EP0855516B1 - Nasslaufender Tauchmotor zum Antreiben einer Kreiselpumpe - Google Patents
Nasslaufender Tauchmotor zum Antreiben einer Kreiselpumpe Download PDFInfo
- Publication number
- EP0855516B1 EP0855516B1 EP98100960A EP98100960A EP0855516B1 EP 0855516 B1 EP0855516 B1 EP 0855516B1 EP 98100960 A EP98100960 A EP 98100960A EP 98100960 A EP98100960 A EP 98100960A EP 0855516 B1 EP0855516 B1 EP 0855516B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- pump
- shaft
- space
- 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.)
- Expired - Lifetime
Links
Images
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
- 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
- F04D13/062—Canned motor pumps pressure compensation between motor- and pump- compartment
Definitions
- the invention is based on a wet-running submersible motor the preamble of claim 1.
- DE-38 28 512 A1 describes a submersible pump unit with a Wet running motor shown, in which the motor in a housing that in a liquid to be pumped is immersed, has a rotor, which is surrounded by a can and a central shaft is carried, which is in both ends of the engine in plain bearings is supported.
- the one protruding from the motor housing is on the pump side Shaft surrounded by a seal formation around the Seal the rotor space of the motor towards the pump side.
- the shaft is hollow over its entire length and is on its end protruding from the motor on the pump side with a Centrifugal pump connectable.
- the wave is at least partially with filled with a liquid and at its pump end with a plug sealed liquid-tight, so that the Liquid cannot escape from the shaft. After all, that is space formed by the can for the rotor of the motor for cooling purposes filled with liquid. Via the intermediate coolant in the hollow shaft, the engine heat becomes the pump area or transferred to the pumped liquid located there, so as to cool the engine.
- the object of the invention is therefore to improve one Wet-running engine of the type mentioned in the introduction that its rotor space is vented automatically after the engine is started and completely fills with liquid, taking an exchange of liquid between rotor space and pump side of the motor during its operation largely to avoid disadvantages for the engine is prevented.
- a wet-running submersible constructed in accordance with the invention can after its manufacture with partial pre-filling of its rotor space delivered safely because there is no risk of leakage consists of the rotor space more and it is ensured that the Rotor space automatically with a after starting the engine Fills part of the liquid to be pumped completely while doing so vented at the same time. It is no longer necessary for the engine must be refilled by the assembly staff at the customer.
- immersing the submersible that is not switched on together with the submersible pump mounted on it into the liquid to be pumped is a sufficient minimum amount of liquid due to the partial priming present in the rotor space, which is a lubrication of the Engine mounts and sufficient engine cooling at the beginning guaranteed its operation.
- the seal design of the submersible is in all embodiments basically designed so that an essential Liquid exchange between the rotor chamber and the pump side of the running Motor no longer takes place when the rotor space is filled is.
- the submersible motor designed according to the invention and its packaging furthermore do not suffer any damage during transport and / or storage because of freezing temperatures conditional leakage of liquid through the partial priming of the Rotor space is avoided from the rotor space.
- the submersible motor is mainly used to drive centrifugal pumps used in wells, especially deep wells, where it In the case of centrifugal pumps, this is advantageous for multi-stage centrifugal pumps acts with which the cold water is conveyed upwards.
- the Submersible motor can also be used to operate centrifugal pumps in one other relatively cold liquid. Therefore is a constant exchange of liquid in the rotor space during the Motor operation not required. Nevertheless, it is sufficient Heat dissipation from the rotor chamber ensures compared to an air filling of the rotor space.
- An advantageous embodiment of the functional unit in the pump side Outstanding shaft end area from the seal design is that this unit as a simple, pump direction permeable valve is formed with a spring-loaded valve body.
- the mentioned functional unit on the pump side Area of the hollow shaft of the motor also in both axial Directions of the shaft be fluid permeable, e.g. B. by use a double valve.
- the wet-running Submersible motor or its rotor space delivered without liquid be, e.g. B. for smaller sizes.
