Magnetically driven pump arrangement having a micropump with forced flushing, and operating method

Abstract

A pump arrangement is disclosed including a magnetically drivable micropump for pumping a liquid pumping medium, a bearing carrier as a base part, and an outer magnet and an inner magnet which transmit a torque to the micropump via an axial shaft. Three radial bearing pieces for the rotational mounting (guidance) of the shaft and of the micropump are positioned and fixed in the bearing carrier. The micropump is held in an eccentric bearing by a cover arranged at an end. A duct structure for a forced flow is provided including at least one radial duct portion in the cover and an axial duct portion in the bearing carrier to flush and/or to lubricate the bearings actively with the pumping medium. One of the bearings is arranged closer to the inner magnet and/or another of the bearings is arranged closer to the micropump.

Claims

1. A pump arrangement comprising a micropump (P) for pumping a liquid and comprising a bearing carrier (22) as a base part, wherein an outer magnet (44) and an inner magnet (40) are provided and an outer rotating magnetic field of the outer magnet provides a rotary movement to the inner magnet attached to an axial shaft for rotating the micropump attached to the axial shaft (10), the pump arrangement further having three radial bearing pieces (1, 2, 3) providing rotational bearing support of the shaft (10) and the micropump (P) and positioned in the bearing carrier (22), one of the radial bearing pieces (3) rotatably supporting an outer rotor (80) of the micropump and being arranged eccentrically with respect to the axial shaft (10), and the two other radial bearing pieces (1,2) are axially spaced apart and rotatably support the axial shaft; wherein one of the two radial bearing pieces rotatably supporting the shaft is arranged closer to the inner magnet (40) and the other one is arranged closer to the micropump, wherein both radial bearing pieces supporting the shaft stay spaced apart from one another; and having a cover (26) arranged at an end of the bearing carrier, axially holding the micropump in the eccentric radial bearing piece; a duct structure (23) for guiding a forced flow of liquid as main pressure side flow of the pumped liquid, the duct structure comprises at least a first and second duct portions (23b, 23f) in the cover (26) and first and second further axial duct portions (23c, 23e) in the bearing carrier (22) to flush or lubricate the radial bearing pieces supporting the shaft actively with a flow portion of the main pressure side flow of the pumped liquid and a hood-shaped cap (24), forming a hermetically sealed housing arrangement (20) comprising the bearing carrier, the hood-shaped cap and the cover (26), wherein the duct structure at the pressure side of the micropump provides for the main pressure side flow to cool the hood-shaped cap from an inside thereof.

2. The pump arrangement according to claim 1, wherein the outer magnet (44) and the inner magnet (40) form a magnetic torque transmission and a magnetic drive thus acts on the shaft (10) and an inner rotor (82) of the micropump (P).

3. The pump arrangement according to claim 2, wherein the inner magnet (40) is rotatably moved by a magnetic field produced by a rotating outer magnet arranged radially outside the inner magnet.

4. The pump arrangement according to claim 2, wherein the inner magnet is rotatably moved by a rotating magnetic field produced by a mechanically non-rotating outer stator in the form of a rotating field.

5. The pump arrangement according to claim 2, wherein the torque transmission is a central rotary coupling.

6. The pump arrangement according to claim 4, wherein the inner and outer magnets (44, 40) are arranged concentrically.

7. The pump arrangement according to claim 1, wherein the outer rotor (80) is an outer rotor of an annular gear pump (P) or an outer rotor of an internal gear pump.

8. The pump arrangement according to claim 1, wherein the inner magnet (40) is mounted on an inner magnet carrier (42).

9. The pump arrangement according to claim 8, wherein the inner magnet (40) having several parts.

10. The pump arrangement according to claim 9, wherein the parts are encapsulated by a casing or coating.

11. The pump arrangement according to claim 1, wherein the radial bearing pieces are joined to the bearing carrier by one of gluing, soldering and welding.

