EP3460246B1 - Centrifugal pump for cryogenic feed media - Google Patents

Centrifugal pump for cryogenic feed media Download PDF

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Publication number
EP3460246B1
EP3460246B1 EP18192242.8A EP18192242A EP3460246B1 EP 3460246 B1 EP3460246 B1 EP 3460246B1 EP 18192242 A EP18192242 A EP 18192242A EP 3460246 B1 EP3460246 B1 EP 3460246B1
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EP
European Patent Office
Prior art keywords
pump
roller bearing
cryogenic
pump housing
housing
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EP18192242.8A
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German (de)
French (fr)
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EP3460246A1 (en
Inventor
Stéphane BOEGLIN
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Fives Cryomec AG
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Fives Cryomec AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/22—Lubricating arrangements using working-fluid or other gaseous fluid as lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0633—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/049—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/406—Casings; Connections of working fluid especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0865—Oxide ceramics
    • F05C2203/0886—Silica

Definitions

  • the present invention describes a centrifugal pump for cryogenic media according to the preamble of the first claim.
  • a known weak point particularly in the case of centrifugal pumps for use with cryogenic conveying media, is the roller bearings which are usually used and on which a motor shaft is mounted.
  • Such a solution of a pump for cryogenic media with unlubricated roller bearings is for example from the Japanese patent document JP 2014/020491 A known.
  • steel races are used, the steel being subjected to cryogenic hardening.
  • the rolling elements can also be made of steel with cryogenic hardening or ceramic. According to the solution shown in this document, an attempt should therefore be made to To increase the abrasion resistance of the bearings in order to be able to dispense with the use of lubricants.
  • a centrifugal pump for conveying a cryogenic medium comprises a main delivery flow of the cryogenic delivery medium between the inlet side or suction side, and the outlet side or pressure side.
  • openings are provided in an outlet flange, part of the escaping, cryogenic delivery medium being branched off from the main delivery flow via these openings and being guided to a connecting piece on the pump housing via pipes arranged outside the pump housing.
  • the connecting piece is located essentially in the same axial position as the upper roller bearing, ie, the roller bearing which is more distant from the pump wheel, with a through a bore in an upper housing cover communicating connection between the connecting piece and the upper roller bearing is created. Lubrication of the upper roller bearing and cooling of the upper roller bearing are thereby achieved.
  • the branched-off part of the cryogenic delivery medium can be returned to the main delivery flow of the cryogenic delivery medium along the motor shaft and via a gap above the impeller designed as an impeller.
  • a one-piece shaft which functions both as a motor shaft and as a pump shaft, shows in DE 1 801 864 a bore extending between the roller bearings, whereby a cavity is formed in this area of the shaft.
  • a communicating connection exists between the connection piece in the cavity in the shaft. Via additional holes in the shaft, a communicating connection is also created between this cavity of the shaft and the roller bearings.
  • known centrifugal pumps have the disadvantage that a large number of pipes, ie comparatively long distances are necessary so that the branched-off part of the cryogenic medium can get to the roller bearings and back into the main flow of the cryogenic medium.
  • the object of the present invention is to provide a centrifugal pump which overcomes the disadvantages of the known prior art and in particular keeps the design of the centrifugal pump as simple as possible.
  • a centrifugal pump fulfills these tasks with the features of claim 1.
  • a first communicating connection in particular a direct connection channel, is formed between the pressure side in the pump housing and the roller bearing on the pump housing, for a branched part of the cryogenic delivery medium to the roller bearing, and a second communicating connection is formed for the branched part between the roller housing on the pump housing side and the suction side of the cryogenic delivery medium back to the suction side in the pump housing, so that circulation of the branched-off part of the cryogenic delivery medium between the pump housing and only the roller bearing on the pump housing side is ensured.
  • a direct connection channel between the pressure side in the pump housing and the roller bearing on the pump housing side is understood as the first communicating connection that, in contrast to the centrifugal pump, consists of the DE 1801864 no indirect connection is made with the roller bearing on the pump housing via the roller bearing on the drive motor side, which is further away from the impeller.
  • the cryogenic delivery medium branched off for lubrication and cooling can circulate in a comparatively small-scale circle. Losses of the branched, cryogenic delivery medium can thereby be kept low.