- the double valve leaves both additional liquid and air from the rotor space emerge so that this space more easily with liquid crowded.
- the submersible motor according to the invention can be used in this embodiment in dry running, i.e. with the rotor space unfilled, be checked if the customer provides a performance data protocol for the not get the desired wet-running submersible wishes if the manufacturer of the submersible motor give the guarantee can guarantee that the performance data of the submersible concerned are. This eliminates the need to fill the rotor space Check the submersible motor and then empty the rotor chamber.
- Fig. 1 the wet-running submersible 1 is shown completely.
- an outer, tubular housing 2 is the usual electric stator 3, which in its interior by a canned pot 4 is limited.
- the canned pot is at the pump end 4 connected to the housing 2 in a liquid-tight manner in the usual way.
- the electrical one is inside the canned pot
- Rotor 5 on a central, in the example shown in their entire length hollow motor shaft 6 is attached.
- the In turn, shaft 6 is in a front slide bearing 7 and in one rear slide bearing 8 rotatably mounted in the usual manner.
- Over a Bearing sleeve 9 supports the rotor 5 during operation of the engine on the front slide bearing 7 axially.
- the motor 1 has an end wall 10 provided, which are firmly connected to the housing 2 and opposite this is sealed in the usual way.
- the end wall 10 has a depression 11 in its central area, in which a seal formation 12 is arranged.
- This training 12 can be a lip seal, for example a Simmerring seal.
- the usual sealing element e.g. B. an annular lip
- the seal formation is sealing against the hollow motor shaft 6 and therefore seals the rotor chamber 13 of the motor 1 to the pump side except for the usual, negligible leakage loss.
- the Seal formation 12 is to be arranged in the recess 11 that the sealing effect of the sealing element of the seal formation in Operation of the engine becomes larger, the more the sealing element Seal formation 12 from the inside of the engine with fluid pressure is applied. For example, this is symbolic in the figures with the direction shown in the seal formation 12 Arrows 43 ( Figures 2 and 3) indicated. The sealing element is then pressed more strongly against the shaft 6.
- the end wall 10 On its pump side is the end wall 10 with several grub screws 14 provided on which the housing of the, not shown, usually multi-stage submersible pump of the centrifugal pump type, which is to be driven by the motor 1 is attached.
- the hollow shaft 6 In front of the end wall 10 is the hollow shaft 6 with inner radial Flow passages 15 provided so that when the rotor space 13th is filled with liquid, a liquid circulation within the rotor space can take place in the usual way.
- the hollow wave exerts a pumping action in the operation of the motor 1 even when the rotor space 13 is only partially filled with liquid. It is so ensured that both the lower slide bearing 8 and that upper radial slide bearing 7 sufficient at the start of operation of the engine be lubricated.
- the hollow shaft 6 is at a radial distance from a sleeve 16 surrounded, which extends from the end wall 10 inwards.
- the sleeve 16 serves at its motor end as a support body for the front slide bearing 7.
- a chamber 18 is formed, which differ from the seal formation 12 as an annular space extends to the front shaft slide bearing 7.
- This chamber ensures that that through the flow passages 15 of the shaft 6 in this chamber fluid inevitably reached the plain bearing 7 over a short distance is passed to lubricate it safely.
- it can Bearing 7 on its outer circumference with a plurality of flow paths 19 be provided to conduct liquid into the rotor space 13. additionally or alternatively, holes 20 can also be provided in the sleeve 16 to be liquid in the front part of the rotor space 13 to lead.
- a functional unit 22 In the end region of the hollow motor shaft 6, which comes from the end wall 10 protrudes centrally outwards, there is a functional unit 22.
- This functional unit is designed according to Fig. 1 that Fluid under certain conditions from the rotor chamber 13 through the Wave 6 can escape to the pump side. This essentially becomes initially be air around the partially pre-filled at the factory Vent the rotor chamber. The simultaneous penetration of liquid from the pump side takes place via the seal formation 12, because this, as indicated by the arrows 43 pointing inwards, so is designed and installed that the penetration of liquid from the pump into the rotor space 13 in order to make it more complete Filling is ensured without the required sealing effect the seal 12 is significantly weakened.
