EP0544693A1 - Axialschubausgleich für kreiselpumpen. - Google Patents
Axialschubausgleich für kreiselpumpen.Info
- Publication number
- EP0544693A1 EP0544693A1 EP91913014A EP91913014A EP0544693A1 EP 0544693 A1 EP0544693 A1 EP 0544693A1 EP 91913014 A EP91913014 A EP 91913014A EP 91913014 A EP91913014 A EP 91913014A EP 0544693 A1 EP0544693 A1 EP 0544693A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- pressure
- axial thrust
- compensation
- gap
- 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.)
- Granted
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
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
Definitions
- the invention relates to a device for fully compensating the axial thrust in centrifugal pumps according to the preamble of claim 1.
- the known devices for the hydraulic axial thrust compensation are, as far as their effect depends on a pressure difference between the pump suction and the pressure side, only able to work properly as long as a sufficient pressure difference is available. This applies especially to single-stage, specifically high-speed pumps, which, due to the low delivery heads, only have small pressure differences available to compensate for the axial forces. Because namely the delivery head becomes ever smaller with increasing delivery flow, the impeller may rub against a fixed part of the centrifugal pump below a maximum possible delivery head.
- the hydraulic axial thrust compensation is essentially based on the fact that the force acting on one side of the compensation piston remains practically constant at a certain operating point of the centrifugal pump, while the force acting on the other side of the compensation piston changes due to the axial adjustment of the piston becomes.
- This change is produced in that the pressure on the compensating piston is varied in a variable gap by throttling depending on its axial position.
- the throttling effect in gaps is very much dependent on the available pressure difference, the control becomes worse and worse with small pressure differences. Since the pressure difference at the throttle gap is proportional to the delivery head of the pump, the problems mentioned occur above all in the overload range, i.e. above an optimal delivery rate.
- the invention has for its object to provide a device of the type mentioned in the preamble of claim 1, which does not require a touching bearing.
- a second, also hydraulically acting compensation system is set, which does not depend on the pump head as the active force and is therefore able to independently compensate the axial forces completely at small pump heads to reach.
- the pressure increase in the pressure side space of the impeller can be accomplished in different ways. Provided that the annular area formed on the suction side between the sealing ring and the outer diameter of the impeller is smaller than the area available on the pressure side, a conveyance caused by the surface roughness of the impeller can already bring about a corresponding pressure increase. This effect can be increased if the roughness of the impeller wall on the suction side is less than that of the impeller wall on the pressure side. But above all, back shovels are capable. or similar funding to achieve the necessary pressure increase without further notice.
- the invention is explained in more detail using an exemplary embodiment. This is based on the description of a known device for compensating the axial thrust, which can be seen in FIG. 3 in a sectional view of a centrifugal pump. 4 shows a diagram of the various forces acting on the side walls of the impeller of this pump as a function of the control gap.
- FIG. 1 shows a device according to the invention for hydraulic compensation of the axial thrust in connection with a centrifugal pump shown in sections.
- a diagram corresponding to this axial thrust compensation is shown in FIG. 2.
- the centrifugal pump shown in FIG. 3 with a known type of axial thrust compensation device has an impeller (2) arranged in a housing (1). Between the housing (1) and the impeller (2) two gaps S-- and S 2 are used to compensate for axial thrust. The width of the gap S-- changes with the axial position of the impeller (2), the width of the gap S 2 remains constant even when the impeller 2 is displaced.
- the housing (1), the impeller (2) and the gaps S-- and S 2 form different, distinguishable spaces: a space (3) in front of the impeller (2), in which a pressure P- ⁇ prevails; a room (4) located behind the impeller (2), which has a pressure P 2 increased by the conveying action of the impeller (2), and a space (5) located between the columns S-- and S 2 , in which a There is an intermediate pressure P 3 .
- Axial forces F 1 and F act on the side walls of the impeller (2) with opposite directions.
- the force F 2 is proportional to the pressure P 2 , which in turn is dependent from the head.
- the force F-_ depends on the variable gap S--.
- the embodiment according to the invention shown in FIG. 1 has a first compensation device which corresponds to the device shown in FIG. 3. It also has gaps S-- and S 2 and a space (5) delimited by them, without all of these details being shown in FIG. 1. The effect of this first compensation device is also the same as that of the device in FIG.
- FIG. 1 has a second hydraulic compensation device which is used in the overload range of the centrifugal pump.
- the elements of this second device are: a collar (8) arranged on the pressure side on the circumference of the impeller (7), openings (9) which connect the inlet (10) of the impeller (7) to the pressure side space (11), and back blades ( 12).
- the impeller (7) forms two variable gaps with the pump housing 1: the gap S-- at the impeller inlet and the gap S 3 at the collar (8).
- the pressures P- ⁇ and P 2 and the force F-- are the pressures P- ⁇ and P 2 and the force F--. Since the side space (11) formed between the pressure-side cover disk of the impeller (7) and the pump housing (1) is delimited by the collar (8) and the gap S with respect to the pressure-side space (4), a pressure of its own arises here P 4 a. Proportional to the pressure P ⁇ is a force F ' 2 which is opposite to the force F- ⁇ .
- the delivery height of the back vanes (12) begins to exceed the impeller delivery height.
- a flow is introduced from the inlet (10) via the openings (9), the space (11) and the collar (8) to the pressure-side space (4).
- the pressure P 4 which arises in space (11) now becomes greater the smaller the gap S 3 becomes.
