EP0341368A1 - Motopompe submersible - Google Patents

Motopompe submersible Download PDF

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Publication number
EP0341368A1
EP0341368A1 EP88710046A EP88710046A EP0341368A1 EP 0341368 A1 EP0341368 A1 EP 0341368A1 EP 88710046 A EP88710046 A EP 88710046A EP 88710046 A EP88710046 A EP 88710046A EP 0341368 A1 EP0341368 A1 EP 0341368A1
Authority
EP
European Patent Office
Prior art keywords
annular chamber
partition
pump according
submersible pump
chamber
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
Application number
EP88710046A
Other languages
German (de)
English (en)
Other versions
EP0341368B1 (fr
Inventor
Werner Dipl.-Ing. Arnswald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABS Pumpen AG
Original Assignee
ABS Pumpen AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ABS Pumpen AG filed Critical ABS Pumpen AG
Priority to AT88710046T priority Critical patent/ATE77447T1/de
Publication of EP0341368A1 publication Critical patent/EP0341368A1/fr
Application granted granted Critical
Publication of EP0341368B1 publication Critical patent/EP0341368B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/10—Units comprising pumps and their driving means the pump being electrically driven for submerged use adapted for use in mining bore holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/0245—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the pump
    • F04D15/0263—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the pump the condition being temperature, ingress of humidity or leakage
    • 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
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid

Definitions

  • the invention relates to a submersible pump, consisting of an electric motor, the shaft of which is arranged vertically or horizontally during operation, a hydraulic part located on the motor shaft, arranged below the motor, and an intermediate chamber provided between the motor housing and the hydraulic part and surrounding the motor shaft, both is sealed against the hydraulic part and against the motor housing via sliding or shaft seals, a medium for lubricating and cooling the seals being provided in the intermediate chamber.
  • the relatively large-volume intermediate chamber is provided with an oil filling which lubricates and cools the seals.
  • oil filling which lubricates and cools the seals.
  • water from the hydraulic part gradually penetrates through the lower seal into the intermediate chamber and dilutes the oil in it.
  • a monitoring electrode responds and gives a signal that requires the pump to be serviced.
  • the intermediate chamber then contains a new, fresh oil filling.
  • the invention is therefore based on the object of eliminating the oil problem in submersible pumps.
  • this object is achieved in that a partition is arranged in the intermediate chamber at a short distance around the motor shaft, which extends at least over part of the chamber height and which divides the intermediate chamber into an inner and an outer annular chamber, and that of the inner an overflow to the outer annular chamber is provided.
  • the oil filling can be reduced to an extremely small amount, which is only filled into the inner annular chamber. If water gradually penetrates through the lower seal, the excess amount of liquid can overflow into the outer annular chamber, where the oil-water mixture is collected.
  • the inner annular chamber is made as small as possible in relation to the outer annular chamber, so that an extremely small amount of oil is required to start up the submersible motor pump.
  • the running time of the pump between two maintenance can be considerably extended, because the outer annular chamber can absorb the excess liquid quantities over a relatively long period of time before maintenance is required.
  • an oil filling can also be dispensed with entirely. Instead, a water or glycol filling or a mixture of water or glycol can be placed in the inner ring chamber from the start can be entered. In some circumstances, it may even be sufficient to work with the water that passes through the lower seal from the hydraulic part without initial filling. With appropriate dimensioning of the individual parts relative to each other, the cooling and lubricating effect of the water is sufficient for both seals.
  • the inner annular chamber is preferably connected directly to the mechanical seal. This means that the lubricant and coolant can adequately supply the lower mechanical seal.
  • the partition can be formed on the upper bearing cover, through which the motor bearing is fixed in the area of the output end of the motor shaft.
  • the partition is expediently designed as a sleeve-shaped apron, the lower end face of which lies closely against the lower floor of the intermediate chamber.
  • the partition can also be designed as a separate tube section, the end faces of which bear closely against the upper bearing cover and the lower bottom of the intermediate chamber.
  • the overflow can be designed as an overflow pipe, the inlet opening of the overflow pipe being sealed lies below the upper end of the inner annular chamber, the edge of the inlet opening is at least partially arranged below the sliding surface of the seal between the inner annular chamber and the motor, the overflow pipe extends through the partition and the outlet opening of the overflow pipe into the outer annular chamber is at the same height or opens below the entrance opening.
  • a closed inner annular chamber is formed, into which the coolant and lubricant can be filled at the factory. There is then no danger that the filled lubricant and cooling liquid will leak out of the inner annular chamber into the outer annular chamber.
  • the overflow pipe preferably extends from its upper inlet opening to close to or into the lower floor of the intermediate chamber, the overflow pipe then being guided around the motor shaft over an arc of almost 360 ° and then extending back up to the outlet opening.
  • This convoluted shape of the overflow pipe ensures that the initial liquid filling present in the inner annular chamber does not leak through the overflow pipe into the outer annular chamber even if the submersible pump is tilted and turned several times. Leakage is avoided in particular during transport.
  • the edge of the inlet opening of the overflow pipe is arranged horizontally in the inner annular chamber, the overflow pipe runs inside the inner annular chamber and extends horizontally through the partition wall in the edge region of the outlet opening.
  • the intermediate chamber wall between the motor housing and the Hydraulic part can be formed in one piece so that the overflow pipe is inserted into the inner annular chamber before the intermediate chamber wall is attached.
