EP2994642A1 - Pump arrangement - Google Patents

Abstract

The invention relates to a pump arrangement, more particularly a magnetic clutch pump arrangement, comprising an inner chamber (11) formed by a pump housing (2) in the pump arrangement (1); a containment shell (10) which hermetically seals an enclosed chamber (12) with respect to the inner chamber (11) formed by the pump housing; an impeller shaft (13) that can be driven in rotation about an axis of rotation (A); an impeller (16) mounted on one end of the impeller shaft (13); an inner rotor (17) mounted on the other end of the impeller shaft (13); an auxiliary impeller (20) mounted in the chamber (12); and an outer rotor (26) which co-operates with the inner rotor (17). According to the invention the auxiliary impeller (20) is secured to the inner rotor (17).

Description

 description

pump assembly

The invention relates to a pump arrangement, in particular magnetic coupling pump arrangement, with an interior formed by a pump housing of the pump assembly, a containment shell which hermetically seals a chamber enclosed by it against the interior formed by the pump housing, an impeller shaft rotatably driven about an axis of rotation, one at one end Impeller shaft arranged impeller, arranged at the other end of the impeller shaft inner rotor, arranged in the chamber auxiliary impeller and cooperating with the inner rotor Außenroior. From DE 27 54 840 A1 such a magnetic coupling pump assembly with Hilfsiaufrad 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 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 is fixed to 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 plate substantially corresponds to the curvature of the bottom of the split pot, 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 disc with a radial distance to the survey, which form blades and corresponding Laufradkanäie 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. has. 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 further impeller channels of the auxiliary impeller.

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

1 shows a longitudinal section through an agnetkupplungspumpenanordnung with an auxiliary impeller according to the invention, the

Fig. 2 shows the longitudinal section through the magnetic coupling pump assembly of FIG. 1 in a relation to FIG. 1 by 90 ⁰ rotated plane, the Fig. 3 is a FIG. 1 corresponding auxiliary wheel in an enlarged view, the

Fig. 4 is a detailed three-dimensional representation of the auxiliary wheel of FIG. 3, the

Fig. 5 is a detailed three-dimensional representation of another embodiment of the auxiliary impeller according to the invention, the

Fig. 6 shows the longitudinal section through a magnetic coupling pump assembly with an auxiliary impeller according to the invention according to FIG. 5, the

7 shows the longitudinal section through a magnetic coupling pump arrangement according to FIG.

 6 with a respect to FIG. 6 rotated by 45 ° inner rotor and FIG. 8 shows the longitudinal section through the magnetic coupling pump assembly of FIG. 6 in a relation to FIG. 6 rotated by 90 ° plane.

FIGS. 1 and 2 show a pump arrangement 1 in the form of a magnetic coupling pump arrangement. 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 pumped medium and an outlet opening 9 for ejecting the pumped 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 Lagerträgeriaterne 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 containment shell 10 is attached to the side facing away from the hydraulic housing 3 of the housing cover 4 and extends at least partially through a limited by the pump housing 2, in particular the Gehäusedeckei 4, the bearing support lantern 5 and the bearing support 6 inner space 11. The containment shell 10 seals one of hermetically sealed to him and the housing cover 4 chamber 12 from the interior 1 from.

A rotatable about an axis of rotation A impeller shaft 3 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, and 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 8, 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 3 rotatably driven about the rotation axis A is arranged.

An unillustrated drive motor, preferably an electric motor, drives a drive roller 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 outer ring-carrying rotor 26 is arranged. The magnets 25 are arranged on the side of the outer rotor 26 facing the gap pot 0. 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 split pot 0 shown enlarged in FIG. 3 has a substantially cylindrical base 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 by 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 crevice pot 10 is formed by a substantially spherical portion-shaped dome region 32 and an outer rim region 33 which forms the transition region between the base body 27 and the dome region 32.

As can be seen from Figs. 3 and 4, 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, which form blades 37 with a channel inlet edge 38 facing the elevation 35 and corresponding impeller channels 39 of the auxiliary rotor 20, are formed on the carrier disk 34 at a radial distance from the elevation 35. 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 exemplary embodiment shown, the blades 37 extend in a curved manner from the fluid inlet region 36 to an outer jacket surface 40 of the auxiliary rotor wheel. The rotor 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 carrier disk 34. The channel bottom 41 the impeller channels 39 is formed in the longitudinal section shown similar to a einhüftigen basket bow, as shown in the Fig. 6. 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 equal to 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 are 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 shown in FIG. 2, at least one through-openings 46 and at least one radial passage opening 48 are provided in the housing cover 4 and in a bearing ring carrier 47 which fixes the bearing arrangement 21. The passage 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. By- Gear 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 arrangement 21, pumped medium can be withdrawn from the flow chamber 14 and fed to the bearing arrangement 21 via the passage openings 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 path 13 surrounded by the bearing arrangement 21 to the end of the impeller shaft 13 located within the chamber 12 and thus to the end Auxiliary wheel 20 extends. If necessary, at least one further radial bore 53 is formed, which likewise communicates with the axial passage 52 formed in the impeller shaft 13. The auxiliary impeller 20 conveys the medium used for cooling and lubrication radially outward into the chamber 12, from where it via several shown in Fig. 1 in the fianschartigen area 49 through holes 54 and formed in the housing cover 4 through holes 55 back into the Flow chamber 14 is promoted.

FIGS. 5 to 8 show a further embodiment of the invention. The auxiliary impeller 20 shown in detail in FIG. 5 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 is greater than the first width W1 or at least equal to the first width W1.

In the elevations forming the blades 37, further impeller channels 56 are formed, which also extend substantially straight, ie without or without significant curvature, from the outer circumferential surface 40 to near the step 42 in the radial direction and have a channel bottom 57 which 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 channels 56 is formed in a longitudinal section similar to a einhüftigen basket bow, as shown in Fig. 7. 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 entry portion 56a and a second width W4 at the outer contact surface 40, the second width W4 being greater than the first width W3 or at least the first width W3 corresponds.

FIGS. 6 to 8 show a pump arrangement 1, which is equipped with an auxiliary impeller 20 shown in FIG. 5. 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. As can be seen from FIG. 6, the at least one radial bore 53 leads into one in comparison to FIG In addition, the bearing ring carrier 47 has parallel to the rotation axis A extending fluid channels 58 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.

FIG. 7 shows the pump arrangement 1 shown in FIG. 6 with an inner rotor 17 turned through 45 ° about the rotation axis A. In the inner rotor 17, fluid channels 59 are provided, which are arranged approximately at the same radial distance from the axis of rotation A. how the fluid channels 58 of the bearing ring carrier 47 and thus, at least in the position shown, are substantially in alignment with them. The fluid channels 59 open into the impeller channels 56 of the auxiliary rotor 20 arranged on the end face of the inner rotor 17 facing the bottom 28 of the split pot 10.

For cooling and lubrication of the bearing assembly 21 is removed from the flow chamber 14 conveying medium and, as shown in Fig. 8, on the at least one passage opening 46 in the housing cover 4 and the at least one passage opening 48 in the flange portion 49 of the bearing ring carrier 47 of the bearing assembly 21 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 Hilfsiaufrad 20th promoted. The auxiliary impeller 20 conveys the medium used for cooling and lubrication mitteis the impeller channels 39 radially outward into the chamber 12th

At the same time, according to FIG. 7, the delivery medium taken from the flow chamber 4 is conveyed from the inner region 50 of the bearing ring carrier 47 into the impeller channels 56 of the hoisting wheel 20 via the fluid channels 59 formed in the inner rotor 17 and radially outward into the chamber 12.

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

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.

