that can achieve a high efficiency, while minimizing linking losses and avoiding complicated designs.
2 0 SUI~iARY OF THE INVENTION
According to the invention there is provided a pump or compressor of a centrifugal type for providing high pressures, comprising: a rotary shaft; a motor connected to the shaft; an impeller connected to the shaft and surrounded by a housing, where the impeller comprises a circular disk connected to a hub; a first set of two or more vanes provided on each side of the circular disk; cover disks provided on the edges of the first set of vanes; and a second set of two or more vanes provided on the outwardly directed sides of the cover disks, where two pressure steps are formed by the first set of vanes, each side of the circular disk and the cover disks, and an additional two pressure steps are formed by the second set of vanes, the cover disks, and a set of pump housing walls located adjacently to the second set of vanes, with single or multiple flow conduits arranged between the outlet of a first pressure step and the inlet of a second pressure step, between the outlet of the second pressure step and the inlet of a third pressure step and between the outlet of the third pressure step and the inlet of a fourth pressure step, and where a last pressure step, which has a highest output pressure, is closer to the motor than any other pressure step and is connected with an outlet, which is located on the same side of the pump or compressor as an inlet and faces in the same direction as the inlet.
In accordance with the invention, a pump or a compressor having more than two pressure steps is provided, which has a very high efficiency due to the minimization of disk losses. The device according to the invention also provides a design that is very compact, easy to mount and adaptable with regard to axial forces and seal pressures.
The present invention, by allowing more than two pressure steps, permits the achievement of higher pump heads. By having a common hub disk, disk losses are minimized and the use of multiple steps results in higher efficiencies, as described above. Additionally, by having a compact, easy to mount design, conventional problems such as complicated service and maintenance, linking losses between steps, and increased mechanical stresses due to long shafts are minimized or avoided.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 shows a sectional view of the pump of an embodiment of the subject invention; and Figure 2 shows the sectional view of Figure 1 inserted in a sectional view of a submersible pump.
DETAILED DESCRIPTION OF THE INVENTION
In the drawings, 1 stands for a rotary shaft and 2 is a pump impeller hub having a disk, 3. 4, 5, 6, and 7 are impeller vanes, 8 and 9 are cover disks and l0 is a part of a pump housing comprising walls 11 and 12 opposing the impeller. 13, 14, 15, 16 and 17 symbolize seals, and 18, 19, 20 and 21 stand for inlets to the pressure steps. 22, 23, 24 and 25 stand for diffusers in the pump steps. 26, 27 and 28 stand for flow conduits and 29 and 30 stand for the inlet and the outlet, respectively, for the pump. 31 stands for the motor unit.
According to the invention, the high-pressure pump comprises a pump housing 10 within which a rotating hub 2 with a connected disk 3 is arranged. The disk 3 is on each side provided with vanes 5 and 6 respectively.
Each group of vanes 5 and 6 are provided with a cover disk 8 and 9, respectively, thereby creating a double-2o sided closed pump impeller. The cover disks 8 and 9 are on their respective opposite sides provided with additional vanes which form another double sided pump impeller together with the pump housing walls 11 and 12, respectively. In this way, a four-step pump impeller is created having two closed and two open channels.
The pump operates in the following way: the liquid is sucked in through the inlet 29 and flows to the inlet 18 of the first pressure step. This step is formed by the vanes 4, the cover disk 8 and the pump housing wall 11.
A flow conduit 26 goes from the diffuser 22 of said first pressure step to the inlet 19 of a second pressure step, said second step being formed by the vanes 5, the underside of the hub disk 3 and the cover disk 8. A second flow conduit 27 goes from the diffuser 23 of said second pressure step to the inlet 20 of a third pressure step, said third 5 step being formed by the vanes 6, the upside of the hub disk 3 and the cover disk 9. A third flow conduit 28 goes from the diffuser 24 of said third pressure step to the inlet 21 of a fourth pressure step, said fourth step being formed by the vanes 7, the cover disk 9 and the pump housing wall 12.
Finally, the liquid leaves the pump via the diffuser 25 of the fourth pressure step through the outlet 30.
The pump according to the present invention provides a number of advantages when compared with conventional high-pressure pumps having one or several pressure steps.
The efficiency is very high because multiple pressure steps bring about more favorable specific rotation speeds and considerable reductions in disk losses.
As shown in Figure 1, the last pressure step, having the highest output pressure, is located adjacently to the motor unit 31 and closer to the motor unit 31 than any other pressure step. Additionally, the outlet 30, connected to the last pressure step, is located on the same side of the device as the inlet 29 and faces in the same direction as the inlet 29. This design, where both the inlet 29 and the outlet 30 are located on the same side of the device and also near the motor unit, results in a very compact, substantially symmetrical pump. This highly compact, symmetrical design results in greater opportunities to reduce axial forces, as well as seal pressures, when compared with conventional devices. Problems such as complicated service and maintenance, linking losses between steps, and increased mechanical stresses due to long shafts are also minimized. The simple design also results in a pump that is much easier to mount than conventional multi-step pumps.
In the embodiment of the invention that is described above, the importance of minimizing the pressure difference between two adjacent pressure steps has been stressed. If it is more important to minimize the axial forces, another order between the steps might be preferable.
It is anticipated by the invention that various such mutual orders of the pressure steps may be employed. The scope of the invention also includes an embodiment where all of the channels in the impeller are closed.
As previously mentioned, the invention is not limited to pumps for liquids, but is also applicable for the pressurizing of gaseous media.