  • the lower part of the intermediate chamber wall can also be designed as a separate insert cover, at least in the region of the bottom of the inner annular chamber, which is detachably connected to the remaining intermediate chamber wall. The insert cover allows the overflow pipe to be inserted and removed independently of the remaining intermediate chamber wall.
  • a sheet metal sleeve can protrude radially inside the overflow pipe from above into the inner ring chamber to below the inlet opening of the overflow pipe, the upper edge of the sheet metal sleeve being thermally conductive to the upper slide ring of the mechanical seal .
  • the liquid level standing in the inner annular chamber may only stand up to the sliding ring of a single and up to the upper sliding ring of a double mechanical seal, so that it is ensured that no liquid penetrates to the engine mount. In the case of a mechanical seal, the upper mechanical ring is therefore least cooled.
  • the z. B. is made of silicon carbide to keep functional.
  • the sheet metal sleeve also prevents a too strong liquid parabola from occurring when the motor shaft rotates, which would lower the liquid level in the storage area where the liquid is most urgently needed and thus reduce the lubricating and cooling effect.
  • the sheet metal sleeve can be thermally connected to the bearing cap of the motor, so that also a cooling effect takes place in this way.
  • deflectors can be provided on the inner surface of the sheet metal sleeve, which cause a further reduction of the liquid parabola and a spray mist formation when the motor shaft rotates, as a result of which additional cooling and lubrication of the upper mechanical seal is generated.
  • the overflow can also be designed as a channel in the partition, the inlet opening of the channel being located just below the upper end of the inner annular chamber and the outlet opening of the channel opening into the outer annular chamber at the same height or below the inlet opening. Due to this measure, a closed inner annular chamber is also formed, which enables maximum cooling and lubricating liquid filling and ensures that the lubricating and cooling liquid does not run out of the inner annular chamber into the outer annular chamber in any transport position.
  • the channel preferably runs as follows: the inlet and outlet openings are designed as radial bores that are open to the inner and outer annular chamber, the channel extends from its inlet opening in the form of an axial bore to Bottom of the partition, then over an arcuate groove of almost 360 ° in the lower end of the partition around the motor shaft and then in the form of an axial hole up to the exit opening.
  • This shape of the channel which essentially corresponds to the course of the overflow pipe described above, can easily be produced in the dividing wall designed as a sleeve-shaped apron.
  • the partition with the molded channel can be made as a molded or cast part.
  • the inlet and outlet opening instead of as bores, can be designed as radial grooves which are open to the inner or outer annular chamber in the upper end face of the dividing wall.
  • the channel then runs between the openings as described above.
  • the security against the leakage of the lubricant and cooling liquid from the inner annular chamber can be increased in such an embodiment in that the inlet and outlet opening of the channel on the upper end face of the partition are not, as above, close together, but z. B. the entrance opening is offset via an arcuate groove of, for example, 180 ° in the upper end face of the partition.
  • the arcuate groove in the lower end face of the partition or the grooves in the upper end face of the partition are preferably sealed against the inner and outer annular chamber by flat seals which abut the lower bottom of the intermediate chamber or the upper bearing cover.
  • One or more deflectors can be provided on the inside of the partition wall, which counteract the formation of a liquid parabola when the motor shaft rotates and cause spray formation, which generates additional cooling and lubrication of the upper seal.
  • the deflectors are preferably in the form of rectangular plates which are connected to the partition on one side and on the opposite Protrude from the bulkhead and extend downward from the top of the bulkhead and are arranged so that the sides of the deflectors projecting from the bulkhead point in the direction of motor shaft rotation.
  • a deflector is provided which covers the inlet opening of the overflow.
  • a seal monitoring electrode which responds to contact with water, can be arranged in the upper region of the outer annular chamber. This makes it possible to determine at what point in time the outer annular chamber is filled with water and the usual maintenance work is to be carried out. Furthermore, a fill level monitoring electrode can be arranged in the inner annular chamber, which responds when the liquid level of the lubricating and cooling liquid falls below a certain level, so that the lubricating and cooling effect is impaired.
  • the area of the submersible pump between the motor housing 1 and the hydraulic part 2 essentially consists of an intermediate chamber 4 surrounding the motor shaft 3, which is sealed both against the hydraulic part 2 and against the motor housing 1 via mechanical seals 5 and 6 .