  • cryogenic delivery medium it is necessary for the cryogenic delivery medium not to evaporate in the region of the unlubricated roller bearing on the pump housing side, which is preferably made possible by preventing the pressure from falling below a certain minimum pressure. Evaporation of the cryogenic medium in the area of the roller bearings can damage the roller bearings.
  • a comparatively small-scale circulation circuit is advantageous since it ensures that the necessary minimum pressure is maintained by the construction.
  • liquid gases such as liquid hydrocarbons such as liquid methane, liquid nitrogen etc. can be used as the cryogenic delivery medium.
  • Liquid gas is understood to mean a gas liquefied by cooling and compression. It has been shown that liquid Hydrocarbons have good lubricating properties and are therefore particularly well suited for cryogenic lubrication.
  • An intermediate piece in the form of a housing cover is preferably located between the motor housing and the pump housing, the housing cover having a connecting channel in the form of a bore between the pressure side and the roller bearing on the pump housing side to form the first communicating connection.
  • a sealing element is preferably arranged between the housing cover on the pump housing side and the shaft in a sealing manner in order to achieve a barrier between the pump housing and the motor housing.
  • the drive motor side in the centrifugal pump according to the invention is preferably a conventional, lubricated roller bearing.
  • the sealing element serving as a barrier to the cryogenic delivery medium thus advantageously avoids the known problems that occur when the cryogenic delivery medium comes into contact with lubricated roller bearings, and also forces the branched part back into the main delivery flow of the cryogenic delivery medium via the second communicating connection.
  • the centrifugal pump according to the invention is preferably designed for use in a horizontal position and is therefore suitable for being attached, for example, to a truck (truck).
  • the motor housing preferably has an outlet bore, in particular at a point at the lowest point in use in a horizontal position, one on the outlet bore toward the suction side running pressure equalization line can be attached.
  • Such an outlet bore with a pressure compensation line attached to it advantageously allows removal of undesirable cryogenic delivery medium which is present in the motor housing and which, for example, due to an inadequate barrier effect, for example due to damage or wear of the sealing element between the pump housing-side housing cover and the shaft, has entered the motor housing.
  • Fig. 1 shows a longitudinal section through a preferred embodiment of the centrifugal pump 1 according to the invention.
  • the centrifugal pump 1 has a motor housing for an electric drive motor unit 12 and a pump housing 2 for receiving the pump elements.
  • it is a single-stage impeller pump with only one impeller 5, and it can also be a multi-stage impeller pump with several impellers 5.
  • the drive motor unit 12 has a shaft 11 which in two roller bearings 20; 21 is stored.
  • the shaft 11 is a one-piece shaft which functions both as a motor shaft and as a pump shaft.
  • a design of the centrifugal pump 1 with a shaft that is not in one piece is also conceivable, in which a motor shaft can be connected to a pump shaft via a coupling.
  • a pump wheel 5 and an impeller 6 designed as an impeller are fastened here by means of a fixing screw 7.
  • the pump wheel 5 is designed here, for example, as a spiral conveyor blade.
  • a suction flange 4 is arranged on the pump housing 2 on the inlet opening E or suction side S for the suction of the main delivery flow F H of the cryogenic delivery medium.
  • the outlet side is arranged here with an outlet flange for the discharge of the main delivery flow F H of the cryogenic delivery medium (not visible in FIG Fig. 1 ).
  • a housing cover 15 Between the motor housing 10 and the pump housing 2 there is an intermediate piece in the form of a housing cover 15, this housing cover 15 producing a fixed connection between the motor housing 10 and the pump housing 2 using suitable fixing means.
  • the housing cover 15 has an adapter and separation function.
  • the pump housing side i.e. the roller housing 21 mounted closer to the pump housing 2 or pump wheel 5.
  • an insulating disk 19 is preferably arranged between the housing cover 15 and the motor housing 10.
  • connection channel 16 is formed here in the form of a bore in the housing cover 15 and extends here, for example, between roller bearings 21 transversely outwards to an outer radial region of the pump housing 2 Fig. 1 only one connection channel 16 is shown, it being possible for one or more connection channels 16 to be present as required.
  • a pressure P 2 on the pressure side D in the outer radial region of the pump housing 2 increases compared to a pressure P 1 on the suction side S in an inner radial region of the pump housing 2 due to the centrifugal forces.
  • the pressure P 2 on the Pressure side D usually corresponds to the pressure to be achieved of the emerging main delivery flow F H of the cryogenic delivery medium.
  • a pressure gradient is formed, where: P 2 > P 1 .
  • This pressure gradient causes a part F A1 to branch off from the main delivery flow F H of the cryogenic delivery medium in the direction of the roller bearing 21 and thereby Flow or cryogenic lubrication and cooling of the roller bearing 21.
