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
  • F04D29/04—Shafts or bearings, or assemblies thereof
  • F04D29/046—Bearings
  • F04D29/048—Bearings magnetic; electromagnetic
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D13/00—Pumping installations or systems
  • F04D13/02—Units comprising pumps and their driving means
• • 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
  • F04D13/021—Units comprising pumps and their driving means containing a coupling
  • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
  • F04D13/025—Details of the can separating the pump and drive area
• • 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
  • F04D13/021—Units comprising pumps and their driving means containing a coupling
  • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
  • F04D13/026—Details of the bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D13/00—Pumping installations or systems
  • F04D13/02—Units comprising pumps and their driving means
  • F04D13/021—Units comprising pumps and their driving means containing a coupling
  • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
  • F04D13/027—Details of the magnetic circuit
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/04—Shafts or bearings, or assemblies thereof
  • F04D29/046—Bearings
  • F04D29/049—Roller bearings

Definitions

• the invention relates to a centrifugal pump having the features of the preamble of claim 1, as known from EP-B1-0171515.
• centrifugal pumps with magnetic coupling represent an important type of industrially used machines for the conveyance of liquids. Compared to the simpler centrifugal pumps with mechanical seal they have the advantage of a hermetic seal of the pump chamber. This makes them especially favorable for the promotion of aggressive or toxic liquids.
• the component referred to below as the pump housing (1) must in practice be made up of several parts. Some of them are wetted by the liquid to be pumped and must be sealed accordingly, others not.
• the pump housing (1) is here shown in one piece.
• FIG. 1 A first known pump of conventional design is shown in Figure 1 and is e.g. advertised in the brochure [1].
• a rotating pump impeller (4') is arranged, which receives the liquid to be conveyed via the suction nozzle (2 1 ) and via the discharge nozzle (3 ') ejects again under pressure.
• the radial bearing of the pump impeller (4 ') takes place by means of an impeller shaft (5') usually in plain bearings (9 ', 10'), the fixed parts in a bearing insert (11 ') are added.
• the lubrication and cooling of the sliding bearing (9 ', 10') takes place by the liquid to be pumped itself.
• This is equipped with permanent magnets (7 '), which in turn must be surrounded before the corrosive and possibly also abrasive attack of the pumped liquid with a cylindrical protective jacket (8') liquid-tight. It should be mentioned only in passing that it may be necessary to protect an approximately metallic, that is to say ferromagnetically, magnet rotor (6 ') from corrosion as well as the shaft (5').
• the part of the rotary coupling which receives and transmits the driving torque of the motor via the drive shaft (15 ') is commonly referred to as a magnet driver (13'). He is also equipped accordingly with permanent magnets (14 '), but rotate in air and therefore are not subject to any special attack.
• the radial and axial bearing of the magnetic drive takes place in commercial rolling bearings (16 ').
• FIG. 2 Another common embodiment, especially for smaller pumps, is shown in Figure 2. Such a pump is e.g. advertised in [2].
• a bearing insert (11 ') can be inexpensively eliminated.
• the pump impeller (4 ') is combined with the magnet rotor (6'), the permanent magnet (7 1 ) and the protective jacket (8 ') to a part.
• This rotating impeller magnetic rotor unit (19 ') is slidably mounted here on a fixed axle (17').
• the axis (17 ') itself is fastened on one side via flow ribs (18') in the suction nozzle (2 '), supported on the other side in the specially shaped containment shell (12').
• design A The design described in FIGS. 1 and 2 and largely conventional today (referred to here as design A) is characterized in that the magnet driver (13 ') is arranged radially outwardly beyond the magnet rotor (6') lying further inward.
• This construction has the advantage that the high mass moment of inertia of the outside magneto drive (13 ') counteracts the overly rapid start-up of the driving motor and thus the tearing off of the magnetic coupling can be prevented more favorably.
• this design facilitates, in particular, a generously axially spaced radial bearing of the pump impeller (4 1 ), which is always desirable due to the high hydraulic forces within the pump.
• magnetic coupling pumps with a magnet rotor (6 ') located radially on the outside, which is in contact with the liquid, and an internal magnet driver (13') are less frequently used.
• This embodiment is referred to as type B.
• Such type B pumps e.g. in DE 01453760 or EP 0171514 or EP 0171515, and are shown in Figure 3, must be carefully designed so that during rapid startup, the magnetic coupling does not break off, which threatens here due to the outside magnetic rotor (6 '). Furthermore, the radially inner magnet driver (13 ') obstructs an axially pulled-out inner slide bearing of the impeller magnetic rotor unit (19'), if not the containment shell (12 '), with its actual opening in the type B drive side must be facing the pump, adversely wound right is executed. An executed pump of type B is advertised in [3] and served as a model for the figure 3.
• the present invention seeks to improve the radial bearing in the magnetic coupling of a generic centrifugal pump.
• a centrifugal pump with the features of claims 1 or 3 is proposed.
• the invention which overcomes the prior art imperfections described above, and in which the radial bearing of the impeller magnetic rotor assembly is displaced outwardly as much as possible, et al. achieved the following advantages:
• the storage is close to the outer housing wall, where by cooling ribs, the approximately heated, thrown off to the outside residual liquid can be effectively cooled;
• the containment shell is no longer used as a supporting component, so that - subordinated to the transmission of magnetic moments - it can always be made thin-walled and nevertheless the risk of overloading and deformation does not exist;
• start-up and emergency camps are dispensable.
• the fixed part of the sliding bearing is arranged on the inside wall surface of the pump housing as a whole or is formed independently by the housing wall or sections of the housing wall of the pump housing, high radial bearing forces can be transmitted over a large axial length and a smooth synchronization of the impeller Magnetic rotor unit can be achieved.
• these are preferably located approximately at the same radial level in order to further improve the running characteristics and the dry running capability of the bearing.
• radial bearing forces can also be absorbed on the pump impeller, e.g. to improve the emergency running and / or starting characteristics.
• best synchronization conditions are achieved if the pump impeller can be rotated radially without contact or force.
• the rotating part of the sliding bearing of the impeller magnetic rotor unit has recesses or elevations on its outer circumference, thereby the sliding properties improving liquid movements can be generated.