  • the intermediate chamber 4 is a short distance around Motor shaft 3 arranged around a partition 7, which extends over part of the height of the intermediate chamber 4 and divides the intermediate chamber 4 into an inner annular chamber 8 and an outer annular chamber 9.
  • the inner annular chamber 8 and the outer annular chamber 9 are connected to one another by an overflow 10.
  • the partition 7 is designed as a sleeve-shaped apron which is formed on the upper bearing cover 11, by means of which the motor bearing 12 is held in the region of the output end of the motor shaft 3.
  • the upper bearing cover 11 is fastened to the motor housing 1 by means of screws 13 and sealed against it by an O-ring 14.
  • the lower end of the sleeve-shaped partition 7 is sealed off from the lower bottom of the intermediate chamber 4 by means of O-rings 15.
  • the wall of the intermediate chamber 4 is designed as a separate insert cover 16 which is fastened to the remaining wall of the intermediate chamber 4 by means of screws 17 and is sealed by the lower one of the O-rings 15.
  • the lower end face of the partition 7 is arranged at a short distance from the insert cover 16.
  • the partition 7 lies laterally on the remaining wall of the intermediate chamber 4 and is sealed against this by the upper one of the O-rings 15.
  • the inner ring chamber 8 thus formed is in direct connection with the lower mechanical seal 5 and the upper mechanical seal 6.
  • the two sliding rings 18 and 19 of each mechanical seal are held by the outer ends of two coil springs 20, the inner ends of which are supported on a clamping ring 21 inserted into an annular groove of the motor shaft 3 in the central region of the inner annular chamber 8.
  • the material of the slide rings 18 and 19 is chosen so that sufficient heat dissipation is made possible. Good Silicon carbide has proven itself for both slide rings 18 and 19 or carbon for the upper slide ring 18 and cast chrome for the lower slide ring 19. Because of the different heat dissipation, it can also be expedient to add different materials for the lower and upper mechanical seal 5 and 6, respectively choose.
  • the overflow 10 installed between the inner annular chamber 8 and the outer annular chamber 9 is designed as an overflow pipe 22.
  • the overflow pipe 22 extends in the inner annular chamber 8 and opens at one end through the partition 7 into the outer annular chamber 9. It consists of a first pipe section 23, which is arranged axially to the motor shaft 3 and which extends from the horizontal inlet opening 24 down to an annular groove 25 formed in the insert cover 16 extends. In the annular groove 25, the overflow pipe 22 is guided around the motor shaft 3 via an arc 26 of almost 360 °.
  • the overflow pipe then extends upward in a third pipe section 27 axially to the motor shaft 3 and extends in a radially directed end section 28 through an opening 29 in the partition 7.
  • the end section 28 is sealed in the opening 29 by a rubber seal 30.
  • the outlet opening 31 of the overflow pipe 22 on the side of the opening 29 in the partition 7 facing the outer annular chamber 9 is arranged below the inlet opening 24.
  • the course of the overflow pipe 22 is shown in perspective in FIG. 3, from which the individual pipe sections can be seen.
  • the volume of the inner annular chamber 8 is smaller than that of the outer annular chamber 9.
  • the inner annular chamber 8 is provided for receiving a cooling and lubricating liquid. These can be filled in at the factory.
  • the maximum height of the liquid level of the cooling and lubricating liquid is determined by the height of the inlet opening 24 of the overflow pipe 22. This height is such that the cooling and lubricating liquid does not touch the upper slide ring 18 of the upper mechanical seal 6 when the submersible pump is in a vertical operating arrangement. In this way, the coolant and lubricant cannot enter the motor housing 1 through the upper seal when the submersible pump is operating.
  • the lubricating and cooling liquid is directly connected to the lower slide ring 19 of the upper mechanical seal 6 and the upper and lower slide rings 19 and 18 of the lower mechanical seal 5. This ensures optimum heat dissipation from these sliding rings. Since the slide ring 18 bears against the slide ring 19, sufficient heat dissipation from the upper slide ring 18 of the upper mechanical seal 6 is also achieved.
  • a sheet metal sleeve 33 is arranged radially inside the overflow pipe 22 in the inner annular chamber 8.
  • the sheet metal sleeve 33 extends from the upper end of the inner annular chamber 8 to below the inlet opening 24 of the overflow pipe 22.
  • the sheet metal sleeve 33 is fastened to the upper bearing cover 11 with the aid of notched nails 34. Its upper end lies on the outside of the upper mechanical ring 18 of the upper mechanical seal 6. Thus, heat is dissipated from the upper slide ring 18 to the wall parts of the intermediate chamber 4 and into the liquid via the sheet metal sleeve 33.
  • the sheet metal sleeve 33 prevents a too strong liquid parabola from occurring when the motor shaft 3 rotates, as a result of which the lubricating and cooling effect would be reduced.