12. The pump arrangement according to claim 1, wherein the bearing carrier (22) is of metal or plastics material provided by injection molding.

13. The pump arrangement according to claim 12, in which at least one heating element (71, 72) is integrated in an injection-molded bearing carrier (22).

14. The pump arrangement according to claim 1, wherein the radial bearing pieces providing the bearings are separate precision components positioned and fixed in the bearing carrier (22) by a joining technology.

15. The pump arrangement according to claim 1, wherein maximum dimensions of the micropump (P) are not greater than 20 mm.

16. The pump arrangement according to claim 1, wherein the duct structure comprises a planar portion (23d) extending in a radial direction.

17. The pump arrangement according to claim 1, wherein the duct structure (23) guides the forced flow of liquid-as the main pressure side flow of the pumped liquid, and actively flushes and lubricates the radial bearing pieces supporting the shaft with the flow portion of the main pressure side flow of the pumped liquid.

18. A pump arrangement comprising a micropump (P) for pumping a liquid and comprising a bearing carrier (22) as a base part, wherein an outer magnet (44) and an inner magnet (40) are provided, to magnetically couple a rotary movement to the micropump (P) via an axial shaft (10), and wherein three radial bearings rotationally support the shaft (10) and the micropump (P) and are provided in the bearing carrier (22), one of the radial bearings (3) receiving and rotatably supporting an outer rotor (80) of the micropump and being arranged eccentrically with respect to the shaft (10) and the two other radial bearings (1,2) are axially spaced apart and rotatably support the axial shaft; the bearing carrier (22) being of metal or plastics material made by injection molding and the radial bearings are provided integrated in the bearing carrier (22); the micropump (P) is held in the eccentric radial bearing (3) by a cover (26) arranged at an end of the bearing carrier (22); a duct structure for a forced flow is provided, having a first radially directed duct portion (23b) in the cover (26) and a second axially directed duct portion (23c, 23e) in the bearing carrier (22; one of the radial bearings supporting the axial shaft is arranged closer to the inner magnet (40) and the other radial bearing supporting the axial shaft is arranged closer to the micropump (P).

19. The pump arrangement according to claim 18, wherein a hermetically sealed housing arrangement (20) is formed of the bearing carrier (22) and a hood-shaped cap (24) on the one hand and the cover (26) on the other hand, the pumped liquid cooling the hood-shaped cap (24) from an inside thereof via the duct structure.

20. The pump arrangement according to claim 18, wherein the duct structure for the forced flow comprises a further portion (23e) in the bearing carrier (22) and the at least two portions in the bearing carrier (22) extend substantially in an axial direction.

21. The pump arrangement according to claim 18, wherein yet another portion (23b) of the duct structure extends through the cover (26) and is positioned on a pressure side of the micropump.

22. The pump arrangement according to claim 18, wherein the duct structure comprises a planar portion (23d) extending in a radial direction.

23. A pump arrangement comprising a magnetically drivable micropump (P) for pumping a fluidic medium and comprising a bearing carrier (22) as a base part, wherein an outer magnet (44) and an inner magnet (40) are provided, magnetically coupling a rotary movement to the micropump (P) via an axial shaft (10), wherein the pump arrangement having a pressure side and a suction side; and wherein three radial bearings rotationally mounting the shaft (10) and the micropump (P) are provided in the bearing carrier (22), one of the radial bearings (3) receiving and rotationally supporting an outer rotor (80) of the micropump and being arranged eccentrically with respect to the shaft (10) and the two other radial bearings (1,2) are axially spaced apart and rotatably support the axial shaft; the micropump (P) is held in the eccentric radial bearing (3) by a cover (26) arranged at the end of the bearing carrier; a duct structure is provided at the pressure side of the micropump and having at least a first duct portion (23b) in the cover (26) and as a continuation thereof a second duct portion (23c, 23e) in the bearing carrier (22) for actively flushing or lubricating the two other radial bearings rotatably supporting the axial shaft by a portion of the pumped-fluidic medium.