- the functional unit 22 can also be designed such that in addition to the way through the seal formation 12 also 22 can convey liquid through this unit to the To fill the rotor chamber 13 via the flow passages 15. simultaneously can also vent the rotor chamber, that is a discharge of air from this room via the functional unit 22 done according to arrow A. Is the rotor space 13 complete filled with fluid and this fluid has become in the course the operation of the motor 1 due to heat development in the rotor 5 warmed up, this creates an overpressure in the rotor space. This overpressure is also immediately dismantled via the functional unit 22 because then a certain small proportion of liquid via this unit can escape to the pump.
- the functional unit 22 can therefore be of various designs be provided. 1 and 2 such a unit is shown, the fluid permeability in one direction, that is only towards the pump side, is permitted in FIGS. 3 and 4 such a unit is shown which has a fluid flow to both the pump side towards and at the same time from the pump side to the rotor space allowed. In the embodiment according to FIGS. 1 and 2 it is a single valve 23, while it is in Fig. 3 and 4 is a double valve 24.
- the functional unit 22 is in the form of the single valve 23 recognizable more clearly. You can see that this is a valve acts with a spring-loaded valve body 26. According to the arrow A, the valve body 26 is lifted from its seat when in the operation of the engine in the rotor space 13 and in the chamber 18 Has developed overpressure. This overpressure is initially caused by the Air in the rotor space, which continuously escapes through the valve 23, exercised, due to the more in the rotor space and more penetrating fluid. Then it is filled Rotor space the liquid heated by the running engine in if necessary, apply pressure to the valve in this space, to relieve the excess liquid pressure.
- Double valve 24 is designed as a two-way valve Double valve 24 can be clearly recognized in its structure. It includes a common cylindrical housing 30 with a rear flow opening 31 and a pump-side filter insert 32. A The corresponding filter insert can also be placed in front of the simple valve 23 be provided according to Figures 1, 2, 3, 5, 6 and 7.
- Within of the housing 30 is a first valve seat ring 33 on the pump side a front flow opening 34 is provided, with rotor space side a first tubular valve body 35 on the valve seat ring 33 is applied.
- This valve body 35 has a central one on the pump side Passage 36 communicating with opening 34.
- a first one Load spring 37 for example a coil spring, presses the Valve body 35 against the valve seat ring 33.
- first valve body 35 On the rotor chamber side open end of the first valve body 35 is a second valve seat ring 38, with the help of the pressure of a second Loading spring 39, which on the other hand abuts the housing 30 and can also be a helical spring.
- a second Loading spring 39 Inside the first valve body 35 there is an axially displaceably held second tubular valve body 40, with circumferential play. Due to the annular gap formed in this way between the valve bodies Flowing fluid out of the rotor space.
- the second valve body 40 is closed on the motor side and is supported by the first load spring 37 pressed against the second valve seat ring 38.
- the two load springs 37 and 39 are advantageously calculated so that the outflow of fluid from the rotor chamber 13 to the pump side is more easily possible is as an ingress of liquid from the pump side towards the rotor space.
- the motor shaft 6 only partially in its Length is hollow. It is only hollow from the pump side trained, thus has a central channel 50 which extends up to Starting area of the rotor chamber 13 of the engine 1 extends. from flow passages in turn open into the inner end of the channel 50 15 to the rotor space 13.
- the Sleeve 16 a chamber 18 may be formed. Also in this embodiment it is so that the seal formation 12 designed so and is mounted that liquid only from the pump side the seal 12 can reach the rotor chamber 13, that is, in reverse Backflow is not possible, so that then according to arrows 52 with internal pressure on the seal their sealing effect is strengthened.
- valve 53 In the case shown the functional unit 22 from a single valve 53 with a spring-loaded Valve body, this valve only a fluid flow permitted according to arrow B from the rotor space to the pump side.