  • Deflectors are provided on the inner surface of the sheet metal sleeve 33, which deflect when the motor shaft 3 rotates cause spray to form. The formation of spray mist generates additional cooling and lubrication of the upper slide ring 18 arranged above the liquid level, without liquid being able to get into the motor housing 1 via this.
  • glycol or oil is used as the lubricating and cooling liquid. This is filled in the inner annular chamber 8 in the factory up to the maximum liquid level.
  • the special shape of the overflow pipe 22 prevents the liquid from running out of the inner annular chamber 8 into the outer annular chamber 9 in different transport positions of the submersible pump.
  • the submersible pump can also be started with a mixture of water and glycol or only with water. It has been found that with the construction of the submersible pump described above, the lubricating and cooling effect of water is sufficient. It is even possible that To start the submersible pump empty and only to use the water penetrating from the hydraulic part 2 into the inner annular chamber 8 for lubrication and cooling.
  • a seal monitoring electrode 32 is arranged, which responds to contact with water. With the help of this electrode it can be determined when the outer annular chamber 8 is filled with water and the usual maintenance work is to be carried out.
  • the partition 7 is designed as a separate pipe section 35.
  • the pipe section 35 extends between the upper bearing cover 11 and the lower insert cover 16. It lies with its outside in its upper end region against a part of the upper bearing cover 11 projecting downward and in its lower end region against a wall part of the intermediate chamber 4 projecting upwards at. Sealing takes place via an O-ring 36 in each case.
  • this exemplary embodiment essentially corresponds to the exemplary embodiment shown in FIG. 1 and described above.
  • the lower insert cover 16 allows the overflow pipe 22 and the lower and upper mechanical seals 5 and 6 to be easily installed independently of the remaining wall of the intermediate chamber 4.
  • the partition wall 7 designed as a pipe section 35 can also be used Attachment of the insert cover 16 can be installed in the inner annular chamber 8.
  • the exemplary embodiment shown in FIG. 4 is distinguished by its particularly compact shape. Through the Arrangement of the lower and upper mechanical seals 5 and 6, the height of the inner annular chamber 8 can be made relatively low.
  • the wall 37 of the intermediate chamber 4 is formed in one piece and, like in the first two exemplary embodiments, is fastened to the motor housing 1 by means of screws 38 at its upper end.
  • the lower mechanical seal 5 is arranged between the wall 37 of the intermediate chamber 4 and the hydraulic part 2. It is pressed against the motor shaft opening in the wall 37 by means of a helical spring 39.
  • the two sliding rings of the lower mechanical seal 5 are made of silicon carbide.
  • the mechanical seal 5 is in direct connection with the pumped medium in the hydraulic part 2. Therefore, the heat from the lower mechanical seal 5 is mainly dissipated into the fluid.
  • the cooling and lubricating liquid present in the inner annular chamber 8 predominantly supplies the upper mechanical seal 6.
  • the upper sliding ring 40 is made of carbon
  • the lower sliding ring 41 is made of cast chrome.
  • the two sliding rings 40 and 41 are held by a clamping ring 42 inserted in an annular groove of the motor shaft 3. Due to this construction shown in FIG. 4, a larger surface of the sliding rings 40 and 41 of the upper mechanical seal 6 is in direct connection with the inner annular chamber 8. This promotes heat dissipation from these sliding rings.
  • the partition 7 is formed in the simple embodiment according to FIG. 4 as a sleeve-shaped apron, the lower end of which is close to the lower bottom of the Intermediate chamber 4 is present. Sealing takes place by means of an annular flat seal 43.
  • the dividing wall 7 is integrally formed on the upper bearing cover 11.
  • the overflow 10, as in the exemplary embodiments described above, is designed as an overflow pipe 22. Due to the more compact inner annular chamber 8, however, the overflow pipe 22 has a lower height.
  • a fill level monitoring electrode 44 is additionally arranged in the inner annular chamber 8. This extends through a radial opening 45 in the partition 7 at a height which is arranged above the lower end and below the upper end of the slide ring 41 of the upper mechanical seal 6.
  • the fill level monitoring electrode 44 responds when the liquid level of the lubricating and cooling liquid falls below the level of the electrode and the lubricating and cooling effect is impaired.
  • FIG. 4 is similar to the exemplary embodiments described above.
  • Carbon is used as the material for the upper slide ring 40, and cast chrome is used for the lower slide ring 41 of the upper slide ring seal 6.
  • FIG. 5 differs from the last described only by a lower insert cover 46 in the bottom region of the inner annular chamber 8.
  • the insert cover 46 is, as in the embodiments according to FIGS. 1 and 2, by means of screws 47 on the remaining wall 48 of the intermediate chamber 4 attached and sealed against this by an O-ring 49.
  • the sleeve is Partition 7 in the lower area on the outside towards the inward end of the wall 48 and is also sealed against this by an O-ring 50.