24. The pump arrangement according to claim 23, wherein a hermetically sealed housing arrangement (20) is formed of the bearing carrier (22), a hood-shaped cap (24) and the cover (26), the pumped liquid for cooling the hood-shaped cap (24) from an inside via the duct structure.

25. The pump arrangement according to claim 24, wherein the hood-shaped cap (24) and the bearing carrier (22) are designed such that the pumped fluidic medium flows onto an inner surface of the cap (24) for cooling.

26. The pump arrangement according to claim 25, wherein more than 50% of the inner surface of the hood-shaped cap (24) is cooled.

27. The pump arrangement according to claim 23, wherein the bearing carrier comprises a concentric elevation or extension.

28. The pump arrangement according to claim 27, wherein the elevation or extension is formed in accordance with a hood-shaped cap and an annular space remains peripherally, wherein the inner magnet (40) axially protrudes, the axial length of which is longer than an axial length of the magnet carrier.

29. The pump arrangement according to claim 27, wherein the concentric elevation or extension carries at an end thereof one of the two other radial bearings and axially opposite thereof a magnet carrier is attached to the shaft (10) for rotation therewith.

30. The pump arrangement according to claim 23, wherein the duct structure for the forced flow comprises a further portion (23e) in the bearing carrier (22) and these at least two portions in the bearing carrier (22) extend substantially in an axial direction and are arranged with a circumferential offset from each other.

31. The pump arrangement according to claim 23, wherein the duct structure (23) guides the forced flow of liquid-as the main pressure side flow of the pumped liquid, and actively flushes and lubricates the two other radial shaft bearings rotatably supporting the axial shaft by a portion of the pumped fluidic medium.

32. A method for pumping a fluid, wherein a rotary movement is transmitted to a micropump (P) via an axial shaft (10) and comprising a pump arrangement, comprising the micropump (P) for pumping the fluid and comprising a bearing carrier (22) as a base part, wherein an outer magnet (44) and an inner magnet (40) are provided to transmit a rotary magnetic field to the micropump (P) for rotating the micropump via the axial shaft (10), and wherein three radial bearing pieces-providing a rotational bearing support of the shaft (10) and the micropump (P) and positioned in the bearing carrier (22), one of the radial bearings (3) rotatably supporting an outer rotor (80) of the micropump and being arranged eccentrically with respect to the shaft (10) and the two other radial bearing pieces (1,2) are spaced apart and rotatably support the axial shaft; a cover (26) arranged at an end of the bearing carrier holds the micropump in the eccentric bearing (3); a duct structure guiding a forced flow of the fluid, the duct structure comprises at least a first duct portion (23b) in the cover (26) and as a continuation thereof at least a first second duct portion (23c, 23e) in the bearing carrier for actively flushing or lubricating the shaft bearings with a portion of the pumped fluid; one of the other two radial bearing pieces is arranged closer to the inner magnet (40) and the other radial bearing piece thereof is arranged closer to the micropump.

33. The pump arrangement according to claim 32, wherein the duct structure (23) guides the forced flow of liquid-as the main pressure side flow of the pumped liquid, and actively flushes and lubricates the shaft bearing with the portion of the pumped liquid.

Description

(1) Embodiments of the invention will be described with reference to the following figures. These will deepen and increase understanding of the invention(s).

(2) FIG. 1 is a vertical section through a first example of a magnetically drivable pump arrangement comprising a micropump. The bearing carrier 22 is the center of the construction; above is a hood-shaped housing portion 24 and below is a cover 26 which rests in an axially bearing manner against the micropump P comprising the outer rotor 80. The hood-shaped housing portion, which hereinafter is also referred to as a separating can or separating cup, is part of a housing 20 which comprises the hood-shaped housing portion 24, a bearing carrier 22 and a cover 26.