  • the circulation is ensured by the pressure gradient or the pressure difference between pressure side D and suction side S. It has been shown that a pressure gradient or a pressure difference between P 1 and P 2 of 0.8 to 8 bar can be adjustable in the centrifugal pump 1 according to the invention, this pressure gradient being able to be influenced in particular by the pump speed and the diameter of the impeller.
  • a second communicating connection is formed for the return of the branched part F A2 of the cryogenic conveying medium back to the suction side S in the pump housing 2, so that a circulation of the branched part F A1 ; F A2 of the cryogenic delivery medium between the pressure side D in the pump housing 2 via the roller housing 21 on the pump housing back to the suction side S is ensured.
  • the second communicating connection is designed in the form of at least one lower opening O 2 of the roller bearing 21 on the pump housing side and can thus reach an upper suction side S 1 .
  • the second communicating connection contains at least one bore B in the impeller 6, which is indicated here by dashed lines, as a result of which the branched part F A2 of the cryogenic delivery medium can return from an upper suction side S 1 to the suction side S. It has been shown that there is a slightly higher pressure between the upper suction side S 1 than the pressure P 1 on the suction side S, as a result of which the branched part F A2 of the cryogenic delivery medium can get back into the main delivery flow F H of the cryogenic delivery medium.
  • a ring-shaped sealing element 18, which surrounds the shaft 11, is arranged between the housing cover 15 and the shaft 11 so as to seal around a barrier between the pump housing 2 and the motor housing 10 to achieve.
  • This sealing element 18 forces - as in Fig. 1 evident in the direction facing away from the motor housing 10 - the branched-off part F A2 of the cryogenic delivery medium via the second communicating connection back into the main delivery flow F H of the cryogenic delivery medium.
  • This in Fig. 1 also has, by way of example - in addition to the sealing element 18 - a labyrinth seal 17 between the unlubricated roller bearing 21 and the sealing element 18.
  • the centrifugal pump 1 allows the branched part F A1 of the cryogenic conveying medium to flow through a gap between the labyrinth seal 17 and the roller bearing 21, so that the branched part F A1 of the cryogenic conveying medium reaches the roller bearing 21 via at least one upper opening O 1 and can be lubricated using the cryogenic fluid.
  • the centrifugal pump 1 is ideally designed or suitable to be operated in a horizontal position, ie with a horizontally oriented longitudinal axis of the shaft 11, for use on a truck, for example.
  • the centrifugal pump 1 is preferably configured such that the in Fig. 1 shown, exit bore 13 in the motor housing 10 is aligned and arranged at a lowest point viewed in the direction of gravity, whereby undesired liquid cryogenic delivery medium located in the motor housing 10 can collect at this point.
  • a pressure compensation line 14 is preferably sealingly attached to the outlet bore 13 and to a bore 3 in the suction flange 4 of the pump housing 2.
  • Such a pressure equalization line 14 is advantageous because the liquid, cryogenic delivery medium is forced out of the interior of the motor housing 10 in the direction of the suction side S at the inlet opening E.
  • Such an outlet bore 13 with a pressure compensation line 14 attached to it advantageously allows removal of liquid cryogenic that is undesirably present in the motor housing 10 Delivery medium, which has reached the motor housing 10 between the pump housing-side housing cover 15 and the shaft 11, for example due to a defective barrier effect, for example due to damage or wear of the sealing element 18.
  • the unlubricated roller bearing 21 in the housing cover 15 here comprises a plurality of balls 23, an inner race 25 and an outer race 27 each with running surfaces between which the balls 23 are arranged, in which case the balls 23 can be made of ceramic.
  • the races 25; 27 are preferably made of steel and ideally have a chrome-based coating in the area of the treads.
  • Such an unlubricated roller bearing 21 or ball bearing is also referred to as a hybrid bearing, in which for the races 25; 27 and the balls 23 (also called rolling elements) different materials are used.
  • the most common type is that of a deep groove ball bearing with conventional races 25; 27 made of steel and balls 23 made of a high-strength ceramic, mostly silicon nitride.
  • roller bearing 20 in the housing cover 9 on the drive motor side can be manufactured identically to the roller bearing 21, but for cost reasons it can also advantageously be a conventional, lubricated roller bearing.
  • the mutual spacing of the balls 23 in the unlubricated roller bearing 21 is determined by a cage (not shown in FIG Fig. 1 ) which has a separate chamber for each ball 23.
  • the inner surfaces of the chambers are preferably cylindrical and the cylinder diameter is chosen to be somewhat larger than the diameter of the balls 23, so that the balls can rotate freely in the cage.
  • this cage is made of reinforced PTFE (P oly t etra f luor e Thylen).
  • this cage can also be made of stainless steel, polyether ether ketone (PEEK), brass or any combination thereof.