  • FIG. 6 shows two exemplary embodiments in one figure, the exemplary embodiment shown in the left half of the figure using an upper mechanical seal 6 and the exemplary embodiment shown in the right half using a shaft seal 51. Otherwise, the two exemplary embodiments are completely identical.
  • the overflow 10 is designed as a channel 52 in the interior of the partition 7.
  • the inlet opening 53 of the channel 52 is arranged just below the upper end of the inner annular chamber 8 in the form of a radial bore. Since the bore is difficult to incorporate from the inside of the sleeve-shaped partition 7, a hole 54 of larger diameter is drilled at the same point from the outside up to approximately the middle of the partition 7. The hole of smaller diameter forming the inlet opening 53 is then created through the hole 54. The hole 54 is then closed from the outside with a plug, not shown in the drawing.
  • the inlet opening 53 of the channel 52 is connected to an axial bore 55 which is open towards the underside of the sleeve-shaped partition 7.
  • an arcuate groove 56 then extends in the lower end face of the partition 7 at almost 360 ° around the motor shaft 3.
  • a second axial bore 57 At the end of the groove 56 there is a second axial bore 57, the length of which corresponds approximately to the length of the first axial bore 55.
  • the upper end of the axial bore 57 is connected to a radial bore open to the outer annular chamber 9, forms the outlet opening 58 of the channel 52 and is arranged at a height below the inlet opening 53.
  • the two closely spaced axial bores 55 and 57 are shown pulled apart at an angle of 180 ° in FIG. 6.
  • FIG. 7 shows a plan view of the lower end face of the partition 7.
  • FIG. 8 shows a plan view of the partition wall 7 formed on the upper bearing cap 11 represents.
  • the part shown in FIGS. 7 and 8 with the molded-in arcuate groove 56 and the axial bores 55 and 57 can be produced in a simple manner as a cast or injection-molded part.
  • FIGS. 6, 7 and 8 corresponds to the exemplary embodiment according to FIG. 4.
  • FIG. 9 shows an exemplary embodiment in which the partition 7 is designed as a separate pipe section 59 and the overflow 10, similar to the previously described exemplary embodiment, is formed as a channel 60 in the pipe section 59.
  • the inlet and outlet openings 61 and 62 of the channel 60 are embedded in the upper end face of the tube section 59 as radial grooves 8 and 9, respectively, which are open to the inner and outer ring chambers. Both openings are close together.
  • the inlet and outlet openings 61 and 62 are in laid the same cutting plane.
  • the groove forming the outlet opening 62 is formed deeper than the groove forming the inlet opening 61 in the upper end face of the pipe section 59.
  • the input and output openings 61 and 62 are each connected to an axial bore 63 or 64, which extends through the pipe section 59.
  • the openings of the axial bores 63 and 64 lying on the lower end face of the pipe section 59 are connected to one another via an arcuate groove 65 which extends in the lower end face of the pipe section 59 around the motor shaft 3.
  • FIGS. 10 to 12 The course of the channel 60, in particular the arrangement of the inlet and outlet openings 61 and 62 in the upper end face of the pipe section 59, the axial bores 63 and 64 and the arcuate groove 65 formed in the lower end face of the pipe section 59 are shown in FIGS. 10 to 12 shown in more detail.
  • the axial bores 63 and 64 lying next to one another at a short distance and the associated inlet and outlet openings 61 and 62 are shown in FIG. 12 pulled apart at an angle of 180 °.
  • the grooves 61 and 62 forming the inlet and outlet opening in the upper end face of the pipe section 59 and the arcuate groove 65 in the lower end face of the pipe section 59 are by flat seals 66 and 67, respectively, on the upper bearing cover 11 and on the lower bottom of the intermediate chamber 4 rest, sealed against the inner and outer annular chamber 8 and 9 respectively.
  • a deflector 68 is arranged on the inside of the tube section 59. It is designed in the form of a rectangular plate that is on one side with the Pipe section 59 is connected and protrudes from the pipe section 59 on the opposite side.
  • the deflector 68 is arranged so that it extends from the upper end of the pipe section 59 over the inlet opening 61 of the overflow 10 and that the side of the deflector 68 protruding from the pipe section 59 points in the opposite direction to the motor shaft rotation.
  • the deflector 68 counteracts the formation of a liquid parabola when the motor shaft 3 rotates and causes spray formation in the upper region of the inner annular chamber 8, as a result of which additional cooling and lubrication of the upper seal is generated.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Motor Or Generator Frames (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)
EP88710046A 1988-05-10 1988-11-18 Motopompe submersible Expired - Lifetime EP0341368B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88710046T ATE77447T1 (de) 1988-05-10 1988-11-18 Tauchmotorpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3815895 1988-05-10
DE3815895 1988-05-10

