Centrifugal pump for conveying a fluid

Abstract

A centrifugal pump for conveying a fluid includes a housing having an inlet and an outlet for the fluid. An impeller is arranged in the housing for rotation in an axial direction to convey the fluid from the inlet to the outlet, a shaft extends in the axial direction for driving the impeller, and a stationary guide device for guiding the fluid from the impeller to the outlet is connected to the housing. A resilient compensating element is disposed between the housing and the guide device, is arranged around the shaft, and holds the guide device in a centered position to the impeller during a radial relative movement to the housing.

Claims

1. A centrifugal pump for conveying a fluid, comprising: a housing having an annular support surface, and an inlet and an outlet for the fluid, the annular support surface facing outwardly; an impeller arranged in the housing and configured to rotate about an axial direction to convey the fluid from the inlet to the outlet; a shaft extending in an axial direction and configured to drive the impeller; a stationary guide having an radial annular surface, and being configured to guide the fluid from the impeller to the outlet, the stationary guide being connected to the housing, and the radial annular surface facing inwardly; a resilient compensating element disposed between the annular support surface of the housing and the radial annular surface of the stationary guide, the resilient compensating element being arranged around the shaft and configured to hold the stationary guide in a centered position with respect to the impeller upon radial relative movement of the stationary guide relative to the housing; and a plurality of connecting elements fixing the stationary guide to the housing with respect to the axial direction, each connecting element of the plurality of connecting elements configured to enable radial relative movement between the housing and the stationary guide, and comprising a sleeve arranged in an axial bore in the housing or in the stationary guide and a fixing device extending through a central longitudinal passage in the sleeve and into an other of the housing or the stationary guide to fix the stationary guide, the central longitudinal passage disposed around an axis passing through a center of the sleeve and the sleeve having an outer diameter which is smaller than an inner diameter of the axial bore, so that an annular gap is formed between the sleeve and a wall limiting the axial bore.

2. The centrifugal pump according to claim 1, wherein the resilient compensating element is annular.

3. The centrifugal pump according to claim 1, wherein the resilient compensating element comprises a first contact surface and a second contact surface, the first contact surface abutting the stationary guide and the second contact surface abutting the housing and the first contact surface and the second contact surface are arranged offset to each other with respect to the axial direction.

4. The centrifugal pump according to claim 1, wherein the resilient compensating element comprises a first transverse leg configured to contact the stationary guide and a second transverse leg configured to contact the housing, the first transverse leg and the second transverse leg connected to each other by a longitudinal leg extending in the axial direction.

5. The centrifugal pump according to claim 1, wherein the impeller or the stationary guide is made of a different material than the housing.

6. The centrifugal pump according to claim 1, further comprising a drive unit configured to drive the impeller, the drive unit being connected to the shaft, and arranged in the housing.

7. The centrifugal pump according to claim 1, wherein the housing is a pressure housing.

8. The centrifugal pump according to claim 7, wherein the pressure housing is configured to operate at an operating pressure of at least 200 bar.

9. The centrifugal pump according to claim 1, wherein the pump is designed for a fluid having a temperature of more than 400° C.

10. The centrifugal pump according to claim 1, further comprising a drive unit arranged below the impeller with respect to a vertical direction.

11. The centrifugal pump according to claim 1, wherein the impeller is a radial impeller.

12. The centrifugal pump according to claim 1, wherein the pump is a boiler circulation pump or as an ebullating pump configured to circulate a process fluid.

13. The centrifugal pump according to claim 1, wherein each sleeve has a length in the axial direction which is larger than a length of the axial bore in which the sleeve is arranged, and each sleeve has a flange at one axial end thereof, the flange having an outer diameter which is larger than the inner diameter of the axial bore in which the sleeve is arranged.

14. The centrifugal pump according to claim 13, wherein each sleeve is configured and arranged such that in the axial direction an axial gap is formed between the flange and the housing or the stationary guide in which the axial bore is provided, so as to prevent abutting of the flange with the housing or the stationary guide.

