EP3575606A1 - Centrifugal pump - Google Patents

Abstract

In the case of a centrifugal pump (100) with a support structure (1) which has a wall (12) with a distal end extending from the wall (12) over a length (l1) and pointing away from the wall (12) (10) and a pump bearing bracket (11) having an outer surface (16), with a drive shaft (8) protruding axially from the distal end (10) of the pump bearing bracket (11), and with a pump drive pulley (18) connected to the drive shaft (8) , a hollow shaft (17) is provided which is arranged coaxially to the drive shaft (8) and extends from the distal end (10) over at least part of the pump bearing bracket (11) and with the drive shaft (8) in which from the distal end (10) protruding area is connected, and the pump drive pulley (18) is connected to the hollow shaft (17).

Description

The invention relates to a centrifugal pump, comprising a support structure having a wall, with a forterstreckenden from the wall over a length, a distal end facing away from the wall and an outer surface having pump bearing support, with an axially projecting from the distal end of the pump bearing support drive shaft and with a drive shaft rotatably connected to the pump drive pulley.

Such a centrifugal pump is known from the WERNERT pump GmbH under the name NE 100-65-250. This pump is a so-called chemical standard pump, which is designed as a centrifugal pump. In this, the pumping medium is sucked axially through an inlet connected to the drive shaft through an inlet and conveyed out by centrifugal forces from a radial outlet. To drive this centrifugal pump is a drive motor comprising a motor shaft having a motor drive pulley. The motor shaft is aligned parallel to the drive shaft and extends away from the distal end of the pump bearing carrier. It is based on a footprint of the pump higher than the drive shaft arranged. To transmit the motor shaft rotation to the drive shaft is a traction means, such as a toothed belt, a V-belt or a chain, which is in operative connection with the motor drive pulley and the pump drive pulley. The traction device can easily be changed, if necessary after reducing the tension under which it is placed during operation.

Due to the pointing away from the distal end of the pump bearing carrier alignment of the motor shaft and the arrangement of the drive motor - viewed from the inlet of the pump housing - behind the centrifugal pump, this centrifugal pump and the drive motor having pump unit has a length equal to about the sum of the lengths of the centrifugal pump and of the drive motor corresponds.

In practice, there is often a desire to reduce the length of the pump set due to the space available for the placement of a pump set. Due to the radial outlet, reverse assembly of the drive motor, which is located above the pump, is usually out of the question because it would collide with parts of the pump housing or with components connected to the outlet.

From the EP 718 530 A1 is a centrifugal pump of the type mentioned above, which is designed as an axial pump. In this case, the liquid is sucked in axially by means of a pump propeller connected to the drive shaft and displaced in the pump housing in an axial flow. The pump housing is approximately tubular arc-shaped such that the liquid emerges approximately transversely to the suction direction. Due to the shape of the housing, these axial pumps are also called "pipe bend pumps".

To drive out of the EP 718 530 A1 known axial pump in turn serves a drive motor which is arranged such that its motor shaft is parallel to the drive shaft. It comprises a motor drive pulley and is connected by means of a traction means with the pump drive pulley in operative connection. However, this drive motor - viewed from the inlet side of the pump housing - not arranged behind the pump housing, but laterally next to or below, so that this pump unit in the axial direction has a shorter length, however, to a significant increase in the width or the need to provide an excavation in the foundation, leads. Although the traction device can again be easily changed. However, that is Increasing the width due to the limited space that is regularly available for the installation of a pump set, undesirable.

The invention is therefore an object of the invention to provide a centrifugal pump, which allows use in a pump unit, which has a smaller footprint and nevertheless a change of the traction means is at least not significantly more difficult.

This object is achieved by the reproduced in claim 1 centrifugal pump and by the reproduced in claim 13 centrifugal pump unit.

In the centrifugal pump according to the invention, a coaxial with the drive shaft arranged hollow shaft is provided which extends from the distal end of the pump bearing support over at least a portion of the pump bearing support and is rotatably connected to the drive shaft in the protruding from the distal end region. The pump drive pulley is rotatably connected to the hollow shaft. Due to this design, the pump drive pulley and thus also the drive motor can be arranged with a smaller distance to the pump housing. In particular, an arrangement of the drive motor above the pump bearing carrier is possible in such a way that the drive motor at least partially covers the pump bearing carrier. The length of a pump unit thus formed with a centrifugal pump according to the invention is thus reduced by about the length of the overlap of drive motor and pump bearing carrier without the change of the traction device would be difficult. It can also - if necessary after reducing its voltage - first removed from the motor drive pulley and then removed by displacement along the pump bearing housing. An assembly of the traction means can be reversed accordingly.