• outside wall of the pump housing is provided in the region of the fixed part of the sliding bearing of the impeller magnetic rotor unit with cooling fins or a cooling jacket, overheating-related bearing damage can be avoided.
• the pump housing wall has a multilayer structure and the innermost material layer consists of a corrosion- or abrasion-resistant material, the longevity is improved even with difficult pumped media.
• the pump length can be shortened considerably despite the fact that the magnet driver inside the pump is stored alone.
• the magnetic drive bearing bearings are preferably used.
• the rolling bearing of the magnetic driver remains unaffected by the pumped liquid.
• the magnet driver preferably has an open towards the drive side cup shape to receive the at least one bearing of the magnet rotor within the pump housing.
• a particularly advantageous mounting of the magnetic driver is achieved by a hollow hollow cantilever, through which the drive shaft of the magnet driver is guided, and which preferably carries on at least one inner or outer surface at least one of its end portions a bearing for the magnetic driver. Tapering in these end areas facilitate the placement of such bearings in a small space. If the tapering starts from the root of the cantilever, high bearing forces can be absorbed in a light construction.
• the at least partial support of the magnetic driver within the space defined by the impeller magnetic rotor unit and the embodiments of such a bearing are of independent inventive significance.
• FIG. 5 shows a first embodiment of a centrifugal pump according to the invention in axial section - schematized;
• FIG. 6 shows a second embodiment;
• Fig. 7 shows a third embodiment
• Fig. 8 shows a fourth embodiment
• Fig. 12 shows an eighth embodiment
• Fig. 13 shows a ninth embodiment
• Fig. 15 shows an eleventh embodiment.
• the embodiments have in common that they have a suction nozzle 2 and a discharge nozzle 3 exhibiting pump housing 1, wherein a pump impeller 4 is mounted coaxially to the suction nozzle and fluidly connected in the radial direction with the discharge nozzle 3.
• the pump impeller 4 has on the drive side a magnetic rotor 6, with which it forms an open to the drive side impeller magnetic rotor unit. This has on its outer circumference the rotating part 9 of a slide bearing, while the fixed part 10 of this sliding bearing is arranged on the inner wall 20 of the pump housing 1.
• the magnet rotor 6 carries permanent magnets 7 on the radially inner side. These stand opposite permanent magnets 14 at radial spacing, which are arranged on the outer surface of an approximately cup-shaped magnet driver 13.
• a partition wall possibly in the form of a so-called split pot 12, interposed, which keeps dry the magnetic driver against the liquid wetted inside the pump.
• the magnet driver 13 is supported at two axially spaced locations via rolling bearings 16a and 16b. This storage takes place in all embodiments - although not mandatory - in each case with respect to the pump housing 1, wherein this storage takes place in the embodiments of Figures 7 to 15 at least pump side within the space formed by the impeller magnetic rotor unit 19.
• a continuous hollow cantilever 39 protrudes from the drive-side housing end wall toward the pump side and has a crawling design 39a, 39b, the drive shaft 15 of the pump passing through it being roller-mounted on its drive-side end region, while a second rolling bearing is mounted in the opposite end region on its outside, the drive shaft 15 indirectly, namely superimposed on the magnet driver 13.
• the latter has a pot shape which is open on the drive side.
• An arrangement according to claim 1 not only offers significant technological advantages, but also leads to an extremely simple construction of the entire pump.
• the slide bearing 9, 10 is arranged exactly here, which can be operated as long as desired with the residual liquid with sufficient cooling.
• very small residual amounts which tend to occur at high delivery heights of the pump and low static counter-pressure, it can not be ruled out that these can escape axially in order to move to even higher radial levels in the impeller. This can be prevented via a lock in the form of a circulating ring 21, as the claim 2 introduces them and is shown in Figure 6.
• the invention of claim 1 can also be exploited to shorten the axial extent of the pump considerably. This is possible because the magnetic driver 13 is not stored in the pump housing 1, but is placed directly on the shaft journal of the drive machine, that is to say ultimately stored by the drive machine. This is usually an electric motor. The electric motor is flanged directly to the pump, which is known as "block construction".
• a preferably detachable, split pot 12 is introduced, as it always finds use in industrial pumps.
• these containment walls are designed with very thin walls on the circumference in order to be able to realize the smallest possible radial gap between magnet rotor 6 and magnet driver 13. Due to the design according to claim 1
• the containment shell 12 can be designed with a smooth end wall and must point with its larger opening in the direction of the drive side.
• the containment shell 12 should not itself be used to support a rolling bearing because of its thinness, it now offers sufficient space for an axially generously dimensioned rolling bearing 16 of the magnet driver 13 in its inner region 24 Baumass the pump are shortened to the conventional block design, but here the magnetic driver 13 is part of the pump, which allows a complete series assembly and stockpiling of the pump.
• the shaft end 25 in such an axially shortened design can advantageously be carried out according to claim 15 or 16 ( Figure 8) so that either via a conventional pump clutch (shown only the pin portion 27 of the pump clutch) the direct connection of a motor is possible (over an intermediate ring could also be flanged directly to the pump) or a shaft journal 28 again leads to the conventional pump with free shaft end (eg to comply with predetermined standard dimensions). Also, such a shaft end 25 should provide the opportunity to attach an additional flywheel 26 to compensate for the mentioned disadvantage of the type B chosen here when starting the pump can. All this would be part of the final assembly of the pump unit (which would also be carried out by the user of the pump itself) and would still allow a large-scale series assembly and cheap stockpiling of the pump at the manufacturer as described above.
• the rotating part 9 of the plain bearing need not necessarily consist of two defined bearing sleeves a and b or from the magnet rotor 6 itself, but according to claim 3 ( Figure 9) as an axially continuous sleeve 29 ( Figure 9, upper half) or molding compound 30 (FIG. FIG. 9, lower half).
• NEN magnetic rotor 6 and the permanent magnets 7 serve. Namely, it is quite common, depending on the field of application of the pump, that the magnetic rotor 6 as ferromagnetic carrier of the permanent magnets 7 must be protected from the attack of the liquid to be conveyed and not in contact with the liquid like the pump impeller (4) may come. The now assumed difference of the materials between pump impeller (4) and magnet rotor 6 is expressed in a different hatching