15. A centrifugal pump for conveying a fluid, comprising: a housing having an annular support surface, and an inlet and an outlet for the fluid, the annular support surface facing outwardly; an impeller arranged in the housing and configured to rotate about an axial direction to convey the fluid from the inlet to the outlet; a shaft extending in an axial direction and configured to drive the impeller; a stationary guide having an radial annular surface, and being configured to guide the fluid from the impeller to the outlet, the stationary guide being connected to the housing, and the radial annular surface facing inwardly; and a resilient compensating element disposed between the annular support surface of the housing and the radial annular surface of the stationary guide, the annular support surface of the housing disposed radially inside of the radial annular surface of the stationary guide, the annular support surface of the housing facing in a direction away from the shaft and the radial annular surface of the guide facing in a direction of the shaft, and the resilient compensating element being arranged around the shaft and configured to hold the stationary guide in a centered position with respect to the impeller upon radial relative movement of the stationary guide relative to the housing.

16. The centrifugal pump according to claim 15, further comprising a plurality of connecting elements fixing the stationary guide to the housing with respect to the axial direction, each connecting element configured to enable radial relative movement between the housing and the stationary guide.

17. The centrifugal pump according to claim 16, wherein each connecting element comprises a sleeve arranged in an axial bore in the housing or in the stationary guide, and a fixing device configured to fix the stationary guide, the fixing device extending through the sleeve.

18. The centrifugal pump according to claim 17, wherein each sleeve has a length in the axial direction which is larger than a length of the axial bore in which the sleeve is arranged, and each sleeve has a flange at one axial end thereof, the flange having an outer diameter which is larger than the inner diameter of the axial bore in which the sleeve is arranged.

19. The centrifugal pump according to claim 18, wherein each sleeve is configured and arranged such that in the axial direction an axial gap is formed between the flange and the housing or the stationary guide in which the axial bore is provided, so as to prevent abutting of the flange with the housing or the stationary guide.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will be explained in more detail hereinafter with reference to the drawings.

(2) FIG. 1 is a partially schematic sectional view of an embodiment of a centrifugal pump according to the invention,

(3) FIG. 2 is an enlarged sectional view of the connection between the housing and the guide device from FIG. 1,

(4) FIG. 3 is a sectional view of the compensating element,

(5) FIG. 4 is a sectional view of the connecting element (without a screw),

(6) FIG. 5 is a sectional view of a first variant for the compensating element in a section along the axial direction, and

(7) FIG. 6 is a second variant for the compensating element in a section vertical to the axial direction.

DETAILED DESCRIPTION OF THE EMBODIMENTS

(8) FIG. 1 illustrates in a partially schematic sectional view an embodiment of a centrifugal pump according to the invention for conveying a fluid, the pump being entirely indicated with the reference sign 1. The centrifugal pump 1 has a housing 2, which has an inlet 3 and an outlet 4 for the fluid, an impeller 5 arranged in the housing 2 for rotation about an axial direction A, which is defined by the set rotation axis of the centrifugal pump 1, a shaft 6 for driving the impeller 5 extending in the axial direction A, as well as a stationary guide device 7 being connected to the housing 2 and guiding the fluid conveyed by the impeller 5 to the outlet 4. The term “diffuser” is also common to the guide device 7.

(9) FIG. 1 illustrates the embodiment in a section along the axial direction A.

(10) Below, a direction vertical to the axial direction is described as radial direction.

(11) In the embodiment described here, the housing 2 comprises an upper housing part 21, as well as a lower housing part 22, which are connected in a sealing manner to each other by screw connections, not illustrated, or by a flange connection.

(12) In the embodiment described here, the centrifugal pump 1 also comprises a drive unit (driver) 8 for driving the impeller 5, which drive unit 8 is connected to the shaft 6, on which the impeller 5 is arranged, wherein the drive unit 8 is arranged in the housing 2 of the centrifugal pump 1. It is understood, that the invention is not limited to such embodiments in which the drive unit 8 is integrated in the housing 2 of the pump 1. In fact, it is also possible, that the drive unit 8 is arranged as a separate device outside the housing 2 of the centrifugal pump 1.