It is also essential that a reduction in the installation space is made possible without the length of the pump bearing support would have to be reduced. It may even be possible to increase the length of the pump bearing carrier, without thereby increasing the overall length of a pump unit according to the invention comprising the centrifugal pump. This is true if the distal end of a Pump bearing carrier, the motor drive disc opposite end face of the drive motor does not exceed.

Due to an extended pump bearing carrier and the distance between the radial bearing for the drive shaft can be increased. Such an enlargement is regularly desirable in centrifugal pumps, since the region of the drive shaft, which protrudes from the pump bearing carrier in the pump housing, also referred to as "Wellenauskragung", is not regularly stored and reduce due to the increase in the bearing clearance, the forces acting radially on the bearings to let.

In principle, it is possible to make the drive shaft - as with centrifugal pumps belonging to the prior art - only with the aid of two pivot bearings, for example roller bearings, arranged inside the pump bearing carrier and spaced apart in the axial direction. This training requires a particularly stable design of the hollow shaft and in particular their connection to the protruding from the distal end of the pump bearing support portion of the drive shaft in order to transmit via the pump drive pulley introduced forces and moments can.

A first preferred embodiment of the invention therefore provides for the storage of the drive shaft and the hollow shaft at least one inner, the drive shaft receiving Innenradiallager and axially spaced from the Innenradiallager at least a first outer, the hollow shaft on the outer surface of the pump bearing support abstützendes provided Außenradiallager. In this case, the inner radial bearing is preferably arranged as far as possible from the distal end of the pump bearing carrier, the outer radial bearing preferably as closely as possible adjacent to the distal end of the pump bearing support, so as to achieve the largest possible bearing distance in the axial direction.

1. 1. Das Außenradiallager ist radial größer als ein an entsprechender axialer Position angeordnetes Innenradiallager, so dass es bereits aus diesem Grund zur Aufnahme höherer Kräfte geeignet ist.
2. 2. Die Kühlung des Außenradiallagers erfolgt unter anderem durch die rotierende (regelmäßig aus einem metallischen, gut Wärme leitenden Werkstoff gefertigten) Hohlwelle, die über bewegte Konvektion Wärme an die Außenluft abgeben kann. Im Gegensatz hierzu kann bei der zum Stand der Technik gehörenden Lageranordnung Wärme der Lager nur über eine unbewegte Konvektion an den Pumpenlagerträger, der zumeist aus einem dickwandigen Gusskörper gefertigt ist, abgegeben werden.

The provision of an outer radial bearing which supports the hollow shaft on the outer surface of the pump bearing carrier also has the further advantages over the bearing arrangement according to the prior art:

1. 1. The outer radial bearing is radially larger than a arranged at a corresponding axial position Innenradiallager, so that it is already suitable for this reason to absorb higher forces.
2. 2. The cooling of the outer radial bearing takes place inter alia by the rotating (made of a metallic, good heat conductive material) hollow shaft, which can deliver heat to the outside air via convection. In contrast, in the bearing arrangement according to the prior art, heat of the bearing can only be dissipated via a stationary convection to the pump bearing carrier, which is usually made of a thick-walled cast body.

In a particularly preferred, second embodiment, a second Außenradiallager is provided to increase the load capacity of the bearing assembly, which supports the hollow shaft on the outer surface of the pump bearing support axially spaced from the first.

It is particularly preferred if the first outer radial bearing near the distal end and the second outer radial bearing are provided near the drive pulley. In this way, the introduction of a high bending moment in the hollow shaft and in the drive shaft due to driving forces is effectively reduced. Also, the hollow shaft can be formed thin-walled compared to the embodiment described above with only a single Außenradiallager, thereby improving the heat dissipation caused by the hollow shaft of the Außenradiallagern and reduce material costs.

In principle, the drive shaft, the hollow shaft and the pump drive pulley can be integrally formed. However, in order to facilitate both the manufacturability as well as the assemblability of these components, it is preferable to provide a plurality of components which can be joined together to form an assembly comprising the drive shaft, the hollow shaft and the pump drive pulley.