- the valve 53 is in a recess 55 at the pump end of the shaft used and includes a valve body 56 which on the one hand the shaft 6 and on the other hand by means of a compression spring 57 in Is held in the closed position.
- the compression spring is supported on the other hand on a holding element 58 with a central passage 59.
- the valve 53 with a passage direction only to the pump side can also be a functional unit with two in this example opposite forward directions are used, for example the double valve 24.
- FIG. 6 is compared to that according to FIG. 5 modified in that no chamber 18 is provided.
- the front slide bearing 7, possibly with its axial passages 19, is therefore held in a separate bearing plate 51 to the Support shaft 6 at the front. Otherwise there are no differences to the embodiment according to FIG. 5.
- Embodiments are particularly for very high speeds of wet running submersible.
- FIG. 7 A still further embodiment is shown in FIG. 7.
- This embodiment has compared to the embodiments described above, with which it otherwise agrees, the distinctive Feature that in the front end wall 10 of the engine 1 Inlet valve 60 is provided.
- This valve is constructed and in the wall 10 is mounted so that it only delivers liquid from the pump side Her come into the rotor space 13 of the motor, the reverse So direction blocks and only under certain funding conditions is used.
- the structure of the device valve 60 itself can be designed as described in connection with the single valve 23 is.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
- Fig. 1
- einen Axialschnitt durch einen naßlaufenden Tauchmotor,
- Fig. 2
- eine Teildarstellung der Ausführungsform nach Fig. 1 in vergrößertem Maßstab mit einer ersten Funktionseinheit,
- Fig. 3
- eine der Figur 2 im wesentlichen gleichende Darstellung mit einer zweiten Funktionseinheit,
- Fig. 4
- die zweite Funktionseinheit allein in größerem Maßstab und im Axialschnitt
- Fig. 5
- einen Axialschnitt durch eine weitere Ausführungsform des naßlaufenden Tauchmotors,
- Fig. 6
- eine weitere, gegenüber der Ausführungsform nach Fig. 5 abgeänderte Ausführungsform, wobei nur dessen pumpenseitiger Bereich in vereinfachter Darstellung und im Axialschnitt gezeigt ist,
- Fig. 7
- eine der Fig. 2 ähnliche Darstellung einer noch weiteren Ausführungsform des Tauchmotors.
Claims (6)
- Naßlaufender Tauchmotor (1) zum Antreiben einer Kreiselpumpe, mit einer in dem mit Flüssigkeit füllbaren Rotorraum des Motors einen elektrischen Rotor (5) tragenden Welle (6), die wenigstens auf ihrem pumpenseitigen Längsabschnitt hohl ausgebildet ist, und mit einer die Welle umgebenden Dichtungsausbildung (12) zum Abdichten des Rotorraumes gegenüber der Pumpe, wobei die Welle in vor und hinter dem Rotor angeordneten Gleitlagern (7, 8) gelagert und innerhalb des Motors mit radialen Strömungsdurchlässen (15) versehen ist, dadurch gekennzeichnet, daß das pumpenseitige, hohle Wellenende eine Funktionseinheit (22) aufweist, die wenigstens in Pumpenrichtung fluiddurchlässig ausgebildet ist, um im Betrieb des Motors (1) zwecks Entlüftung seines Rotorraumes (13), der wenigstens über die Dichtungsausbildung (12) selbsttätig mit Förderflüssigkeit füllbar ist, und Abbau von Überdruck im Rotorraum gegenüber dem Flüssigkeitsdruck im Pumpenbereich Fluid aus dem Rotorraum zur Pumpe durchzulassen.
- Naßlaufender Tauchmotor nach Anspruch 1, dadurch gekennzeichnet, daß die Funktionseinheit (22) am pumpenseitigen Ende der Welle (6) als ein in Pumpenrichtung durchlässiges Ventil (23) mit federbelastetem Ventilkörper (26) ausgebildet ist.