(3) FIG. 2 is a view of the cover side (from below in FIG. 1), the directions top and bottom relating merely to the representation in the figures and not being prejudicial to the construction as such in terms of its installation direction. A sectional plane III-III is sketched in FIG. 2 and shown in FIG. 3, the section having three inflections A, B and C which should be taken into account when considering FIG. 3. As a result, the ducting 23, which will be described in more detail below, is clearer in FIG. 3 than it can be shown in FIG. 1, which corresponds to a section III-III which has no inflection points but rather extends centrally in a planar manner.

(4) FIG. 2a is a detail enlargement of the center of FIG. 2, in order to clarify the statements made with respect to FIG. 2. In particular, the micropump P which comprises an outer rotor 80 and an inner rotor 82 is highlighted here. The shaft 10 as an axial reference of the arrangement interlocks with a polygonal portion 10a in a correspondingly formed inner opening of the inner rotor 82, in order to drive said rotor.

(5) FIG. 3 is the sectional view along the line III-III from FIG. 2 and having the inflections A, B and C to be taken into account, as shown therein. In addition, FIG. 3 also shows a fluid guidance system F from the intake side to the pressure side of the micropump, such as a flushing flow F. The associated duct structure 23 is often used as a synonym for the flow guidance of the liquid pumping medium which follows the duct structure 23. The duct structure 23 consists of a plurality of portions which will be described.

(6) FIG. 4 is a further embodiment of how the arrangement according to FIGS. 1 and 2 is inserted into a housing 20* and driven by a drive motor 95 via a rotatable outer magnet 44. The shaft 10 and the hood-shaped portion 24 of the in this case inner housing 20 serve as a reference.

(7) FIG. 5 is a further embodiment comprising a stationary stator magnet 48 which can produce a rotating magnetic field and drives the inner magnet 40 upon transmission of a torque. Owing to the electrical production of the rotating field, access to the modified housing 20 is achieved via a connection plug 91 which does not need to convey a rotatable shaft into the housing 20 from the outside. An integrated heater 71, 72 of a particular design is also shown.

(8) A liquid pumping medium (not shown physically), which can have different material compositions but is suitable for pumping by a micropump, is to be pumped. For automotive construction this is for example urea, water or methanol. Hazardous media, for example in chemistry, crystallizing media, for example the above-mentioned urea in automotive construction, or volatile media, for example methanol in fuel cell technology, can equally be pumped using the embodiments described below.

(9) The pumping is continuous pumping while the micropump P, which is inserted in a bearing 3 which is referred to as a rotor seat in FIG. 1, is in operation.

(10) FIG. 1 shows as a central component a shaft 10 which is arranged in the axis of the construction. It is rotatably mounted in two further bearings 1 and 2, the two bearings having a spacing a from each other.

(11) All three said bearings 1, 2 and 3 are designed as bearing pieces which are precision bearing parts. They are inserted separately into the bearing carrier 22 and fixed there by means of a joining technology after positioning. Gluing, soldering or welding are suitable joining technologies.

(12) Oxide ceramics, non-oxide ceramics, metal or even plastics material are possible materials for the precision bearings, which are produced separately to precision. Examples of oxide ceramics are aluminum oxide or zirconium oxide. In a particular configuration, in the case of expected high wear or when a long service life is desired, ceramics are used. In normal applications with relatively low wear, metal can be used. Plastics material is also a possibility for the bearings, which in the case of a one-piece design of the bearing carrier 22 are preferably produced by injection molding directly with the production of the bearing carrier 22 as plastics material bearing regions, but are not separate bearing parts but rather only bearing regions or, in functional terms, bearings.

(13) The construction of the housing 20 in FIG. 1 comprises firstly the following three components: hood-shaped cap 24, bearing carrier 22 and cover 26. The bearing carrier is designed such that it receives the three aforementioned radial bearings 1, 2 and 3 and represents the core piece of the magnetically driven micropump and of the associated housing construction. The bearing carrier can have relatively wide tolerances and be made of less solid materials, for example aluminum or plastics material. The precision and accuracy to be obtained are achieved by installing the bearing pieces which are connected to the bearing carrier 22 by joining.