In particular, it is preferable to form at least the pump drive disk as a separate component that can be fastened to the hollow shaft and is particularly preferably interchangeable. Not just an exchange of the pump drive pulley upon reaching a wear limit is then possible, but if necessary, can be changed by changing the pump drive disc relative to one with a different diameter, the speed of the drive shaft during operation without changing the speed of a drive motor, which may be desirable to adapt the centrifugal pump to different operating conditions.

It is also preferable to provide the assembly of drive shaft and hollow shaft of two separate and joinable components in order to facilitate the manufacturability and assembly. In a first, preferred embodiment, a region of the hollow shaft which encloses the first outer radial bearing is fixedly connected to the drive shaft so that both this region of the hollow shaft and the drive shaft are also supported and centered in the state not connected to the further part of the hollow shaft ,

In a second preferred embodiment, the one component comprises the drive shaft and the second component comprises the hollow shaft with a reaching over the distal end of the pump bearing carrier and the connection with the drive shaft causing region. Although in this embodiment, the mountability is facilitated. However, there is a joint between the bearings, which may eventually lead to a bad alignment of the bearings.

In a centrifugal pump according to the invention comprises - preferably - the drive shaft has a first length range a, which is determined by the center distance of the maximum axial distance exhibiting inner and outer radial bearing, and a second length range b, by a bearing-free length over which the drive shaft in the pump housing protrudes, is determined.

If the centrifugal pump according to the invention is an axial pump or a centrifugal pump whose drive shaft extends approximately vertically (vertical pump), it has surprisingly been found that this centrifugal pump has a particularly high stability relative to the production costs, if for the dependencies of the first and second Length ranges a, b apply: $$\mathrm{0}.\mathrm{6}<\mathrm{b}/\left(\mathrm{a}+\mathrm{b}\right)<\mathrm{0}.\mathrm{8th}$$

If the centrifugal pump according to the invention is a centrifugal pump, it has surprisingly been found that the following applies to the first and second length ranges a, b: $$\mathrm{0}.\mathrm{45}<\mathrm{b}/\left(\mathrm{a}+\mathrm{b}\right)<\mathrm{0}.\mathrm{65}$$

The invention also includes a centrifugal pump assembly with a centrifugal pump according to the invention, which comprises a drive motor which comprises a motor shaft having a motor drive pulley and which is arranged such that the motor shaft runs parallel to the drive shaft. Furthermore, this centrifugal pump unit comprises a traction means, which is in operative connection with the motor drive pulley and the pump drive pulley.

In a particularly preferred embodiment of this centrifugal pump assembly, a dimensionally stable intermediate housing is provided on the side of the support structure from which the pump bearing support extends. Under "dimensionally stable" is to be understood that the intermediate housing can absorb all at least substantially torsion by the weight of the drive motor and by acting due to the transmission of the drive torque from the motor drive shaft to the pump drive shaft to the intermediate housing forces. Due to this measure, the drive motor can be fastened exclusively to the intermediate housing, as a result of which this pump unit is particularly compact and requires no further components whose production costs increase to support the drive motor.

If - as particularly preferred - the intermediate housing is designed such that it at least partially surrounds the motor drive pulley, the pump drive pulley and the traction means, it serves at least partially as protection against contact and as protection against the ingress of contaminants, so that the with such - im Operation of the pump set required - Protective devices can reduce the associated effort.

Fig. 1

ein Kreiselpumpenaggregat mit einem ersten Ausführungsbeispiel einer erfindungsgemäßen Kreiselpumpe, die als Axialpumpe ausgebildet ist, teilweise im Längsschnitt;

Fig. 2

ein Kreiselpumpenaggregat mit einem zweiten Ausführungsbeispiel einer erfindungsgemäßen Kreiselpumpe, die als Zentrifugalpumpe ausgebildet ist, teilweise im Längsschnitt;

Fig. 3

ein Kreiselpumpenaggregat mit einem dritten Ausführungsbeispiel einer erfindungsgemäßen Kreiselpumpe, die als vertikale Zentrifugalpumpe ausgebildet ist, in einer Aufsicht;

Fig. 4

dasselbe Ausführungsbeispiel im Schnitt gemäß Schnittlinie A-A in Fig. 3;

Fig. 5

die Antriebswelle des ersten Ausführungsbeispiels der erfindungsgemäßen Kreiselpumpe in einer Einzeldarstellung;

Fig. 6

die Antriebswelle des zweiten Ausführungsbeispiels der erfindungsgemäßen Kreiselpumpe in einer Einzeldarstellung;

Fig. 7

- rein schematisch - eine bevorzugte Variante einer Ausgestaltung der Lagerung einer die Antriebswelle, eine Hohlwelle und eine Pumpenantriebsscheibe umfassenden Baugruppe sowie deren Kopplung mit einem Antriebsmotor einer erfindungsgemäßen Kreiselpumpe;

Fig. 8

eine weitere bevorzugte Variante dieser Baugruppe in einer Fig. 7 entsprechenden Darstellung;

Fig. 9

eine weitere bevorzugte Variante dieser Baugruppe in einer Fig. 8 entsprechenden Darstellung sowie

Fig. 10

eine weitere bevorzugte Variante dieser Baugruppe in einer Fig. 8 entsprechenden Darstellung.

In the drawings, embodiments of the invention - in part purely schematically - shown. Show it:

Fig. 1

a centrifugal pump assembly with a first embodiment of a centrifugal pump according to the invention, which is designed as an axial pump, partially in longitudinal section;

Fig. 2

a centrifugal pump assembly with a second embodiment of a centrifugal pump according to the invention, which is designed as a centrifugal pump, partially in longitudinal section;

Fig. 3

a centrifugal pump assembly with a third embodiment of a centrifugal pump according to the invention, which is designed as a vertical centrifugal pump, in a plan view;

Fig. 4

the same embodiment in section along section line AA in Fig. 3 ;

Fig. 5

the drive shaft of the first embodiment of the centrifugal pump according to the invention in a single representation;

Fig. 6

the drive shaft of the second embodiment of the centrifugal pump according to the invention in a single representation;

Fig. 7

purely schematically - a preferred variant of an embodiment of the storage of a drive shaft, a hollow shaft and a pump drive pulley comprehensive assembly and their coupling with a drive motor of a centrifugal pump according to the invention;

Fig. 8

Another preferred variant of this assembly in one Fig. 7 corresponding representation;

Fig. 9

Another preferred variant of this assembly in one Fig. 8 corresponding representation as well

Fig. 10

Another preferred variant of this assembly in one Fig. 8 corresponding representation.

The first, in Fig. 1 as a whole with 100 designated embodiment of a centrifugal pump according to the invention is designed as an axial pump. This axial pump comprises a support structure 1, which are arranged on a pump housing 1A and a pipe bend housing 1B flanged thereto with approximately the shape of a 90 ° tubular bend. Such a centrifugal pump is therefore also called "pipe bend pump". The pipe bend housing 1B has an inlet flange 2, which surrounds an inlet 3, and an outlet flange 4, which surrounds an outlet 5. The pipe bend housing 1B is arranged such that the inlet flange 2 lies approximately in a vertical plane, the outlet flange 4 approximately in a horizontal plane.

To the inlet flange 2, the pump housing 1A is flanged in the form of a pump propeller housing 6, in which a pump propeller 7 is housed. It is rotatably mounted on a drive shaft 8, which extends approximately horizontally from the pump propeller 7 through a drive shaft tunnel 9 of the pipe bend housing 1B and on to the pump housing 1A remote, distal end 10 of a pump bearing support 11 having a length l1. In the illustrated embodiment, the pump bearing support 11 is mounted on a vertical to the drive shaft 8 wall 12 of the support structure 1, to which also the outlet flange 4 of the pipe bend housing 1B is attached.

Between the drive shaft tunnel 9 and the pump bearing support 11, a sealing arrangement 13 is provided which prevents leakage of medium to be pumped from the drive shaft tunnel 9.

The parts of the pump housing 1A of the pipe bend housing 1B and the drive shaft tunnel 9 which come into contact with the medium to be pumped are coated with a layer 14 which is resistant to aggressive media, so that this centrifugal pump 100 can also be used, for example, in chemical plants.

The drive shaft 8 protrudes from the distal end 10 of the pump bearing carrier 11 and is here provided with a radial extension 15 whose outer circumference is greater than the outer diameter of the pump bearing carrier 11 and the thus over the outer surface 16 of the same. The outer surface 16 is formed by a separately formed sleeve 11 A of the pump bearing carrier 11.

With the radial extension 15, a hollow shaft 17 is rotatably connected, which extends along the pump bearing support 11 coaxial with the drive shaft 8.

With the help of the hollow shaft 17 thus the drive shaft 8 can be set in rotation. For this purpose, in the region of the wall 12 facing the end of the hollow shaft 17, a pump drive pulley 18 is attached, which is formed in the illustrated embodiment as a pulley, concretely as a multi-V belt pulley. In the centrifugal pump assembly 400 comprising the centrifugal pump 100, the multiple-belt pulley cooperates with a traction means 19, which correspondingly comprises a plurality of juxtaposed V-belts in the illustrated embodiment. The traction means 19 rotates in the illustrated embodiment, in turn, designed as a multi-V-belt pulley motor drive pulley 20, which is mounted on a motor drive shaft 21 of a drive motor 22, here an electric motor. It is understood that all constructive variants that enable a rotary coupling of the drive pulleys can be used as traction means and drive pulleys. Examples include chains and toothed or ribbed belts and adapted thereto drive pulleys.

The drive shaft 8 is mounted in the centrifugal pump 100 exclusively by means of the pump bearing support 11 in a first length range a. For this purpose, an inner, the drive shaft receiving Innenradiallager 23, which is disposed in the vicinity of the wall 12 facing the end of the pump bearing support 11, a first outer spaced from the Innenradiallager 23, the hollow shaft 17 on the outer surface 16 of the pump bearing support in the region of the distal End supporting outer radial bearing 24 and a second outer, the hollow shaft 17 on the outer surface 16 of the pump bearing support 11 in the area of the pump drive pulley 18 supporting outer radial bearing 25 is provided. The inner radial bearing 23 is designed as a cylindrical roller bearing, the first outer radial bearing 24 as a single ball bearing and the second outer radial bearing as a double ball bearing.

Between the Innenradiallager 23 and the pump propeller 7 no further storage of the pump shaft 8 is provided. Accordingly, this length is also referred to as a bearing-free length region b or wave projection.

In the first embodiment 100, the code number b / (a + b) of the two length ranges is 0.7 (see FIG Fig. 5 ).

At the in Fig. 1 illustrated embodiment of the centrifugal pump assembly 400, the wall 12 is part of a dimensionally stable intermediate housing 26. This includes another, parallel to the wall 12 wall 27 which includes a motor receiving flange 27A, to which the drive motor 22 is flanged. The walls 12 and 27 are interconnected via transverse connecting walls, not shown in the drawing, so that the intermediate housing has a box-like shape. Due to the dimensionally stable design of the intermediate housing 26 further components for attachment of the drive motor 22 are not needed. The pump drive pulley 18, the motor drive pulley 20 and the traction means 19 are located substantially within the intermediate housing 26, so that already by this a substantial part of the required personal protection is provided.

In practice, an in Fig. 1 Not shown protection against contact be provided, which prevents people during operation with rotating components can come into contact.

This in Fig. 1 illustrated centrifugal pump assembly 400 is characterized by the particular configuration of the centrifugal pump 100 by a particularly compact, in particular short design while maintaining a large axial distance of the inner radial bearing 23 and the first outer radial bearing 24. In addition, it is apparent that nevertheless the traction means - after the necessary relaxation - disassembled and can be mounted accordingly, without the need for complex construction measures.

The second embodiment 200 of a centrifugal pump according to the invention, which in the in Fig. 2 Centrifugal pump 400 is used, differs only in terms of the operation of the centrifugal pump of the first embodiment 100. This is formed in the second embodiment as a centrifugal pump. For the sake of avoiding repetitions, only the differences between the second exemplary embodiment 200 and the first exemplary embodiment 100 will be discussed below. With the first embodiment, functionally matching components are provided with the same reference numerals as in the first embodiment.

In the second embodiment 200 of the centrifugal pump according to the invention, a pump housing 201B surrounded by a ring housing 201A is arranged on the support structure 1. The ring housing is made of metal, the pump housing made of plastic. The pump housing 201B has an axially directed inlet 203 and a radially upwardly directed outlet 205. Within the pump housing 201B is an impeller 206 driven by means of the approximately horizontally oriented drive shaft 8, by means of which the liquid to be pumped is sucked through the inlet 203 and conveyed out of the outlet 205 under the effect of centrifugal force.

The code number b / (a + b) of the two length ranges in the second embodiment is 0.53 (see Fig. 6 ).