- Naßlaufender Tauchmotor nach Anspruch 1, dadurch gekennzeichnet, daß die Funktionseinheit (22) am pumpenseitigen Ende der Welle (6) aus einem Doppelventil (24) besteht, das in beiden axialen Richtungen der Welle (6) sowohl öffnet als auch schließt.
- Naßlaufender Tauchmotor nach Anspruch 3, dadurch gekennzeichnet, daß das Doppelventil (24) ein gemeinsames Gehäuse (30) mit einer vorderen und einer hinteren Durchflußöffnung (34, 31) umfaßt, in dem ein erster, pumpenseitiger Ventilsitzring (33), ein erster rohrförmiger, rotorraumseitiger Ventilkörper (35) mit einem pumpenseitigen, zentralen Durchgang (36), eine erste Belastungsdruckfeder (37), ein innerhalb des ersten rohrfömrigen Ventilkörpers umfangsmäßigem Spiel axial verschieblich gehalterter, zweiter rohrförmiger Ventilkörper (40), ein am rotorraumseitigen offenen Ende des ersten Ventilkörpers (35) vorgesehener zweiter Ventilsitzring (38) und eine zweite, sich am zweiten Ventilsitzring und an dem gemeinsamen Gehäuse abstützende zweite Belastungsdruckfeder (39) vorgesehen sind, wobei sich die erste Belastungsdruckfeder (37) am ersten und zweiten Ventilkörper (35, 40) abstützt.
- Naßlaufender Tauchmotor nach Anspruche 1, dadurch gekennzeichnet, daß der Funktionseinheit (22) ein Filter (32) vorgeordnet ist.
- Naßlaufender Tauchmotor nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Dichtungsausbildung (12) für die Welle (6) derart gestaltet ist, daß sie bei Flüssigkeitsüberdruck im Rotorraum den Austritt von Fluid aus diesem verhindert.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19702723A DE19702723A1 (de) | 1997-01-27 | 1997-01-27 | Naßlaufender Tauchmotor zum Antreiben einer Kreiselpumpe |
DE19702723 | 1997-01-27 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0855516A1 EP0855516A1 (de) | 1998-07-29 |
EP0855516B1 true EP0855516B1 (de) | 2003-06-25 |
Family
ID=7818387
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98100960A Expired - Lifetime EP0855516B1 (de) | 1997-01-27 | 1998-01-21 | Nasslaufender Tauchmotor zum Antreiben einer Kreiselpumpe |
Country Status (3)
Country | Link |
---|---|
US (1) | US6140725A (de) |
EP (1) | EP0855516B1 (de) |
DE (2) | DE19702723A1 (de) |
Families Citing this family (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001298903A (ja) * | 2000-04-10 | 2001-10-26 | Moric Co Ltd | ブラシレスdcモータ |
DE10052797A1 (de) * | 2000-10-25 | 2002-05-08 | Bosch Gmbh Robert | Elektromotorisch angetriebene Pumpe und Verfahren zur Herstellung einer solchen Pumpe |
DE10064717A1 (de) * | 2000-12-22 | 2002-07-11 | Grundfos As | Verfahren zum Betreiben eines Pumpenaggregats |
US20020153789A1 (en) * | 2001-04-19 | 2002-10-24 | Knox Dick L. | Pressurized bearing system for submersible motor |
US7492069B2 (en) * | 2001-04-19 | 2009-02-17 | Baker Hughes Incorporated | Pressurized bearing system for submersible motor |
US6758416B2 (en) | 2002-08-30 | 2004-07-06 | Robert Bosch Gmbh | Fuel injector having an expansion tank accumulator |
WO2004020835A1 (de) * | 2002-08-31 | 2004-03-11 | Oase Gmbh | Tauchmotorpumpe mit frostschutzeinrichtung |