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Description

Technisches GebietTechnical field

Die vorliegende Erfindung beschreibt eine Zentrifugalpumpe für kryogene Fördermedien gemäss Oberbegriff des ersten Patentanspruches.The present invention describes a centrifugal pump for cryogenic media according to the preamble of the first claim.

Stand der TechnikState of the art

Bekannt sind aus dem Stand der Technik Pumpen für kryogene Medien. Eine bekannte Schwachstelle gerade bei Zentrifugalpumpen für den Einsatz mit kryogenen Fördermedien liegt bei den üblicherweise verwendeten Rollenlagern, auf welchen eine Motorwelle gelagert ist.Pumps for cryogenic media are known from the prior art. A known weak point, particularly in the case of centrifugal pumps for use with cryogenic conveying media, is the roller bearings which are usually used and on which a motor shaft is mounted.

Die Einflüsse eines kryogenen Fördermediums auf geschmierte Rollenlager sind an sich bekannt. Es hat sich gezeigt, dass gängige Schmiermittel in der Regel ziemlich rasch durch im Lagerbereich entstehende oder dort eindringende Dämpfe zumindest teilweise aufgelöst werden. Diese Effekte zeigen sich grundsätzlich bei allen bekannten Schmiermitteln für Rollenlager und sie zeigen sich im Laufe der Zeit selbst dann, wenn speziell abgedichtete geschmierte Lager verwendet werden.The effects of a cryogenic medium on lubricated roller bearings are known per se. It has been shown that common lubricants are usually at least partially dissolved by vapors that arise in the bearing area or penetrate there. These effects are generally seen in all known lubricants for roller bearings and they show up over time even when specially sealed lubricated bearings are used.

Aufgrund dieser Schmiermittelproblematik sind deshalb auch Lösungen für Pumpen mit kryogenen Fördermedien entwickelt worden, wobei die Rollenlager nicht geschmiert sind.Because of this lubricant problem, solutions for pumps with cryogenic fluids have been developed, whereby the roller bearings are not lubricated.

Eine solche Lösung einer Pumpe für kryogene Fördermedien mit ungeschmierten Rollenlagern ist beispielsweise aus dem japanischen Patentdokument JP 2014/020491 A bekannt. Gemäss diesem Dokument werden Laufringe aus Stahl eingesetzt, wobei der Stahl einer kryogenen Härtung unterzogen wurde. Die Rollkörper können ebenfalls aus Stahl mit kryogener Härtung oder aus Keramik bestehen. Gemäss der in diesem Dokument gezeigten Lösung soll somit versucht werden, die Abrasionsfestigkeit der Lager zu erhöhen, um dadurch auf den Einsatz von Schmiermitteln verzichten zu können.Such a solution of a pump for cryogenic media with unlubricated roller bearings is for example from the Japanese patent document JP 2014/020491 A known. According to this document, steel races are used, the steel being subjected to cryogenic hardening. The rolling elements can also be made of steel with cryogenic hardening or ceramic. According to the solution shown in this document, an attempt should therefore be made to To increase the abrasion resistance of the bearings in order to be able to dispense with the use of lubricants.