Bezugszeicheniiste

1 pump assembly 27 main body

 2 pump housing 28 bottom

 3 Hydraulic housing 29 Connecting flange

4 housing cover 30 bore

 5 bearing bracket lantern 31 screw

 6 bearing brackets 32 calotte area

7 Bearing cover 33 Brim area

8 inlet opening 34 bearing plate

 9 Ausiassöffnung 35 Survey

 10 split pot 36 fluid inlet area

11 interior 37 scoop

 12 chamber 38 channel entry edge

13 impeller shaft 39 impeller channel

13a shaft portion 40 outer circumferential surface

13b shaft portion 41 channel bottom

 14 flow chamber 42 stage

 15 opening 43 mounting hole

 16 impeller 44 threaded hole

17 inner rotor 45 recess

 18 magnet 46 through hole

19 screw 47 bearing ring carrier

20 auxiliary wheel 48 passage opening

21 Bearing arrangement 49 Flange-type area

22 Driving Inside 50 Interior

 23 ball bearings 51 radial bore

24 ball bearings 52 axial channel

 25 Magnet 53 Radial bore

26 outer rotor 54 through hole Through hole Impeller channel Channel bottom F uid channel

Fluid channel rotation axis

Claims

Claims Pump arrangement 1. Pump arrangement, in particular magnetic coupling pump arrangement, with a housing formed by a pump housing of the pump assembly, a containment shell hermetically seals a chamber enclosed by him against the inner space formed by the pump housing, a rotatably driven about an axis of rotation impeller shaft, one arranged at one end of the impeller shaft Impeller, arranged at the other end of the Laufradwe! Le inner rotor, arranged in the chamber Hilfslaufrad and with the [nnenrotor cooperating outer rotor, characterized in that the Hilfslaufrad (20) on the inner rotor (17) is attached. 2. Pump arrangement according to claim 1, characterized in that the containment shell (10) has a base body (27) with an open side and an open side opposite by means of a curved bottom (28) closed side and the auxiliary impeller (20) has a support disc (34), the bottom (28) of the gap pot (0) facing outer surface has a curvature. 3. Pump arrangement according to claim 2, characterized in that the curvature of the outer surface of the support disc (34) substantially corresponds to the curvature of the bottom (28) of the gap pot (10). 4. Pump arrangement according to one of claims 2 to 3, characterized in that in the center of the support disc (34) is provided a paraboloid-like elevation (35). 5. Pump arrangement according to one of claims 2 to 4, characterized in that on the support disc (34) at a radial distance from the elevation (35) a plurality of elevations are formed, which blades (37) and corresponding Laufradkanäle (39) of the auxiliary wheel ( 20) form. 6. Pump arrangement according to claim 5, characterized in that the impeller channels (39) have a channel bottom (41), which is similar to a einhüftigen basket bow. 7. Pump arrangement according to one of claims 2 to 6, characterized in that the support disc (34) facing away from the top of the blades (37) near the Kanaieintrittskante (38) has a step (42). 8. Pump arrangement according to one of claims 2 to 7, characterized in that the impeller shaft (13) and the inner rotor (17) form one of the support disc (34) opposite cover plate of the auxiliary rotor (20). 9. Pump arrangement according to one of claims 5 to 8, characterized in that in the blades (37) forming increases further impeller passages (56) are formed, extending in the radial direction from the outer circumferential surface (40) to near the stage (42 ). 10. Pump arrangement according to claim 9, characterized in that the further impeller channels (56) have a Kanaigrund (57), at least partially a Has buckle, which corresponds substantially to the curvature of the outer surface of the support plate (34). 11. Pump arrangement according to one of claims 1 to 10, characterized in that the impeller shaft (13) has an axial passage (52) which communicates with the fluid inlet region (36) of the auxiliary impeller (20) in connection. Pump arrangement according to one of claims 1 to 11, characterized in that in the inner rotor (17) fluid channels (59) are provided, which in the further run wheel channels (56) of the auxiliary wheel (20) open.