- the difference between the pressures P 4 and P 2 also increases as the gap S 3 becomes smaller.
- the force F ' 2 increases and moves the impeller (7) back into an equilibrium position before it can start on the pump housing (1).
- the force F ' 2 is therefore no longer independent of the gap S-, as was the force F 2 in the previously known embodiment of FIG. 3. It changes with the gap S 3 , which in turn changes in mirror image reversal to the gap S--. The result of this is that the force F ' 2 , which increases from a certain gap width, has a profile which certainly results in an intersection with the profile of the force F-. The diagram shown in FIG. 2 illustrates this.
- FIG. 1 represents a device for the complete compensation of the axial thrust, which in addition to a first compensation system, which corresponds to the compensation device of FIG. 3, sets a second, contact-free compensation system.
- the two systems used together work together to create a new, independent compensation device.
- the part referred to here as the second compensation system can also be used a different type of system, which takes over the axial thrust compensation for the normal operation of the centrifugal pump outside the overload range, can be summarized.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Nitrogen Condensed Heterocyclic Rings (AREA)
- Control Of Transmission Device (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4026905A DE4026905A1 (de) | 1990-08-25 | 1990-08-25 | Axialschubausgleich fuer kreiselpumpen |
DE4026905 | 1990-08-25 | ||
PCT/EP1991/001357 WO1992003662A1 (de) | 1990-08-25 | 1991-07-19 | Axialschubausgleich für kreiselpumpen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0544693A1 true EP0544693A1 (de) | 1993-06-09 |
EP0544693B1 EP0544693B1 (de) | 1994-09-21 |
Family
ID=6412905
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP91913014A Expired - Lifetime EP0544693B1 (de) | 1990-08-25 | 1991-07-19 | Axialschubausgleich für kreiselpumpen |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0544693B1 (de) |
AT (1) | ATE112019T1 (de) |
DE (2) | DE4026905A1 (de) |
WO (1) | WO1992003662A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2567582B (en) * | 2016-08-08 | 2022-06-01 | Efficient Energy Gmbh | Electric disc armature comprising a pressure reducer for the motor gap |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4421888A1 (de) | 1994-06-23 | 1996-01-04 | Klein Schanzlin & Becker Ag | Einrichtung zum Axialschubausgleich bei Kreiselpumpen |
ES2130945B1 (es) * | 1996-07-03 | 2000-02-16 | Bombas Electricas Sa | Bomba centrifuga de tipo vortice. |
SE525029C2 (sv) * | 2001-07-13 | 2004-11-16 | Abs Pump Prod Ab | Anordning vid centrifugalpump |
US6824350B2 (en) * | 2003-02-25 | 2004-11-30 | Careseal, S.L. | Hydrodynamic sealing system for centrifugal systems |
CN103016395A (zh) * | 2012-12-11 | 2013-04-03 | 江苏大学 | 离心泵叶轮不等扬程水力设计方法 |
CN103104547A (zh) * | 2013-03-07 | 2013-05-15 | 江苏大学 | 气液两相流核主泵叶轮不等扬程水力设计方法 |
DE102017211940A1 (de) * | 2017-07-12 | 2019-01-17 | Bayerische Motoren Werke Aktiengesellschaft | Brennstoffzellensystem für ein Kraftfahrzeug sowie Strömungsmaschine für ein Brennstoffzellensystem |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1323412A (en) * | 1919-12-02 | schorr | ||
DE497595C (de) * | 1930-05-09 | Aeg | Einseitig saugende Kreiselpumpe | |
US1488931A (en) * | 1921-10-26 | 1924-04-01 | Marechal Paul Joseph Charles | Turbo engine |
US1999163A (en) * | 1929-06-04 | 1935-04-23 | Allen Sherman Hoff Co | Centrifugal pump |
FR876247A (fr) * | 1941-06-18 | 1942-10-30 | Rateau Soc | équilibrage axial automatique pour turbomachine |
JPS4938641B1 (de) * | 1970-08-06 | 1974-10-19 | ||
DE2733631A1 (de) * | 1977-07-26 | 1979-02-08 | Hermetic Pumpen Gmbh | Kreiselpumpe |
US4867633A (en) * | 1988-02-18 | 1989-09-19 | Sundstrand Corporation | Centrifugal pump with hydraulic thrust balance and tandem axial seals |
-
1990
- 1990-08-25 DE DE4026905A patent/DE4026905A1/de not_active Withdrawn
-
1991
- 1991-07-19 WO PCT/EP1991/001357 patent/WO1992003662A1/de active IP Right Grant
- 1991-07-19 EP EP91913014A patent/EP0544693B1/de not_active Expired - Lifetime
- 1991-07-19 DE DE59103062T patent/DE59103062D1/de not_active Expired - Fee Related
- 1991-07-19 AT AT91913014T patent/ATE112019T1/de not_active IP Right Cessation
Non-Patent Citations (1)
Title |
---|
See references of WO9203662A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2567582B (en) * | 2016-08-08 | 2022-06-01 | Efficient Energy Gmbh | Electric disc armature comprising a pressure reducer for the motor gap |
Also Published As
Publication number | Publication date |
---|---|
DE59103062D1 (de) | 1994-10-27 |
DE4026905A1 (de) | 1992-02-27 |
ATE112019T1 (de) | 1994-10-15 |
EP0544693B1 (de) | 1994-09-21 |
WO1992003662A1 (de) | 1992-03-05 |
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