(14) The bearing carrier 22 also serves to accommodate all the static seals, which are not identified separately in the figures but are immediately clear to a person skilled in the art. These are O-rings and seals for attaching the cover 26, the hood-shaped cap 24 (also referred to as a separating can) and the magnetic drive unit, which can be seen for example in FIG. 4 with its lower portion and a rotatable outer magnet 44.

(15) In FIG. 1, the mounting of the cover 26 from the lower side of the bearing carrier 22 is symbolized by a penetrating screwing device 22. This mounting can also take place as shown for the mounting of the hood-shaped cap 24 on the other side of the bearing carrier 22, specifically by means of pressure pads 21, via which a mounting force of a further screwing device 22 is uniformly transmitted to the periphery of the lower mounting flange of the hood 24. If the cover 26 is made for example of ceramic material, such an arrangement with pressure pads (not shown separately in FIG. 1) is recommended.

(16) The magnetic drive system is placed inside the hood-shaped cap 24, around the shaft 10 at the upper end. In this case the shaft has an end which is remote from the pump or remote from the rotor, which is also referred to as the drive-side or magnet-side end of the shaft 10. The other end 10a of the shaft 10 interlocks with the inner rotor 82, as shown in FIG. 2a. This is the pump-side end of the shaft 10, which end is supported axially against the cover 26.

(17) The drive takes place from outside (not shown in FIG. 1) and acts as a coupling of a torque, in particular as a central rotary coupling, the inner magnet 40 and an outer magnet 44 or 48 shown in FIGS. 4 and 5 being arranged concentrically with each other. It is possible to speak of a central rotary coupling when the outer magnet and the inner magnet rotate together. They are then arranged concentrically with each other.

(18) The inner magnet 40 is axially longer than a carrier 42 for this inner magnet, which carrier is connected to the shaft 10 for rotation therewith and is also connected to the inner magnet 40 for rotation therewith. This inner magnet carrier is axially shorter and is located at the upper end, not touching but rather leaving a gap, close to the upper wall 24b of the hood-shaped cap 24.

(19) An achievable relatively large spacing which the two first bearings 1 and 2, provided for the rotary mounting of the shaft 10, have from each other should be mentioned. The lower bearing is located close to the micropump P, actually directly at the micropump P and serves as an opposing axial bearing for the two rotors 80, 82. The axial bearing opposing these rotors is the inner region of the cover 26. An achievable spacing a is more than three times larger than the axial height of one of the two bearings 1, 2.

(20) The bearing 2 remote from the pump is placed on an elevation or extension 22a arranged concentrically with the hood-shaped cap. At its (upper) end said elevation or extension carries said bearing piece 2 and leaves an annular gap in relation to the inner magnet carrier 42. The elevation or extension is also designed geometrically such that it forms a cylindrical annular gap in relation to the inner magnet 40. The inner magnet 40 in turn has axial spacing to leave an annular space 23d which forms a portion of a duct structure 23, which will be described in more detail below.

(21) Since the inner magnet 40 also leaves a cylindrical annular gap in relation to the inner surface of the hood-shaped cap 24 (separating can), a fluid can flow through the entire interior of this hood-shaped cap provided that no above-described geometric parts are placed there. In particular, an inner wall of the hood-shaped cap 24 should be mentioned, which inner wall can be cooled by a fluid flow which will be described below, for which purpose the aforementioned annular gap is provided outside the inner magnet 40.

(22) The shaft 10 has, between the two bearing pieces 1, 2, an annular space 22b which is radially larger than a diameter of the shaft 10.

(23) The shaft 10 is arranged centrically with respect to the hood-shaped cap 24, while the rotor seat as bearing piece 3 is arranged eccentrically. This bearing piece 3 receives the outer rotor 80 mounted eccentrically with respect to the centrically rotated inner rotor 82.

(24) FIGS. 2 and 2a show the pump P comprising the inner rotor and the outer rotor 80, 82 and also the expansion and tapering of the rotating pumping chambers, typical of an annular gear pump. Alternatively, instead of the annular gear pump according to FIG. 2a, an internal gear pump can also be used, which is not shown separately in the figures.

(25) The fluid is supplied (on the intake side) via a duct portion 23a (intake side). The outlet of the pump P discharges into a pressure nodule, which can be seen in FIG. 2a and transitions into a radial duct portion 23b. Said portions 23a, 23b are portions of the duct structure 23 which guides the fluid from the inlet F.sub.u (intake side) to the outlet F.sub.D (pressure side).

(26) The pressure side F.sub.D is located at the outlet of the pump P in the radial duct portion 23b. A further portion of the ducting 23, which passes through the bearing carrier 22 andin the examplecomprises two axial duct portions 23c and 23e, is located between F.sub.D and F.sub.D. These two duct portions are shown clearly in FIG. 2a. They have a peripheral offset from each other but both extend in the axial direction in the bearing carrier 22.

(27) The axial section in FIG. 3 will be described with reference to FIG. 2. The sectional plane III-III has three inflections or lines A, B and C. A is located in the center of the axis or the shaft 10. The second inflection B is located in the center of the first axial portion 23c of the fluid guidance system (the duct structure 23). The second inflection is located in the second axial portion 23e of the duct structure 23.

(28) Further axial portions of the duct structure 23 can be found in the cover 26. The portion 23a is provided on the inlet side (intake side) of the fluid F. An additional axial portion 23f is provided in the cover 26 on the pressure side of the arrangement in FIG. 3.

(29) A further radial portion of the ducting 23 is the transition of the direct pressure outlet of the pump P along the portion 23b of the duct structure 23, towards the first axial portion 23c in the bearing carrier 22.

(30) By means of the duct structure 23, a forced flow is produced which occurs during operation of the pump P and provides not only useful pumping of the fluid F but also performs a number of functions.

(31) The above-described bearings 1, 2 and 3 are lubricated or flushed, or both. The separating can 24 (as the hood-shaped cap of the housing 20) is cooled from the inside, the cooling surface being at least 50% of the entire inner surface of the hood 24, but preferably over 70%.

(32) This can be seen at a first elevation 22c of the bearing carrier 22, which elevation transitions in a tapering manner into the above-described elevation or extension 22a. A short distance away the hood 24 abuts against the edge surface and is attached to the bearing carrier 22 by the peripheral pressure pad 21 and accordingly positioned screws, of which one screw 22 can be seen in FIG. 1. Preferably, three such mounting screws can be provided (not shown). Peripheral static seals, which are not given separate reference numerals but can be identified by the hatching, are shown in all the figures.

(33) By means of the axial duct portion 23c, the fluid F is supplied on the pressure side as pressurized fluid FD, not directly to the outlet in the cover 26 but first to the above-mentioned annular space 23d which is formed between an upper surface of the bearing carrier (extending between the shoulders 22c and 22a) and a downward facing surface of the inner magnet 40. This portion 23d is planar and is part of the duct structure 23.

(34) The axial portion 23c guides pressurized fluid to this planar annular space 23d, which fluid is distributed into the remaining free spaces inside the hood 24 and flows therethrough. It can flow back out via the second axial duct portion 23e and be supplied to the outlet side or pressure side of the micropump arrangement comprising bearings according to the figures via the axial duct portion 23f in the cover 26.

(35) A large portion of the inner surface of the cylindrical wall 24a of the hood-shaped cap 24 can thus be cooled.

(36) Although only the axial duct portion 23e of the duct structure 23 in the bearing carrier (on the pressure side) can be seen in FIG. 1 owing to the position of the section, and a duct segment 23b actually extending radially cannot be seen in the cover 26, the radial portion 23b and the first axial portion 23c can be seen in the modified section according to FIG. 2a.