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Electromagnetism (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Sliding-Contact Bearings (AREA)
• Rolling Contact Bearings (AREA)
• Magnetic Bearings And Hydrostatic Bearings (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Related Child Applications (2)

Publications (2)

Family

ID=38375284

Family Applications (2)

Family Applications Before (1)

Country Status (9)

Families Citing this family (50)

Family Cites Families (13)

• 2006
  • 2006-03-31 DE DE202006005189U patent/DE202006005189U1/de not_active Expired - Lifetime
• 2007
  • 2007-03-29 KR KR1020087026741A patent/KR101410628B1/ko not_active Expired - Fee Related
  • 2007-03-29 JP JP2009501958A patent/JP5461172B2/ja not_active Expired - Fee Related
  • 2007-03-29 AT AT07723756T patent/ATE472060T1/de active
  • 2007-03-29 DE DE502007002031T patent/DE502007002031D1/de active Active
  • 2007-03-29 CN CN2007800118957A patent/CN101415950B/zh not_active Expired - Fee Related
  • 2007-03-29 US US12/295,350 patent/US8162630B2/en not_active Expired - Fee Related
  • 2007-03-29 AT AT08003862T patent/ATE449263T1/de active
  • 2007-03-29 EP EP08003862A patent/EP1965081B1/fr not_active Not-in-force
  • 2007-03-29 EP EP07723756A patent/EP2002126B1/fr not_active Not-in-force
  • 2007-03-29 ES ES08003862T patent/ES2335946T3/es active Active
  • 2007-03-29 WO PCT/EP2007/002814 patent/WO2007112938A2/fr not_active Ceased
  • 2007-03-29 DE DE502007004191T patent/DE502007004191D1/de active Active

Non-Patent Citations (1)

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