(13) Below, it is referred to the application important for practice with an exemplary nature, that the embodiment of a centrifugal pump 1 according to the invention described here is designed as an ebullating pump. As mentioned above, ebullating pumps are pumps which are used for fluidized bed process or ebullated bed process in the hydrocarbon processing industry. These processes are used to clean heavy hydrocarbons, which remain in the bottom of fractionating columns, for example in the oil refinery, for example to desulphurize and/or to break into lighter hydrocarbons, which then can be used more economical as distillates. An example heavy hydrocarbons mentioned here can be heavy oil, which remains in the refinery of oil. In a method, according to the state of the art, the original substance, that is to say the heavy hydrocarbons as heavy oil, for example, is heated, mixed with hydrogen and then introduced as a process fluid into the fluidized bed reactor or into the ebullated bed reactor. Then, the cleaning or the breaking-up, respectively, of the process fluid takes place in the reactor by catalysts, which are kept in suspension in the reactor, in order to ensure contact as close as possible with the process fluid. For supplying the reactor with the process fluid or for circulating the process fluid, respectively, is used an ebullating pump, which is typically mounted directly to the reactor.

(14) As a result of the process, the process fluid is under a very high pressure, for example of at least 200 bar, and at a very high temperature, for example above 400° C., the ebullating pump has to be designed for such pressures and temperatures. In doing so, in particular the housing 2 of the centrifugal pump 1, which housing 2 encloses the impeller 5 and the drive unit 8, is designed as a pressure housing, which can safely withstand these high operating pressures of, for example, 200 bar or more. Additionally, the ebullating pump 1 also is designed in such a manner, that it can convey a hot process fluid without risk, which process fluid having a temperature of more than 400° C. The ebullating pump 1 usually is arranged in such a manner, that the shaft 6 extends in the vertical direction, wherein the impeller 5 is arranged at the top. This customary use position, is also illustrated in FIG. 1.

(15) Although the design of the centrifugal pump 1 is referred to as an ebullating pump, it is understood, however, that the invention is not limited to such designs or applications, respectively. The centrifugal pump 1 according to the invention can also be designed for other applications, for example as an immersion pump, which is entirely or partially immersed in a liquid, e.g. water, in the operating state. The centrifugal pump 1 can also be designed as a horizontal pump, in which the shaft 6 extends in the horizontal direction. In particular, the invention is suitable for such centrifugal pumps, which are used for conveying very hot fluids of, for example more than 400° C., as well as for centrifugal pumps 1, which are used for conveying very cold fluids of, for example −160° C. or even lower temperatures. Examples mentioned here are boiler circulation pumps, with which are circulated in thermal power plants for energy generation of the heat transfer fluids, especially of the heat transfer fluids in the primary circuit, or pumps, which are used in the field of energy generation by CSP (concentrated solar power) technology for conveying the heat transfer fluid (HTF: heat transfer fluid), usually a melted salt, or pumps in cryoindustry or cryotechnology, respectively, with which, for example, liquefied natural gas (LNG: liquefied natural gas) in the temperature range of, for example −160° C., is conveyed.

(16) In the embodiment of the centrifugal pump according to the invention which pump is designed as ebullating pump, illustrated in FIG. 1, the impeller 5 is arranged above the drive unit 8 with respect to the normal use position, illustrated in FIG. 1. The impeller 5 comprising a number of vanes or blades 51, with which impeller the fluid is conveyed from the inlet 3, which is arranged here above the impeller 5, to the outlet 4, which is arranged here at the side of the housing 2. Here the impeller 5 is designed as closed impeller 5 in a manner known per se with a hub 53 and a cover plate 52 facing the inlet 3 (see FIG. 2), between which the blades 51 are arranged. In doing so, the cover plate 52 covers the blades 51, so that substantially closed channels for the fluid are formed between these blades.

(17) In a manner known per se, the impeller 5 is surrounded by the stationary guide device 7, also referred to as diffusor, which is arranged externally around the impeller 5 with respect to the radial direction. The guide device 7 comprises a number of stationary guide vanes 71 in a manner known per se (see FIG. 2), with which the fluid conveyed by the impeller 5 is guided to the outlet 4 of the pump 1.

(18) The stationary guide device 7 is mounted to the housing 2 via a plurality of connecting elements (connectors) 9 and here in particular connected to the lower housing part 22 of the housing 2.

(19) Each connecting element 9 preferably comprises a fixing means or device (fixer) 91 including a thread (see FIG. 2), by which fixing device the guide device 7 is fixed to the housing 2. The fixing device 91 particularly is a screw connection, for example a screw or a (thread) bolt.

(20) A drive unit 8 drives the impeller 5, which drive unit is designed here as an electrical canned motor in a manner known per se. The drive unit 8 comprises an internal rotor 81 as well as an external stator 82 surrounding the rotor 81. A can 83 is disposed between the rotor 81 and the stator 82, which can hermetically seal the stator 82 against the rotor 81 in a well known manner. The rotor 81 is connected torque-proof to the shaft 6, extending in the axial direction A, and on the other hand the shaft is connected torque-proof to the impeller 5, so that the impeller 5 can be driven by the drive unit 8.

(21) With respect to the axial direction immediately above or immediately below the drive unit 8, a radial bearing 12 is disposed in each case for the radial bearing of the shaft 6. The impeller 5 is centered by the radial bearing 12 with respect to the housing 2. An axial bearing 16 is disposed for the shaft 6 below the lower radial bearing according to the description.

(22) Due to the process, the fluid to be conveyed in the ebullating pump 1 has a very high temperature, which is in the range of 450° C., for example. This enormously high temperature causes very strong thermal loads in the pump 1. These thermal loads are based, for example, on the high temperature gradients in the pump 1, because, on the one hand, parts of the pump 1, as for example the impeller 5 or the guide device 7, are in direct physical contact with the hot fluid that flows through it, and on the other hand, parts of the pump, as for example at least parts of the housing 2 are in direct physical contact and thus in thermal contact with the ambience of the pump 1, wherein the ambient air is drastically lower—or drastically higher at low-temperature applications.

(23) Additionally, very significant temperature transients can arise, in particular when starting the pump as long as it has not yet reached its operating point, or when shutting down the pump. Especially in the event of an emergency shutdown of the pump, for example if the catalyst fails in the reactor the temperature of the fluid has to be lowered by more than 100° C. within a short time, for example within a few minutes.

(24) Such temperature gradients or temperature transients can cause enormous thermal stresses in the pump 1, which are based on, inter alia, different thermal elongation of various components, especially for one thing on the different thermal elongation of the housing 2, then again on the guide device 7, which is connected to the housing 2. However, it is not even necessary, that these different components such as the housing 2 and the guide device 7 have greatly different coefficients of thermal expansion, for different thermal expansions can arise in these components solely due to the geometry or due to the different masses of the components or due to strong temperature gradients, which can cause significant stresses. Of course, this problem can be even more pronounced, if the housing 2 of the pump 1 and the guide device 7 are manufactured from different materials, which have significantly different coefficients of thermal expansion.

(25) Due to these different thermal expansions, there is the risk, that the centering of the guide device 7 to the impeller 5 is lost or is no longer ensured, respectively. As it can be seen in particular in the enlarged view of FIG. 2, only a very small clearance S in the form of an annular gap is disposed in the radial direction between the rotating cover plate 52 of the impeller 5 and the stationary guide device 7, via which clearance the fluid can flow back from the pressure side of the impeller 5 to the inlet 3. This annular gap or this clearance, respectively, is intentionally kept very small, particularly in order to avoid an excessive backflow of the fluid. Due to this small clearance S, it is very important, that the impeller 5 runs as accurately centered as possible with respect to the guide device 7. If deformation arises due to different thermal expansions of the housing 2 and of the guide device 7, so that the guide device 7 loses its centricity with respect to the impeller 5, there is a significant risk, that the rotating impeller 5 directly contacts the stationary guide device 7, which can result in serious damages to the impeller 5 or to the pump 1, respectively.

(26) That is the reason why, according to the invention, a resilient compensating element (compensator) is disposed between the housing 2 and the guide device 7, which compensating element is arranged around the shaft 6 and which can hold the guide device 7 in a centered position with respect to the impeller 5 during a radial relative movement, in particular in the case of a relative displacement between the housing 2 and the guide device 7.

(27) Then, the different elongation between the housing 2 on the one hand, and the guide device 7 on the other hand is compensated by a corresponding deformation of the resilient compensating element 10.

(28) For a better understanding, FIG. 2 illustrates an enlarged sectional view of the connection between the housing 2 and the guide device 7 with the resilient compensating element 10 arranged in between. The section takes place in the axial direction. FIG. 3 further illustrates a sectional view of the compensating element 10 in a section along the axial direction A. For a better overview, the guide device 7 is indicated in FIG. 3, while the housing 2 is not illustrated.

(29) If, due to the described thermal effects, different elongations arise in the housing 2 and in the guide device 7 and specifically in the area in which the guide device 7 is connected to the housing 2, here the lower housing part 22, so the resilient compensating element 10 is deformed, whereby the relative displacement in the radial direction of the housing 2 with respect to the guide device 7 is compensated in this area, so that the guide device 7 remains in its centered position with respect to the impeller 5. Thus, the resilient compensating element 10 acts as a spring, with which relative movements in the radial direction are compensated between the housing 2 and the guide device 7, so that the guide device 7 remains centered with respect to the impeller 5.

(30) In the embodiment described here, the resilient compensating element 10 is designed to be annular, especially as an axially symmetrical spring ring with respect to the axial direction. Suitable materials for the compensating element 10 are basically all materials, which are generally used for springs, for example spring steel. Spring steel is particularly distinguished by a significantly higher elastic limit compared to other steels. The compensating element 10 is preferably designed in such a manner with respect to its material properties and to its geometry, that it elastically deforms in the operating state of the pump 1, when stresses arise and that it returns to its original shape after the elimination of stresses. Preferably, a plastic deformation of the compensating element 10 is avoided, hence an exceeding of its elastic limit.

(31) As it can be seen in particular in FIG. 1 and FIG. 2, the annular compensating element 10 is arranged symmetrically around the shaft 6 between the housing 2 and the guide device 7, in such a manner that the guide device 7 is in contact with the housing 2 via the compensating element 10 with respect to the radial direction.

(32) The guide device 7 comprises a mounting foot 72 (see FIG. 2), by which the guide device 7 is connected to the housing 2. The mounting foot 72 comprises a radially internal annular surface 73, which is concentric with respect to the shaft 6 and thus axially symmetrical with respect to the axial direction A, on which annular surface the compensating element 10 is supported.

(33) The housing 2, here the lower housing part 22, has an annular support surface 23, which is concentric with respect to the shaft 6 and thus axially symmetrical with respect to the axial direction A, on which annular support surface 23 the compensating element 10 is supported. The support surface 23 is arranged radially internal with respect to the annular surface 73, wherein the support surface 23 and the annular surface 73 are coaxial.

(34) As it is particularly evident from FIGS. 2 and 3, the compensating element 10 has a first and a second contact surface 101 or 102, respectively, wherein the first contact surface 101 abuts on the guide device 7, namely on the annular surface 73 of the guide device 7, and wherein the second contact surface 102 abuts on the housing 2, namely on the support surface 23. The first and the second contact surface 101 or 102, respectively, are arranged offset to each other with respect to the axial direction. Hence, the compensating element 10 is designed in such a manner, that it contacts the guide device 7 only with the first contact surface 101 and the housing 22 only with the second contact surface 102 with respect to the radial direction.

(35) For this purpose, the compensating element 10 has a substantially S-shaped cross-sectional area, that is to say the compensating element 10 has a first transverse leg 103 for contacting the guide device 7 as well as a second transverse leg 104 for contacting the housing 2, wherein the first transverse leg 103 and the second transverse leg 104 are connected to each other by a longitudinal leg 105 extending in the axial direction A. The first and the second transverse leg 103 or 104, respectively, extend in each case in the radial direction. The first transverse leg 103 comprises the first contact surface 101 and the second transverse leg 104 comprises the second contact surface 102.

(36) Preferably, the annular compensating element 10 is measured in such a manner with respect to its outer diameter DA, that it can be inserted in the guide device 7 with an interference fit, so that first contact surface 101 is pre-clamped against the annular surface 73. The inner diameter DI of the annular compensating element 10 is measured in such a manner, that the compensating element 10 can still be mounted after being inserted into the guide device 7, that is in the pre-clamped state, that is to say the compensating element 10 can be arranged around the support surface 23 of the housing 2.

(37) In the embodiment illustrated in FIG. 3, this means, that the outer diameter DA of the first transverse leg 103 is slightly larger in the unclamped state than the diameter of the space limited by the annular surface 73. The inner diameter DI of the second transverse leg 104 is measured in such a manner, that it is after inserting the compensating element 10 into the guide device 7, that is in the unclamped state of the compensating element 10, at least as large as the diameter of that part of the housing 2, which is limited by the support surface 23.

(38) When different elongations of the housing 2 and of the guide device 7 arise in the operating state of the centrifugal pump 1, both contact surfaces 101 and 102 of the compensating element 10 are displaced relative to each other in the radial direction, wherein the radial relative movement between the housing 2 and the guide device 7 is compensated, so that the guide device 7 remains in its centered position with respect to the impeller 5.

(39) Thus, the main function of the compensating element 10 is to ensure the maintenance of the centered position of the guide device 7 with respect to the impeller 5 in the case of radial relative movements, thermally induced, between the guide device 7 and the housing 2. As a rule, the relative displacement between the housing 2 and the guide device 7 can be compensated by a deformation of the connecting elements 9, via which the guide device 7 is connected to the housing 2. Hereby, relatively strong mechanical stresses can arise in the connecting elements 9, for example by shearing stresses or bending stresses. In order to reduce or to avoid these mechanical loads, it is a particularly preferred measure to provide a plurality of connecting elements 9, which fix the guide device 7 to the housing 2 with respect to the axial direction A, wherein each connecting element 9 is designed in such a manner, that it allows radial relative movement between the housing 2 and the guide device 7. Regarding such a design, the guide device 7 is supported in a quasi-floating manner with respect to the housing 2 in the radial direction, thus the guide device 7 can be moved or displaced, respectively, with respect to the housing 2 in the radial direction.

(40) Such a preferred design of the connecting elements 9 is explained in more detail below with reference to FIG. 2 and FIG. 4. Thus, FIG. 4 illustrates a sectional view of the connecting element 9 in a section along the axial direction A, wherein the fixing device 91 is not illustrated in FIG. 4 for reasons of a better overview.

(41) Each connecting element 9 comprises a sleeve 92, which is arranged in an axial bore 13 in the guide device 7, more precisely in the mounting foot of the guide device 7. Of course, deviating from the illustration in FIGS. 2 and 4 it is also possible in an analogously same way, that the axial bore 13, which takes the sleeve 92, is disposed in the housing 2.

(42) The connecting element 9 further comprises the fixing device 91 for fixing the guide device 7 to the housing 2, wherein the fixing device 91 extends through the sleeve 92 into the housing 2 in the axial direction A. The fixing device 91 realizes preferably a screw connection and particularly preferred an expansion screw connection. For this purpose, the fixing device 91 preferably is a screw or a thread bolt or a stud bolt, especially preferred an expansion screw or an expansion stud bolt, as illustrated in FIG. 2. The expansion stud bolt 91 joins in a threaded hole 24 with its lower end (FIG. 2) in the housing 2 according to the description, which threaded hole aligns with the axial bore 13, but having a smaller inner diameter than the axial bore 13. The thread, disposed in the area of the lower end of the expansion stud bolt 91, joins in the thread of the threaded hole 24, so that the expansion stud bolt 91 is tightly connected to the housing 2.

(43) The sleeve 92 has an outer diameter D92, which is smaller than the inner diameter D13 of the axial bore 13, so that an annular gap 14 is formed between the sleeve 92 and the wall limiting the axial bore 13, which annular gap extends in the axial direction A along the entire length L of the axial bore 13.

(44) The sleeve 92 has a length H in the axial direction A, which length is larger than the length L of the axial bore 13. The sleeve 92 has a flange 93 at its upper axial end according to the illustration (FIG. 4), the flange having an outer diameter D93, which is larger than the inner diameter D13 of the axial bore 13. The sleeve 92 abuts on the housing 2 with its lower axial end according to the illustration (FIG. 4).

(45) As it can be seen in particular in FIG. 4, the length H of the sleeve 92 is measured in such a manner, that an annular axial gap 15 is formed between the flange 93 and the guide device 7, in which the axial bore 13 is disposed, with respect to the axial direction A, so that abutting of the flange 93 on the guide device 7 is avoided.

(46) In order to connect the guide device 7 to the housing 2, the expansion stud bolt 91, passing through the sleeve 92, is screwed in the threaded hole 24 in the housing 2. The upper end of the expansion stud bolt according to the illustration (FIG. 2), which also includes a thread, projects beyond the flange 93 in the axial direction A. A nut 94 is screwed on this end, which nut finally abuts on the flange 93. The guide device 7 is fixed to the housing 2 by tightening the nut 94 with respect to the axial direction A. Thereby, the expansion stud bolt 91 is preferably tensioned.