Es hat sich jedoch gezeigt, dass Materialkombinationen aus Metall und Keramik in ungeschmierten Rollenlagern beziehungsweise Kugellagern (auch allgemein als Wälzlager bezeichnet) in Pumpen, insbesondere Zentrifugalpumpen, keine genügende Ausfallsicherheit bieten. Je mehr die Drehzahl der Motorwelle erhöht wird, desto höher ist die reibungsbedingte Belastung zwischen den einzelnen Komponenten des Rollenlagers.However, it has been shown that material combinations of metal and ceramic in unlubricated roller bearings or ball bearings (also generally referred to as roller bearings) in pumps, in particular centrifugal pumps, do not offer sufficient reliability. The more the speed of the motor shaft is increased, the higher the frictional load between the individual components of the roller bearing.

Da die Möglichkeiten hinsichtlich der Optimierung der Materialienpaarungen bzw. Materialkombinationen des ungeschmierten Rollenlagers an Grenzen stösst, sind ebenfalls Lösungen von Pumpen für kryogene Fördermedien mit so genannter kryogener Schmierung der Rollenlager, d.h. eine Schmierung anhand eines Teils des kryogenen Fördermediums, bekannt.Since the possibilities for optimizing the material pairings or material combinations of the unlubricated roller bearing reach their limits, solutions of pumps for cryogenic media with so-called cryogenic lubrication of the roller bearings, i.e. Lubrication using part of the cryogenic fluid is known.

Aus der US 3,652,186 und der US3,975,117 ist beispielsweise eine Zentrifugalpumpe zum Fördern eines kryogenen Mediums bekannt. Die Zentrifugalpumpe umfasst einen Hauptförderstrom des kryogenen Fördermediums zwischen der Eintrittsseite beziehungsweise Saugseite, und der Austrittsseite beziehungsweise Druckseite.From the US 3,652,186 and the US3,975,117 For example, a centrifugal pump for conveying a cryogenic medium is known. The centrifugal pump comprises a main delivery flow of the cryogenic delivery medium between the inlet side or suction side, and the outlet side or pressure side.

Im Austrittsbereich, d.h. auf der Druckseite, der in US 3,652,186 gezeigten Zentrifugalpumpe sind Öffnungen in einem Auslassflansch vorgesehen, wobei über diese Öffnungen ein Teil des austretenden, kryogenen Fördermediums vom Hauptförderstrom abgezweigt und über ausserhalb des Pumpengehäuses angeordnete Rohrleitungen an einen Anschlussstutzen am Pumpengehäuse geführt wird.In the exit area, ie on the pressure side, the in US 3,652,186 Centrifugal pump shown, openings are provided in an outlet flange, part of the escaping, cryogenic delivery medium being branched off from the main delivery flow via these openings and being guided to a connecting piece on the pump housing via pipes arranged outside the pump housing.

Der Anschlussstutzen befindet sich im Wesentlichen in derselben axialen Position wie das obere, d.h. dem Pumpenrad entferntere, Rollenlager, wobei durch eine Bohrung in einem oberen Gehäusedeckel eine kommunizierende Verbindung zwischen Anschlussstutzen und dem oberen Rollenlager geschaffen wird. Dadurch werden eine Schmierung des oberen Rollenlagers sowie eine Kühlung des oberen Rollenlagers erzielt.The connecting piece is located essentially in the same axial position as the upper roller bearing, ie, the roller bearing which is more distant from the pump wheel, with a through a bore in an upper housing cover communicating connection between the connecting piece and the upper roller bearing is created. Lubrication of the upper roller bearing and cooling of the upper roller bearing are thereby achieved.