Incidentally, the basic structure of the second embodiment 200 of the centrifugal pump according to the invention corresponds in principle to that of the embodiment 100, so that reference is made to the description thereof in this regard.

The third embodiment 300 of a centrifugal pump according to the invention, which in which in Fig. 3 and 4 As shown, centrifugal pump assembly 400 is used, as well as the second embodiment 200 is formed as a centrifugal pump. For the sake of avoiding repetitions, only the differences between the third embodiment 300 and the second embodiment 200 will be discussed below. Functionally matching components with the first and second embodiments are provided with the same reference numerals in the first and second embodiments.

In the third embodiment 300 of the centrifugal pump according to the invention are on the support structure 1 in turn surrounded by a ring housing 301 A pump housing 301 B, within which there is a driven by means of the drive shaft 8 impeller 306 is located. The drive shaft 8 is in contrast to the first and second embodiments, not approximately horizontally, but approximately vertically aligned. Accordingly, pumps of the type of the third embodiment 300 are also referred to as vertical pumps.

The pump housing 301B has a downwardly directed inlet 303, through which the liquid to be pumped is sucked through an inlet filter upstream of the inlet in the pumping direction and conveyed out from a radially outwardly directed outlet 305 under the action of centrifugal force. Downstream of the outlet 305 in the pumping direction is a 90 ° bend 307, to which in turn a riser pipe 308 is flanged, through which the liquid to be pumped is conveyed upwards. Incidentally, the basic structure of the third embodiment 300 of the centrifugal pump according to the invention in principle corresponds to that of the second embodiment 200, wherein the third embodiment 300 is distinguished due to the inventive design by a comparison with the prior art reduced height.

The code number b / (a + b) of the two length ranges is 0.7 in the third embodiment.

At the in Fig. 7 purely schematically illustrated first preferred variant of an embodiment and storage of the drive shaft 8, the hollow shaft 17 and the pump drive pulley 18 comprehensive assembly 32, the drive shaft 8 and the hollow shaft 17 are integrally formed. The pump drive pulley 18 is removably mounted on the hollow shaft. For storage, only the Innenradiallager 23 and the first outer radial bearing 24 are provided.

At the in Fig. 8 illustrated, further preferred variant, the second outer radial bearing 25 is further provided, which additionally supports the hollow shaft 17 in the pump drive pulley 18 on the pump bearing carrier 11, so that the forces to be absorbed by the hollow shaft 17 are reduced and these can be formed thin-walled.

At the in Fig. 9 illustrated, another preferred variant, the inner radial bearing 23 and the first and the second outer radial bearing 24, 25 are provided. In that regard, this variant corresponds to in Fig. 8 shown. However, the entirety 33 of drive shaft and hollow shaft of two separate and joinable components 28, 29 is provided. The first part 28 is fixedly connected to the drive shaft 8 and comprises a portion 30 of the hollow shaft 17, which encloses the first outer Außenradiallager.

At the in Fig. 10 illustrated, a further preferred variant comprises a part 28, the drive shaft 8 and the second part 29, the hollow shaft 17 with the area 30, which then serves the connection with the drive shaft 8 in the projecting beyond the distal end of the pump bearing support 11 end.

In the FIGS. 7 to 10 In each case, a contact protection 31 is shown which protects persons from coming into contact with rotating components located outside the pump bearing carrier 11.

In the Fig. 7 to 10 Variants shown can alternatively be used in embodiments 100, 200 and 300.

Bezuaszeichenliste:

100

Embodiment centrifugal pump

200

Embodiment centrifugal pump

300

Embodiment centrifugal pump

400

A centrifugal pump unit

1

supporting structure

1A

pump housing

1B

Elbows housing

2

inlet flange

3

inlet

4

outlet flange

5

outlet

6

Pump impeller housing

7

pumps propeller

8th

drive shaft

9

Drive shaft tunnel

10

distal end

11

Pump bearing support

11A

shell

12

wall

13

sealing arrangement

14

layer

15

radial extension

16

outer surface

17

hollow shaft

18

Pump drive pulley

19

traction means

20

Motor drive plate

21

Motor drive shaft

22

drive motor

23

Interior radial bearings

24

first outer radial bearing

25

second outer radial bearing

26

dimensionally stable intermediate housing

27

wall

27A

Engine mount flange

28

component

29

component

30

Hollow shaft area

31

contact protection

32

module

33

entirety

201A

ring case

201B

pump housing

203

inlet

205

outlet

206

Wheel

301A

ring case

301B

pump housing

303

inlet

304

intake

305

outlet

306

Wheel

307

90 ° bow

308

riser

a

first length range

b

stock-free length range

l1

Length of the pump bearing carrier

A-A

cut

Claims (15)