(47) Thus, the guide device 7 is connected to the housing 2 by the interaction of the majority of connecting elements 9, wherein the guide device 7 is fixed with respect to the axial direction A. This is done here by the preferably tensioned expansion stud bolts 91 in interaction with the sleeve 92, on the one hand, abutting on the housing and on the other hand, forming the support surface for the nut 94 with its flange 93, with which nut the expansion stud bolt 91 can be tensioned. In this state, the guide device 7 is fixed with an axial clearance 15 with respect to the axial direction.

(48) The guide device 7 is supported in a floating manner with respect to the housing 2 in the radial direction, due to the annular gap 14 in the axial bore between the sleeve 92 and the guide device 7. In spite of the fixing in the axial direction A, the guide device 7 can be moved with respect to the housing 2 in the radial direction. If a different elongation of the housing 2 on the one hand and of the guide device 7 on the other hand arises in the operating state of the pump 1, so the connecting elements 9 allow a relative displacement between the housing 2 and the guide device 7, due to the annular gap 14.

(49) The axial gap 15 is also particularly advantageous for such a relative displacement, which axial gap is disposed between the flange 93 and the mounting foot 72 of the guide device 7. Because of the fact, the flange 93 having no direct physical contact to the mounting foot 92, thus not abutting on this, there is no need to overcome in the case of a relative displacement any static frictional forces or dynamic frictional forces, which would act on or with, respectively, the mounting foot 72, when the flange is rested or tensioned.

(50) Here, it is particularly advantageous, that the connecting elements 9, fixing the guide device 7 to the housing 2 with respect to the axial direction A, are designed in such a manner, that they allow a radial relative movement between the housing 2 and the guide device 7 without an axial tensioning.

(51) The solution according to the invention, with which thermally induced elongation effects can be compensated, is also suitable in particular for such embodiments, in which the impeller 5 and/or the guide device 7 is manufactured of a different material than the housing 2. For technical reasons, it can be advantageous to use a different material for the impeller 5 and/or the guide device 7 than for the housing 2.

(52) The housing 2 is usually made of a steel or of a cast material such as cast iron. It is preferably for some applications, when the impeller 5 is made of a different material. As already mentioned, generally a chemically very aggressive fluid is conveyed with the ebullating pump, for example, which fluid may additionally have abrasive properties. Therefore, it may be desirable to manufacture the impeller 5 and the guide device 7, which are perfused by the fluid, of a different material with higher wear resistance, which is more resistant to the load collective by the fluid, and thus allowing a longer service life or longer maintenance intervals, respectively. This may be, for example, a material with a very good corrosion resistance or hot corrosion resistance, respectively. Particularly suitable for the impeller 5 and the guide device 7 of an ebullating pump, but also for other high-temperature applications, are nickel-base alloys, which are known under the trade name Inconel.

(53) Therefore, Inconel is also advantageous, because it can be treated particularly well by methods for surface hardening, such as for example bonding. With regard to Inconel, the diffusion processes during bonding are much deeper inside the material, as when using other materials, for example austenitic steel, so that especially wear resistant surfaces can be generated by bonding.

(54) It is understood, that for the specific design of the compensating element 10 numerous other variants are possible, of course than that illustrated in FIG. 3.

(55) For example. in FIG. 5 is illustrated a first variant for the compensating element 10, wherein the compensating element 10 is designed annularly again. In contrast to the design illustrated in FIG. 3, the first variant, illustrated in FIG. 5, has a cross-sectional area, which is substantially shaped as a parallelogram, which abuts on the guide device 7 with the first contact surface 101, and with the second contact surface at the housing 2. In this case, it may be advantageous to flatten the respective corners in order to enlarge the contact surfaces 101 or 102, respectively.

(56) It is also by no means necessary, that the compensating element 10 is designed as a complete ring. FIG. 6 illustrates a second variant for the compensating element 10 in a section vertical to the axial direction A, wherein the section plane is in the compensating element 10. With regard to this second variant, the compensating element 10 comprises a plurality, here four, of separate segments 10a, 10b, 10c, 10d, each of them being arranged between the housing 2 and the guide device 7, wherein the segments 10a, 10b, 10c, 10d are preferably arranged symmetrically around the shaft 6. Each individual segment 10a, 10b, 10c, 10d can be, for example, designed with a cross-sectional area, which corresponds to that illustrated in FIG. 3 or in FIG. 5. Of course, other designs are also possible with respect to the cross-sectional area.