Claims
1. A pump or compressor of a centrifugal type for providing high pressures, comprising:
a rotary shaft;
a motor connected to the shaft;
an impeller connected to the shaft and surrounded by a housing, where the impeller comprises a circular disk connected to a hub;
a first set of two or more vanes provided on each side of the circular disk;
cover disks provided on the edges of the first set of vanes; and a second set of two or more vanes provided on the outwardly directed sides of the cover disks, where two pressure steps are formed by the first set of vanes, each side of the circular disk and the cover disks, and an additional two pressure steps are formed by the second set of vanes, the cover disks, and a set of pump housing walls located adjacently to the second set of vanes, with single or multiple flow conduits arranged between the outlet of a first pressure step and the inlet of a second pressure step, between the outlet of the second pressure step and the inlet of a third pressure step and between the outlet of the third pressure step and the inlet of a fourth pressure step, and where a last pressure step, which has a highest output pressure, is closer to the motor than any other pressure step and is connected with an outlet, which is located on the same side of the pump or compressor as an inlet and faces in the same direction as the inlet.
a rotary shaft;
a motor connected to the shaft;
an impeller connected to the shaft and surrounded by a housing, where the impeller comprises a circular disk connected to a hub;
a first set of two or more vanes provided on each side of the circular disk;
cover disks provided on the edges of the first set of vanes; and a second set of two or more vanes provided on the outwardly directed sides of the cover disks, where two pressure steps are formed by the first set of vanes, each side of the circular disk and the cover disks, and an additional two pressure steps are formed by the second set of vanes, the cover disks, and a set of pump housing walls located adjacently to the second set of vanes, with single or multiple flow conduits arranged between the outlet of a first pressure step and the inlet of a second pressure step, between the outlet of the second pressure step and the inlet of a third pressure step and between the outlet of the third pressure step and the inlet of a fourth pressure step, and where a last pressure step, which has a highest output pressure, is closer to the motor than any other pressure step and is connected with an outlet, which is located on the same side of the pump or compressor as an inlet and faces in the same direction as the inlet.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE9903278-1 | 1999-09-15 | ||
| SE9903278A SE521399C2 (en) | 1999-09-15 | 1999-09-15 | Rotodynamic high pressure machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2319607A1 CA2319607A1 (en) | 2001-03-15 |
| CA2319607C true CA2319607C (en) | 2003-11-04 |
Family
ID=20416981
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002319607A Expired - Fee Related CA2319607C (en) | 1999-09-15 | 2000-09-14 | A roto-dynamic high pressure machine |
Country Status (11)
| Country | Link |
|---|---|
| EP (1) | EP1085212B1 (en) |
| JP (1) | JP2001099091A (en) |
| AR (1) | AR026878A1 (en) |
| AT (1) | ATE319934T1 (en) |
| AU (1) | AU762289B2 (en) |
| BR (1) | BR0004211A (en) |
| CA (1) | CA2319607C (en) |
| DE (1) | DE60026490T2 (en) |
| MX (1) | MXPA00008931A (en) |
| SE (1) | SE521399C2 (en) |
| ZA (1) | ZA200004443B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB0916901D0 (en) * | 2009-09-25 | 2009-11-11 | Dynamic Boosting Systems Ltd | Diffuser |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE155337C (en) * | ||||
| CH93071A (en) * | 1918-11-01 | 1922-02-16 | Johnston Frame William | Further development in ventilators and multistage centrifugal pumps. |
| DE345856C (en) * | 1920-02-20 | 1921-12-17 | Bbc Brown Boveri & Cie | Centrifugal machine for compressing and conveying gases or liquids with several stages connected in series |
| CH252609A (en) * | 1945-01-13 | 1948-01-15 | Sulzer Ag | Multi-stage compressor. |
| US3102680A (en) * | 1961-06-27 | 1963-09-03 | Sam F Fogleman | Multistage centrifugal gas compressor |
| DE2115330A1 (en) * | 1971-03-30 | 1972-10-19 | Demag Ag | Multi-stage compressor of radial or semi-radial design |
-
1999
- 1999-09-15 SE SE9903278A patent/SE521399C2/en not_active IP Right Cessation
-
2000
- 2000-08-21 ZA ZA200004443A patent/ZA200004443B/en unknown
- 2000-08-23 DE DE60026490T patent/DE60026490T2/en not_active Expired - Fee Related
- 2000-08-23 AT AT00850140T patent/ATE319934T1/en not_active IP Right Cessation
- 2000-08-23 EP EP00850140A patent/EP1085212B1/en not_active Expired - Lifetime
- 2000-09-07 AR ARP000104695A patent/AR026878A1/en not_active Application Discontinuation
- 2000-09-12 MX MXPA00008931A patent/MXPA00008931A/en unknown
- 2000-09-13 AU AU59418/00A patent/AU762289B2/en not_active Ceased
- 2000-09-14 CA CA002319607A patent/CA2319607C/en not_active Expired - Fee Related
- 2000-09-14 JP JP2000279423A patent/JP2001099091A/en active Pending
- 2000-09-15 BR BR0004211-0A patent/BR0004211A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| EP1085212B1 (en) | 2006-03-08 |
| MXPA00008931A (en) | 2004-10-15 |
| AU5941800A (en) | 2001-03-22 |
| ATE319934T1 (en) | 2006-03-15 |
| EP1085212A3 (en) | 2002-05-29 |
| AU762289B2 (en) | 2003-06-19 |
| SE9903278D0 (en) | 1999-09-15 |
| SE521399C2 (en) | 2003-10-28 |
| EP1085212A2 (en) | 2001-03-21 |
| AR026878A1 (en) | 2003-03-05 |
| JP2001099091A (en) | 2001-04-10 |
| ZA200004443B (en) | 2001-05-22 |
| DE60026490T2 (en) | 2006-10-12 |
| CA2319607A1 (en) | 2001-03-15 |
| BR0004211A (en) | 2001-04-10 |
| DE60026490D1 (en) | 2006-05-04 |
| SE9903278L (en) | 2001-03-16 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |