EP2994642B1 - Pump arrangement - Google Patents

Description

The invention relates to a pump arrangement, in particular magnetic coupling pump arrangement, with a formed by a pump housing of the pump assembly interior, a bottom having a containment shell which hermetically seals a chamber enclosed by him against the interior formed by the pump housing, a rotatable about an axis rotatable impeller shaft, an an impeller arranged at one end of the impeller shaft, an inner rotor disposed at the other end of the impeller shaft, an auxiliary impeller disposed in the chamber, and an outer rotor cooperating with the inner rotor.

From the DE 27 54 840 A1 Such a magnetic coupling pump arrangement with Hilfslaufrad is known. The auxiliary wheel is disc-shaped and provided with radial bores. However, this embodiment represents in terms of their efficiency an inefficient impeller or conveyor variant and reduces the overall efficiency of the pump assembly. In addition, a not inconsiderable effort to produce the Hilfslaufrades is required.

The US 4,850,818 A shows a magnetic coupling pump with a formed as an inner rotor magnetic holding element. The magnet holding element is provided with blades on the front side, along its outer edge, in order to ensure a low liquid pressure behind the end face of the magnetic element.

The object of the invention is to provide a magnetic coupling pump assembly with an easy to manufacture forced lubrication current drive with improved efficiency.

The object of the invention is achieved in that the auxiliary wheel of semi-open design and is fixed with its open side on the bottom of the gap pot facing end side of the inner rotor.

Since the auxiliary impeller is attached with its open side to the bottom of the gap pot facing end side of the inner rotor, it is possible to use the advantages of a closed channel wheel by a much easier to manufacture open impeller. In addition, the impeller has no hub and is easy to assemble and disassemble.

According to one embodiment, the containment shell has a base body with an open side and an open side opposite by means of a curved bottom closed side and the Hilfslaufrad has a support plate whose facing the bottom of the gap pot outer surface has a curvature.

By the curvature of the outer surface of the support disc substantially corresponds to the curvature of the bottom of the can, the dead space usually spanned by the curved bottom of the can is filled, whereby no additional required by the magnetic coupling axial space is used up. In addition, the pressure resistance of the split pans is not unnecessarily reduced.

To improve the flow guidance of the medium when entering a fluid inlet region of the auxiliary wheel, a paraboloid-like elevation is ideally provided in the middle of the support disk.

According to a further embodiment, it is provided that a plurality of elevations are formed on the support disk with a radial distance to the elevation, which form blades and corresponding impeller channels of the auxiliary impeller.

According to a further embodiment, it is proposed that the impeller ducts have a channel bottom, which is similar to a einhüftigen basket bow. This leads to an improvement of the flow guidance.

In a further embodiment of the invention, it is provided that the upper side of the blades facing away from the support disk has a step near the channel entry edge. The stage serves as an abutment shoulder and centering device for exact alignment of the attached to the inner rotor auxiliary wheel.

In the sense of a simple and cost-effective production, the impeller shaft and the inner rotor form a cover disk of the auxiliary wheel opposite the support disk.

According to a further advantageous embodiment, further impeller passages are formed in the elevations forming the blades, which impeller extend in the radial direction from the outer circumferential surface to near the step.

To improve the flow guidance of the medium, the further impeller channels have a channel bottom, which at least partially has a curvature which substantially corresponds to the curvature of the outer surface of the carrier disk.

According to the invention, the impeller shaft has an axial passage which communicates with the fluid inlet region of the auxiliary impeller.

In the context of the invention, it is proposed that in a further embodiment fluid channels are provided in the inner rotor, which open into the other impeller channels of the auxiliary rotor.

Fig. 1

den Längsschnitt durch eine Magnetkupplungspumpenanordnung mit einem erfindungsgemäßen Hilfslaufrad, die

Fig. 2

den Längsschnitt durch die Magnetkupplungspumpenanordnung gemäß Fig. 1 in einer gegenüber der Fig. 1 um 90 ° gedrehten Ebene, die

Fig. 3

ein der Fig. 1 entsprechendes Hilfslaufrad in vergrößerter Darstellung, die

Fig. 4

eine detaillierte dreidimensionale Darstellung des Hilfslaufrades gemäß Fig. 3, die

Fig. 5

eine detaillierte dreidimensionale Darstellung einer weiteren Ausführungsform des erfindungsgemäßen Hilfslaufrades, die

Fig. 6

den Längsschnitt durch eine Magnetkupplungspumpenanordnung mit einem erfindungsgemäßen Hilfslaufrad gemäß der Fig. 5, die

Fig. 7

den Längsschnitt durch eine Magnetkupplungspumpenanordnung gemäß Fig. 6 mit einem gegenüber der Fig. 6 um 45° gedrehten Innenrotor und die

Fig. 8

den Längsschnitt durch die Magnetkupplungspumpenanordnung gemäß Fig. 6 in einer gegenüber der Fig. 6 um 90° gedrehten Ebene.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below. It shows the

Fig. 1

the longitudinal section through a magnetic coupling pump assembly with an auxiliary impeller according to the invention, the

Fig. 2

the longitudinal section through the magnetic coupling pump assembly according to Fig. 1 in one opposite the Fig. 1 rotated 90 °, the

Fig. 3

one of the Fig. 1 corresponding Hilfslaufrad in an enlarged view, the

Fig. 4

a detailed three-dimensional representation of the auxiliary wheel according to Fig. 3 , the

Fig. 5

a detailed three-dimensional representation of another embodiment of the auxiliary impeller according to the invention, the

Fig. 6

the longitudinal section through a magnetic coupling pump assembly with an auxiliary impeller according to the invention according to the Fig. 5 , the

Fig. 7

the longitudinal section through a magnetic coupling pump assembly according to Fig. 6 with one opposite the Fig. 6 rotated by 45 ° inner rotor and the

Fig. 8

the longitudinal section through the magnetic coupling pump assembly according to Fig. 6 in one opposite the Fig. 6 rotated by 90 ° level.

The Fig. 1 and 2 show a pump assembly 1 in the form of a magnetic coupling pump assembly. The pump arrangement 1 has a multipart pump housing 2 of a centrifugal pump, which comprises a hydraulic housing 3 designed as a spiral housing, a housing cover 4, a bearing support lantern 5, a bearing support 6 and a bearing cover 7.

The hydraulic housing 3 has an inlet opening 8 for sucking in a conveyed medium and an outlet opening 9 for ejecting the conveyed medium. The housing cover 4 is arranged at the inlet opening 8 opposite side of the hydraulic housing 3. On the side facing away from the hydraulic housing 3 of the housing cover 4, the bearing support lantern 5 is attached. The bearing carrier 6 is attached to the housing cover 4 opposite side of the bearing support lantern 5. The bearing cap 7 is in turn secured to the side facing away from the bearing support lantern 5 side of the bearing support 6.

A split pot 10 is attached to the side facing away from the hydraulic housing 3 side of the housing cover 4 and extends at least partially by a pump housing 2, in particular from the housing cover 4, from the bearing support lantern 5 and the bearing support 6 limited interior 11. The containment shell 10 seals one of hermetically sealed to him and the housing cover 4 chamber 12 from the interior 11 from.

A rotatable about an axis of rotation A impeller shaft 13 extends from a limited by means of the hydraulic housing 3 and the housing cover 4 flow chamber 14 through an opening provided in the housing cover 4 opening 15 into the chamber 12th

An impeller 16 is fastened to a shaft end of the impeller shaft 13 located within the flow chamber 14, an inner rotor 17 arranged inside the chamber 12 is arranged at the opposite end of the shaft, which has two shaft sections 13a, 13b with increasing diameters. The inner rotor 17 is equipped with a plurality of magnets 18, which are arranged on the side of the inner rotor 17 facing the gap pot 10. On the inner rotor 17, an auxiliary wheel 20 is fastened by means of screws 19 or other suitable fastening means.

Between the impeller 16 and the inner rotor 17, a bearing assembly 21 operatively connected to the impeller shaft 13 which is rotatably driven about the rotation axis A is arranged.

An unillustrated drive motor, preferably an electric motor, drives a drive shaft 22. The drivable about the axis of rotation A drive shaft 22 is arranged substantially coaxially with the impeller shaft 13. The drive shaft 22 extends through the bearing cap 7, the bearing support 6 and at least partially into the bearing support lantern 5. The drive shaft 22 is mounted in two housed in the bearing support 6 ball bearings 23, 24. At the free end of the drive shaft 22, a plurality of magnets 25-bearing outer rotor 26 is arranged. The magnets 25 are arranged on the side of the outer rotor 26 facing the containment shell 10. The outer rotor 26 extends at least partially over the containment shell 10 and cooperates with the inner rotor 17, such that the rotating outer rotor 26 by means of magnetic forces the inner rotor 17 and thus the impeller shaft 13 and the impeller 16 also set in a rotational movement.

The Indian Fig. 3 Enlarged pot 10 shown has a substantially cylindrical body 27. The main body 27 is open at the side facing the housing cover 4 and closed at the side opposite the open side by means of a curved bottom 28. On the open side, a ring-like connection flange 29 is arranged, which is integrally formed with the base body 27 or fixed thereto by welding or other suitable fastening means or devices, such as screws, rivets or the like. The connecting flange 29 has a plurality of bores 30 extending parallel to the axis of rotation A, through which screws 31 can be inserted and screwed into corresponding threaded bores in the housing cover 4. The bottom 28 of the split pot 10 is formed by a substantially spherical segment-shaped dome region 32 and an outer, the transition region between the base body 27 and dome region 32 forming rim region 33.

Like from the Fig. 3 and 4 can be seen, the auxiliary wheel 20 has a support plate 34, the bottom 28 of the gap pot 10 facing outer surface has a curvature. The curvature of the outer surface of the support plate 34 substantially corresponds to the curvature of the bottom 28 of the can 10 in the middle of the support plate 34 is a paraboloid-like elevation 35 in a fluid inlet region 36 is provided. Furthermore, a plurality of elevations are formed on the support disk 34 with a radial distance to the elevation 35, which blades 37 form a channel inlet edge 38 facing the elevation 35 and corresponding impeller ducts 39 of the auxiliary impeller 20. The elevation 35 contributes to an improvement in the flow guidance of the medium when it enters the impeller channels 39 of the auxiliary impeller 20. In the embodiment shown, the blades 37 extend curved from the fluid inlet region 36 to an outer circumferential surface 40 of the auxiliary rotor 20. The impeller channels 39 have a channel bottom 41, which in turn has a curved shape which substantially corresponds to the curvature of the outer surface of the support disk 34. The channel bottom 41 the impeller channels 39 is formed in the longitudinal section shown similar to a einhüftigen basket bow, as in the Fig. 6 shown. The impeller channels 39 have a first width W1 at the fluid inlet region 36 and a second width W2 at the outer lateral surface 40, wherein the second width W2 is greater than the first width W1 or at least the first width W1.

The support disk 34 facing away from the top of the blades 37 has near the channel inlet edge 38, a step 42 which serves as a contact shoulder and centering device for the attached to the inner rotor 17 auxiliary impeller 20. On one of the support plate 34 opposite cover disc, which closes the trained between the blades 37 impeller 39, can be dispensed with, since the impeller shaft 13 and the inner rotor 17 form the cover plate of the auxiliary rotor 20. Due to its semi-open design, the auxiliary wheel 20 is both casting technology, as easy to demold, as well as by mechanical processing, since the impeller channels are easily ausfräsbar, easy to manufacture.

Radially outwardly spaced from the steps 42, extending through the support plate 34 and the blades 37 mounting holes 43 are provided, through which the screws 19 inserted and screwed into at the bottom 28 of the gap pot 10 facing side of the inner rotor 17 formed threaded holes 44 , The auxiliary wheel 20 is thus fastened with its open side on the bottom 28 of the gap pot 20 facing end face of the inner rotor 17. At the side opposite the channel inlet edge 38, each blade 37 preferably has at least one recess 45. This generates an additional pressure increase.

As in Fig. 2 1, at least one passage openings 46 are provided in the housing cover 4 and at least one radial passage opening 48 is provided in a bearing ring carrier 47 which fixes the bearing arrangement 21. The through-opening 48 extends through a flange-like region 49 with which the bearing ring carrier 47 positioned coaxially with the axis of rotation A and extending into the chamber 12 is fastened to the housing cover 4 by means of a screw connection, not shown. The passage openings 46 and 48 connect the flow chamber 14 with an inner region 50 of the bearing ring carrier 47th

Thus, for the cooling and lubrication of the bearing assembly 21, fluid may be withdrawn from the flow chamber 14 and supplied to the bearing assembly 21 via the ports 46 and 48, respectively. Via at least one radial bore 51, the conveying medium is conveyed from the inner region 50 into an axial passage 52 which extends from a region of the impeller shaft 13 which is surrounded by the bearing assembly 21 to the end of the impeller shaft 13 located within the chamber 12 and thus to the auxiliary impeller 20 extends. The axial channel 52 is thus in communication with the fluid inlet region 36 of the auxiliary impeller 20. If necessary, at least one further radial bore 53 is formed, which is also in communication with the axial passage 52 formed in the impeller shaft 13. The auxiliary wheel 20 promotes the medium used for cooling and lubrication radially outward into the chamber 12, from where it has several in the Fig. 1 shown axial through holes 54 formed in the flange-like region 49 and in the housing cover 4 formed through holes 55 is conveyed back into the flow chamber 14.

The Fig. 5 to 8 show a further embodiment of the invention. That in the Fig. 5 Auxiliary impeller 20 shown in detail has blades 37 formed by elevations on the support disk 34, which impeller channels 39 define radially outwardly extending from the fluid inlet region 36. In the exemplary embodiment shown, the blades 37 extend in a straight line from the fluid inlet region 36 to the outer lateral surface 40 of the auxiliary impeller 20. The impeller channels 39 have a first width W1 at the fluid inlet region 36 and a second width W2 at the outer lateral surface 40, the second width W2 being greater as the first width W1 or at least the first width W1 corresponds.

In the blades 37 forming increases further impeller channels 56 are formed, which also extend in the radial direction also substantially straight, ie without or without significant curvature, from the outer surface 40 to close to the level 42 and have a channel bottom 57, at least partially a vault which substantially corresponds to the curvature of the outer surface of the support plate 34. The channel bottom 57 of the impeller 56 is formed in a longitudinal section similar to a einhüftigen basket bow, as in the Fig. 7 shown. The impeller passages 56 extend from the region 42 adjacent the step to the outer skirt surface 40 and have a first width W3 at a fluid inlet region 56a and a second width W4 at the outer lateral surface 40, the second width W4 being greater than the first width W3 or at least the first width W3 corresponds.

The Fig. 6 to 8 show a pump assembly 1, which with a according to the Fig. 5 shown auxiliary impeller 20 is equipped. The view of Fig. 6 and 7 correspond to the view of Fig. 1 , The view of Fig. 8 corresponds to the view of Fig. 2 , Like from the Fig. 6 as can be seen, the at least one radial bore 53 leads into one in comparison to the Fig. 1 and 2 In addition, the bearing ring carrier 47 has fluid channels 58 running parallel to the axis of rotation A, which connect the inner region 50 of the bearing ring carrier 47 with the chamber 12 enclosed by the gap pot 10 and the housing cover 4.

The Fig. 7 shows the in the Fig. 6 In the inner rotor 17 fluid channels 59 are provided, which are arranged at approximately the same radial distance from the axis of rotation A, as the fluid channels 58 of the bearing ring carrier 47 and thus, at least in the position shown, with these lie substantially in alignment. The fluid channels 59 open into the impeller channels 56 of the at the bottom 28 of the gap pot 10 facing end face of the inner rotor 17 arranged auxiliary impeller 20th

For cooling and lubrication of the bearing assembly 21 14 medium is removed from the flow chamber and, as in the Fig. 8 shown, via the at least one passage opening 46 in the housing cover 4 and the at least one passage opening 48 in the flange-like region 49 of the bearing ring carrier 47 of the bearing assembly 21 is supplied. About the at least one radial bore 53, the fluid from the inner region 50 of the bearing ring carrier 47 in the axial channel 52 and the auxiliary wheel 20th promoted. The auxiliary impeller 20 conveys the medium used for cooling and lubrication by means of the impeller channels 39 radially outward into the chamber 12.

At the same time according to Fig. 7 the conveying medium taken from the flow chamber 14 is conveyed from the inner region 50 of the bearing ring carrier 47 via the fluid passages 59 formed in the inner rotor 17 into the impeller passages 56 of the auxiliary runner 20 and radially outwards into the chamber 12.

From the chamber 12, the medium via the in the Fig. 6 and Fig. 7 shown formed in the housing cover 4 at least one passage opening 55 back into the flow chamber 14 promoted.

In the embodiments shown, the auxiliary impeller 20 is shown with either the impeller ducts 39 or the impeller ducts 39 and the impeller ducts 56. It is understood that the auxiliary impeller 20 may also be provided exclusively with the impeller channels 56. <U> REFERENCE LIST </ u> 1 pump assembly 27 body 2 pump housing 28 ground 3 hydraulic housing 29 flange 4 housing cover 30 drilling 5 Bearing bracket lantern 31 screw 6 bearing bracket 32 Kalottenbereich 7 bearing cap 33 flanged area 8th inlet port 34 carrying disc 9 outlet 35 survey 10 containment shell 36 Fluid inlet area 11 inner space 37 shovel 12 chamber 38 Channel leading edge 13 impeller shaft 39 impeller channel 13a shaft section 40 Outer casing surface 13b shaft section 41 channel base 14 flow chamber 42 step 15 opening 43 mounting hole 16 Wheel 44 threaded hole 17 inner rotor 45 recess 18 magnet 46 Through opening 19 screw 47 Bearing ring carrier 20 auxiliary impeller 48 Through opening 21 bearing arrangement 49 flange-like area 22 drive shaft 50 interior 23 ball-bearing 51 radial bore 24 ball-bearing 52 axial 25 magnet 53 radial bore 26 outer rotor 54 Through opening 55 Through opening 56 impeller channel 57 channel base 58 fluid channel 59 fluid channel A axis of rotation

Claims (12)

1. Pump arrangement, in particular magnetic clutch pump arrangement, having an interior space (11) formed by a pump casing (2) of the pump arrangement, having a containment can (10) which has a base (28) and which hermetically seals off a chamber surrounded by said containment can with respect to the interior space formed by the pump casing, having an impeller shaft (13) which can be driven in rotation about an axis of rotation, having an impeller (16) which is arranged on one end of the impeller shaft, having an inner rotor (17) arranged on the other end of the impeller shaft, having an auxiliary impeller (20) arranged in the chamber, and having an outer rotor (26) which interacts with the inner rotor,
   characterized in that
   the auxiliary impeller (20) is of semi-open construction and is fastened by way of its open side to that face side of the inner rotor (17) which faces toward the base (28) of the containment can (10).
2. Pump arrangement according to Claim 1, characterized in that the containment can (10) has a main body (27) with an open side and with a side which is situated opposite the open side and which is closed by way of a domed base (28), and the auxiliary impeller (20) has a rear shroud (34), whose outer surface facing toward the base (28) of the containment can (10) has a domed form.
3. Pump arrangement according to Claim 2, characterized in that the domed form of the outer surface of the rear shroud (34) substantially corresponds to the domed form of the base (28) of the containment can (10).
4. Pump arrangement according to one of Claims 2 to 3, characterized in that a paraboloid-like elevation (35) is provided in the center of the rear shroud (34).
5. Pump arrangement according to one of Claims 2 to 4, characterized in that, on the rear shroud (34), at a radial distance from the elevation (35), there are formed multiple raised portions which form vanes (37) and corresponding impeller channels (39) of the auxiliary impeller (20).
6. Pump arrangement according to Claim 5, characterized in that the impeller channels (39) have a channel base (41) which is similar in form to a rampant three-center arch.
7. Pump arrangement according to one of Claims 2 to 6, characterized in that the upper side, which is averted from the rear shroud (34), of the vanes (37) has a step (42) close to the channel inlet edge (38).
8. Pump arrangement according to one of Claims 2 to 7, characterized in that the impeller shaft (13) and the inner rotor (17) form a cover shroud, situated opposite the rear shroud (34), of the auxiliary impeller (20).
9. Pump arrangement according to one of Claims 5 and 6, characterized in that, in the raised portions which form the vanes (37), there are formed further impeller channels (56) which extend in a radial direction from the outer lateral surface (40) as far as a point close to the step (42).
10. Pump arrangement according to Claim 9, characterized in that the further impeller channels (56) have a channel base (57) which, at least in part, has a domed form which corresponds substantially to the domed form of the outer surface of the rear shroud (34).
11. Pump arrangement according to one of Claims 1 to 10, characterized in that the impeller shaft (13) has an axial channel (52) which is connected to the fluid inlet region (36) of the auxiliary impeller (20).
12. Pump arrangement according to one of Claims 1 to 11, characterized in that, in the inner rotor (17), there are provided fluid channels (59) which issue into the further impeller channels (56) of the auxiliary impeller (20).

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