Publications (2)

Publication Number Publication Date
EP0341368A1 true EP0341368A1 (fr) 1989-11-15
EP0341368B1 EP0341368B1 (fr) 1992-06-17

Family

ID=6354040

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88710046A Expired - Lifetime EP0341368B1 (fr) 1988-05-10 1988-11-18 Motopompe submersible

Country Status (7)

Country Link
EP (1) EP0341368B1 (fr)
JP (1) JPH03504150A (fr)
AT (1) ATE77447T1 (fr)
AU (1) AU2787089A (fr)
DE (1) DE3872225D1 (fr)
WO (1) WO1989011039A1 (fr)
ZA (1) ZA891315B (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2277561A (en) * 1993-04-28 1994-11-02 Abs Pump Prod Ab Shaft sealing arrangement
DE19711185A1 (de) * 1997-03-18 1998-09-24 Werner Dipl Ing Arnswald Tauchmotorpumpe
DE10239998A1 (de) * 2002-08-27 2004-03-04 Gardena Manufacturing Gmbh Pumpenanordnung
EP2669525A1 (fr) * 2012-05-31 2013-12-04 Grundfos Holding A/S Agrégat de pompe centrifuge
RU175587U1 (ru) * 2017-05-29 2017-12-11 Акционерное общество (АО) "Научно-исследовательский институт "Лопастных машин" ("НИИ ЛМ") Центробежный вертикальный погружной насос
RU175622U1 (ru) * 2017-05-29 2017-12-12 Акционерное общество (АО) "Научно-исследовательский институт "Лопастных машин" ("НИИ ЛМ") Вертикальный центробежный погружной насос
RU176502U1 (ru) * 2017-05-12 2018-01-22 Открытое акционерное общество (ОАО) "Турбонасос" Центробежный вертикальный насос
RU2681727C1 (ru) * 2018-01-29 2019-03-12 Александр Семенович Дубовик Уплотнительный герметичный модуль центробежного насоса

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FR1507108A (fr) * 1966-01-03 1967-12-22 Moto-pompe électrique immergée
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FR2389015A1 (fr) * 1977-04-29 1978-11-24 Itt Boite a huile pour pompe
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GB854526A (en) * 1957-03-04 1960-11-23 Harry E La Bour Improvements in or relating to rotary shaft seals and pumps provided with such seals
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Title
ENGINEERING, Band 192, Nr. 4978, 15. September 1961, Seiten 358-360; "The flygt "Bibo 3" submersible contractors' pump" *
WORLD PUMPS, Nr. 5, Mai 1987, Seiten 149-152, Morden, Surrey, GB; F.F. BERG: "Large submersible pumps for water transfer applications" *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2277561A (en) * 1993-04-28 1994-11-02 Abs Pump Prod Ab Shaft sealing arrangement
GB2277561B (en) * 1993-04-28 1996-07-31 Abs Pump Prod Ab Shaft sealing arrangement
DE19711185A1 (de) * 1997-03-18 1998-09-24 Werner Dipl Ing Arnswald Tauchmotorpumpe
DE19711185C2 (de) * 1997-03-18 1999-11-18 Werner Arnswald Tauchmotorpumpe
DE10239998A1 (de) * 2002-08-27 2004-03-04 Gardena Manufacturing Gmbh Pumpenanordnung
EP2669525A1 (fr) * 2012-05-31 2013-12-04 Grundfos Holding A/S Agrégat de pompe centrifuge
WO2013178444A1 (fr) * 2012-05-31 2013-12-05 Grundfos Holding A/S Pompe centrifuge
RU176502U1 (ru) * 2017-05-12 2018-01-22 Открытое акционерное общество (ОАО) "Турбонасос" Центробежный вертикальный насос
RU175587U1 (ru) * 2017-05-29 2017-12-11 Акционерное общество (АО) "Научно-исследовательский институт "Лопастных машин" ("НИИ ЛМ") Центробежный вертикальный погружной насос
RU175622U1 (ru) * 2017-05-29 2017-12-12 Акционерное общество (АО) "Научно-исследовательский институт "Лопастных машин" ("НИИ ЛМ") Вертикальный центробежный погружной насос
RU2681727C1 (ru) * 2018-01-29 2019-03-12 Александр Семенович Дубовик Уплотнительный герметичный модуль центробежного насоса

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JPH03504150A (ja) 1991-09-12
DE3872225D1 (de) 1992-07-23
EP0341368B1 (fr) 1992-06-17
ATE77447T1 (de) 1992-07-15
WO1989011039A1 (fr) 1989-11-16
AU2787089A (en) 1989-11-29
ZA891315B (en) 1989-11-29

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