US8910718B2 (en) * | 2003-10-01 | 2014-12-16 | Schlumberger Technology Corporation | System and method for a combined submersible motor and protector |
US20060034717A1 (en) * | 2004-08-13 | 2006-02-16 | Joseph Castellone | Wet rotor circulators |
DE102005056309B4 (de) * | 2005-11-25 | 2007-12-13 | Fpe Fischer Gmbh | Kreiselpumpe mit Entlüftung |
CN100448141C (zh) * | 2006-10-16 | 2008-12-31 | 中山大学 | 交流永磁潜水电机 |
EP2091133B1 (de) | 2008-02-13 | 2012-08-15 | Askoll Holding S.r.l. | Elektrischer Motor und Elektropumpe |
BRPI0802897A2 (pt) * | 2008-08-19 | 2011-04-26 | Higra Ind Ltda | bombas modulares |
DE102010026239B4 (de) * | 2010-06-29 | 2012-05-31 | Joh. Heinr. Bornemann Gmbh | Unterwasserförderaggregat mit einer Pumpe und einer Antriebseinrichtung |
DE102010026132A1 (de) * | 2010-07-05 | 2012-01-05 | Mahle International Gmbh | Laufrad und Fluidpumpe |
US9145865B2 (en) | 2012-06-29 | 2015-09-29 | General Electric Company | Electric fluid pump |
CN102868249B (zh) * | 2012-10-15 | 2014-09-10 | 浙江东音泵业股份有限公司 | 井用潜水电机 |
EP3032712B1 (de) | 2014-12-12 | 2018-02-07 | Goodrich Control Systems | Motor für ein elektrohydraulisches Stellorgan |
US10634152B2 (en) * | 2018-08-17 | 2020-04-28 | Itt Manufacturing Enterprises Llc | Multi-bearing design for shaft stabilization |
EP3763943B1 (de) * | 2019-07-10 | 2024-09-04 | Grundfos Holding A/S | Verfahren zur herstellung eines spalttopfes |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1098820B (de) * | 1959-09-04 | 1961-02-02 | Lederle Pumpen & Maschf | Durch einen Spaltrohrmotor angetriebene mehrstufige Kreiselpumpe |
US3135211A (en) * | 1960-09-28 | 1964-06-02 | Integral Motor Pump Corp | Motor and pump assembly |
US3264653A (en) * | 1964-09-18 | 1966-08-02 | Taco Inc | Pump |
FR1454906A (fr) * | 1965-11-26 | 1966-02-11 | Const Stork Freres & Cie Sa At | Pompe de circulation pour eau chaude |
GB1237633A (en) * | 1968-04-11 | 1971-06-30 | Marelli & C Spa Ercole | Improvements in or relating to electric water-pumps |
FR1581541A (de) * | 1968-05-22 | 1969-09-19 | ||
CH532201A (de) * | 1970-12-11 | 1972-12-31 | Inventio Ag | Schmier- und Filtereinrichtung für Umwälzpumpe |
DE2941133C2 (de) * | 1979-10-10 | 1985-01-31 | Speck-Kolbenpumpen-Fabrik Otto Speck Kg, 8192 Geretsried | Heizungsumwälzpume |
DE8029658U1 (de) * | 1980-11-06 | 1981-02-26 | Hanning & Kahl Gmbh & Co, 4800 Bielefeld | Unterwasserpumpe fuer springbrunnen o.dgl. |
DE3828512A1 (de) | 1988-08-23 | 1990-03-08 | Grundfos Int | Tauchpumpenaggregat |
US5129795A (en) * | 1991-05-31 | 1992-07-14 | Powerdyne Corporation | Motor driven pump |
-
1997
- 1997-01-27 DE DE19702723A patent/DE19702723A1/de not_active Withdrawn
-
1998
- 1998-01-21 EP EP98100960A patent/EP0855516B1/de not_active Expired - Lifetime
- 1998-01-21 DE DE59808774T patent/DE59808774D1/de not_active Expired - Lifetime
- 1998-01-27 US US09/013,967 patent/US6140725A/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP0855516A1 (de) | 1998-07-29 |
DE59808774D1 (de) | 2003-07-31 |
DE19702723A1 (de) | 1998-08-06 |
US6140725A (en) | 2000-10-31 |
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