(37) In addition to the main flow of the fluid F, a flushing flow F should also be mentioned. This penetrates the bearing surfaces of the precision bearings along the path F in FIG. 3. In so doing it flushes the two bearings 1, 2 and, owing to the pressure difference, reaches the pump P on the intake side thereof. Lubrication of the bearings is also achieved.

(38) The flushing flow F passes along the shaft and into the central cavity 22b through which the shaft 10 passes, or in which it rotates, while it is rotatably supported by the two bearing pieces 1, 2, which have a mutual spacing a.

(39) The path along the fluid guidance system 23 will be summarized and described again clearly.

(40) The liquid pumping medium is drawn in on the intake side through the housing cover 26 and fed to the axial duct portion 23a in the micropump P comprising rotors 82, 80, or drawn in thereby. It follows the rotating pumping chambers according to FIG. 2a of the micropump (also referred to simply as the pump) and is fed to the pressure-side portion of the fluid guidance system. The pressure-side outlet of the pump P ends in the radial duct portion 23b. At the end thereof it is fed to the internal duct 23c in the bearing carrier 22 and conveyed into the separating can 24. The fluid flows through this separating can (the hood-shaped cap 24) and reaches the pressure-side opening in the housing cover 26 via a further axial duct portion 23e.

(41) An aligned duct portion 23f, which is a continuation of the axial duct portion (or duct segment) 23e, is provided in the cover 26. By means of this fluid guidance system, fluid flows actively through all regions of the pump, while the dead volume of the pump is limited. The pressure difference between the rotor-side end of the shaft and the drive-side end of the shaft 10 provides forced flushing F and thus lubrication of the bearings 1, 2 by the liquid pumping medium.

(42) The above-described bypass flow, referred to as flushing flow F, follows the pressure gradient between a pumping pressure in the separating can region (inside the hood 24) and the lower pressure in the region of the rotor bearing assembly (the intake side). The medium flowing through the separating can 24 is simultaneously used to cool the separating can and the inner magnet 40.

(43) Owing to the rotating magnetic field and the mostly metal design of the hood-shaped cap 24, heat is produced via eddy currents, and the fluid flow is used to carry away this heat.

(44) In another embodiment, shown in FIG. 5, the separating can may also be omitted. The hood-shaped cap is shown again in FIG. 5, but can be dispensed with owing to the drive shown therein and can be omitted. This embodiment (not shown) is made possible in that an outer housing 20 is formed which is produced outside the outer magnet 48 and is connected in a sealing manner to the bearing carrier. This can be done via a screwing device, of which two screws 22 can be seen. The pressure pad 21 and the hood-shaped cap 24 are omitted.

(45) Both the outer magnet 48, which carries current-carrying windings 49 (not shown), and the inner magnet 40 are then arranged in the same space and distinguished by being referred to as outer and inner. Owing to the lack of a rotary movement of the outer magnet 48, the torque is transmitted to the inner magnet 40 via the rotating field.

(46) The electrical energy is supplied via the connection plug 91, which represents an opening in the motor housing 28, which is part of the modified housing construction 20. An integrated control system 90 on a circuit board is shown and produces the current flows in the spatially distributed windings 49 to produce the rotating field.

(47) In a particular type of embodiment, which need not necessarily apply only to this example, but can also be used for the other examples, a heating winding 72 is arranged around the shaft in the bearing carrier 22. A further heating winding 71 can be located closer to the cover 26 and surround the pump P.

(48) The heating windings 71, 72 are electrically conductive resistance windings to which current is applied. This current can also be supplied via the connection cover 91.

(49) In the other regions of FIG. 5 this example corresponds to the design of that in FIGS. 1 and 2.

(50) The integrated heaters 71 and/or 72, which can be provided individually or in combination, improve the cold start capability of the pump when thick or viscous pumping media are to be pumped which, owing to reduced ambient temperature, cannot yet be pumped, for example in automotive construction.

(51) The heating can be used particularly advantageously in connection with a bearing carrier 22 which is produced by injection molding, for example from metal or plastics material.