Centrifugal pump (100, 200, 300),
with a support structure (1) having a wall (12),
with a pump bearing support (11) extending forwards over a length (l1) from the wall (12), a distal end (10) facing away from the wall (12) and having an outer surface (16),
with a drive shaft (8) protruding axially from the distal end (10) of the pump bearing carrier (11),
and with a drive shaft (8) rotatably connected pump drive pulley (18),
characterized,
in that a hollow shaft (17) arranged coaxially with the drive shaft (8) is provided, which extends from the distal end (10) over at least part of the pump bearing carrier (11) and with the drive shaft (8) in the distal end (10). protruding area is rotatably connected,
and that the pump drive disc (18) with the hollow shaft (17) is rotatably connected. Centrifugal pump according to claim 1, characterized in that for storage of the drive shaft (8) and the hollow shaft (17) at least one inner, the drive shaft (8) receiving Innenradiallager (23) and axially spaced from the Innenradiallager (23) at least a first outer, the hollow shaft (17) on the outer surface (16) of the pump bearing support (11) supporting Außenradiallager (24) are provided that preferably a second outer, the hollow shaft (17) on the outer surface (16) of the pump bearing carrier (11) axially from the first spaced apart supporting outer radial bearing (25) is provided, and that preferably the first outer radial bearing (24) near the distal end (10) and the second outer radial bearing (25) near the pump drive pulley (18) are provided. Centrifugal pump according to claim 1 or 2, characterized in that the pump drive disc (18) is designed as a separate, on the hollow shaft (17) attachable and preferably replaceable component. Centrifugal pump according to one of claims 1 to 3, characterized in that the entirety (33) of drive shaft (8) and hollow shaft (17) consists of two separate and joinable components (28, 29), and that preferably the drive shaft (8) in a region (30) with the hollow shaft (17) is fixedly connected, which surrounds the first outer radial bearing (24). Centrifugal pump according to claim 6, characterized in that the one component (28) the drive shaft (8) and the second component (29) the hollow shaft (17) with a over the distal end (10) of the pump bearing carrier (11) reaching and the connection comprising the drive shaft (8) causing area. Centrifugal pump according to one of claims 1 to 5, characterized in that the drive shaft (8) has a first length range (a), which is determined by the center distance of the maximum axial distance from each other having inner and outer radial bearings (23, 24), and a second length range (b), which is determined by a bearing-free length (b), via which the drive shaft (8) projects into the housing (1, 201, 301). Centrifugal pump according to one of claims 1 to 6, characterized in that the centrifugal pump (100) is an axial pump. Centrifugal pump according to claim 7, characterized in that for the relationship between the first and the second length ranges a, b: 0.6 <b / (a + b) <0.8 Centrifugal pump according to one of claims 1 to 8, characterized in that the centrifugal pump is a centrifugal pump (200). Centrifugal pump according to claim 9, characterized in that for the relationship between the first and the second length ranges a, b: 0.45 <b / (a + b) <0.65 Centrifugal pump according to one of claims 1 to 6, characterized in that the centrifugal pump is a vertical pump (300). Centrifugal pump according to claim 11, characterized in that for the relationship between the first and the second length ranges a, b: 0.6 <b / (a + b) <0.8 Centrifugal Pump Unit (400),
with a centrifugal pump (100, 200, 300) according to any one of claims 1 to 12, comprising a drive motor (22) comprising a motor drive shaft (21) comprising a motor drive pulley (20) and arranged such that the motor shaft (21) is parallel to the drive shaft (8),
and a traction means (19) operatively connected to the motor drive pulley (20) and the pump drive pulley (18). Centrifugal pump assembly (400) according to claim 13, characterized in that the centrifugal pump assembly (400) comprises a dimensionally stable intermediate housing (26) on the side of the support structure (1) from which the pump bearing support (11) extends. Centrifugal pump assembly (400) according to claim 14, characterized in that the motor drive pulley (20), the pump drive pulley (18) and the traction means (19) are at least partially surrounded by the intermediate housing (26).

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