(52) FIG. 4 shows a further embodiment which uses the construction from FIGS. 1/3. In this case a motor 95 is shown as a drive on a superordinate housing construction 20*, a motor shaft 94 of which motor engages mechanically in a cover plate 29 of the housing construction 20* and rotates a rotating outer magnet 44 via an outer magnet carrier 45 which opens out radially. Said outer magnet, coupled via a magnetic field and by the hood-shaped cap 24, entrains the inner magnet 40 in rotation and forms a central rotary coupling. The motor 95 is actuated by an electrical control system 96 which is shown in detail in FIG. 2 and is preferably placed at the upper end of the motor 95.

(53) The inner magnet 40 and outer magnet 44 are advantageously concentric with each other and not offset from each other in the axial direction. This minimizes axial forces which can/could act on the shaft 10 via the magnetic field.

(54) The superordinate housing construction 20* is connected mechanically to the bearing carrier 22 in a sealing manner. Again, this can be done by means of a screwing device, of which two screws 22 can be seen, as also shown in FIG. 5.

(55) Worth noting, in this embodiment too, is the use of only one axial bearing of the shaft 10, namely at the cover 26, and the free end of the shaft close to the upper horizontal wall 24b of the hood-shaped cap 24. Also worth noting, not only in this embodiment but also in the other embodiments, is the lack of any dynamic seal, that is to say any shaft seal to be provided to seal in relation to a rotating part.

(56) The lower side of the cover 26 is 26d and on this side an inlet and outlet are provided, which in this case are provided with O-ring seals and have a larger diameter than the diameter of the outgoing duct portions.

(57) The lower surface of the bearing carrier 22 is 22d. The cover 26 is placed on this surface in order to achieve the axial guidance of the duct portions 23e and 23b and also to guide the axial portion 23a to the intake side of the pump P and also to guide the radial duct portion 23b to the pressure-side outlet side of the pump P.

(58) The following can be said with regard to the drive-side magnet constructions comprising the outer magnet 44 and the inner magnet 40, and also applies to the examples in FIGS. 1 to 3.

(59) At the drive-side end of the shaft 10, the inner magnet 40 arranged there via the magnet carrier 42 is preferably in one piece (made from one piece). It can consist of hard ferrite. Another mode of construction is the coating of a plastics-bonded magnetic material around the end of the shaft (in the region of the outer magnet 44) and without a shaft-side magnet carrier. As a further alternative, the inner magnet 40 can be made of a plurality of parts. This plurality of parts is held on the magnet carrier 42. For this purpose a plurality of individual magnets arranged in a ring (as segments or sectors) can be used and is assembled on the magnet carrier 42. If only one piece of a magnet is provided, this sits as an annular magnet on the magnet carrier 42 and is joined thereto for rotation therewith.

(60) The plurality of individual magnet pieces (in the form of plate-like magnets) made of relatively high-grade magnetic material can be assembled on the magnet carrier 42. Rare earth magnets are examples of such plate-like magnets.

(61) If corrosive media are to be pumped, the individual magnets (as magnet pieces) can additionally be coated or encapsulated. However, such magnets would be coated or encapsulated only if they come into physical contact with the pumped corrosive fluid. For the inner magnet 40 this is the case in all the embodiments. For the outer magnet 44 this is the case only when the pumping fluid flows around it as stator 48, without a hood-shaped cap 24.

(62) The embodiment, described with reference to FIG. 5, of the production of the bearing carrier 22 by injection molding entails the omission of bearing pieces which would be added separately and the provision of bearing regions as functional bearings. Three of these bearings (produced in one piece or in an integrated manner as bearings) are provided. Two of these bearing regions guide and support the shaft 10. A further one supports the outer rotor 80 of the micropump P.

(63) The bearings can already be integrated during production by injection molding, without additional bearing components (referred to above as bearing pieces) needing to be added. This embodiment is not shown separately, but can be understood by analogy.