Das untere, d.h. dem Pumpengehäuse näher gelegene beziehungsweise pumpengehäuseseitige, Rollenlager wird ebenfalls mit dem abgezweigten Teil des kryogenen Fördermediums versorgt, indem zwischen dem Rollenlagergehäuse und der Welle genügend Spiel vorhanden ist für den Durchtritt des kryogenen Fördermediums an dieser Stelle. An der Austrittsstelle aus dem unteren Rollenlager kann entlang der Motorwelle sowie über einen Spalt oberhalb des als Flügelrad ausgestalteten Laufrads der abgezweigte Teil des kryogenen Fördermediums in den Hauptförderstrom des kryogenen Fördermediums zurückgeführt werden.The lower, i.e. The roller bearing, which is closer to the pump housing or on the pump housing side, is also supplied with the branched-off part of the cryogenic conveying medium, since there is sufficient play between the roller bearing housing and the shaft for the cryogenic conveying medium to pass through at this point. At the point of exit from the lower roller bearing, the branched-off part of the cryogenic delivery medium can be returned to the main delivery flow of the cryogenic delivery medium along the motor shaft and via a gap above the impeller designed as an impeller.

Im Weiteren ist aus der DE 1 801 864 eine weitere Zentrifugalpumpe zum Fördern eines kryogenen Mediums bekannt, bei welcher auf der Druckseite ein Teil des kryogenen Fördermediums vom Hauptförderstrom abgezweigt wird und über ein ausserhalb der Pumpe sich befindliches Rohrleitungssystem zu einem oberhalb des oberen Rollenlagers sich befindlichen Anschlussstutzen.Furthermore, from the DE 1 801 864 Another centrifugal pump for delivering a cryogenic medium is known, in which a part of the cryogenic delivery medium is branched off from the main delivery flow on the pressure side and via a pipe system located outside the pump to a connection piece located above the upper roller bearing.

Eine einstückige Welle, welche sowohl als Motorwelle wie auch als Pumpenwelle fungiert, weist in DE 1 801 864 eine sich zwischen den Rollenlagern erstreckende Bohrung auf, womit in diesem Bereich der Welle ein Hohlraum ausgebildet ist. Zwischen dem Anschlussstutzen in dem Hohlraum in der Welle existiert eine kommunizierende Verbindung. Über zusätzliche Bohrungen in der Welle wird zudem zwischen diesem Hohlraum der Welle und den Rollenlagern eine kommunizierende Verbindung geschaffen.
Die aus US 3,652,186 und DE 1 801 864 bekannten Zentrifugalpumpen haben jedoch den Nachteil, dass eine Vielzahl von Rohrleitungen, d.h. vergleichsweise lange Wege, notwendig sind, damit der abgezweigte Teil des kryogenen Fördermediums zu den Rollenlagern und wieder zurück in den Hauptförderstrom des kryogenen Fördermediums gelangen kann.A one-piece shaft, which functions both as a motor shaft and as a pump shaft, shows in DE 1 801 864 a bore extending between the roller bearings, whereby a cavity is formed in this area of the shaft. A communicating connection exists between the connection piece in the cavity in the shaft. Via additional holes in the shaft, a communicating connection is also created between this cavity of the shaft and the roller bearings.
From US 3,652,186 and DE 1 801 864 However, known centrifugal pumps have the disadvantage that a large number of pipes, ie comparatively long distances are necessary so that the branched-off part of the cryogenic medium can get to the roller bearings and back into the main flow of the cryogenic medium.

Darstellung der ErfindungPresentation of the invention

Die vorliegende Erfindung hat sich zur Aufgabe gestellt, eine Zentrifugalpumpe bereitzustellen, welche die Nachteile des bekannten Standes der Technik überwindet und insbesondere den konstruktiven Aufbau der Zentrifugalpumpe möglichst einfach hält.The object of the present invention is to provide a centrifugal pump which overcomes the disadvantages of the known prior art and in particular keeps the design of the centrifugal pump as simple as possible.

Diese Aufgaben erfüllt eine Zentrifugalpumpe mit den Merkmalen des Patentanspruches 1.A centrifugal pump fulfills these tasks with the features of claim 1.

Erfindungsgemäss ist zwischen der Druckseite im Pumpengehäuse und dem pumpengehäuseseitigen Rollenlager eine erste kommunizierende Verbindung, insbesondere ein direkter Verbindungskanal, ausgebildet für einen abgezweigten Teil des kryogenen Fördermediums zum Rollenlager, und zwischen dem pumpengehäuseseitigen Rollenlager und der Saugseite ist eine zweite kommunizierende Verbindung ausgebildet für den abgezweigten Teils des kryogenen Fördermediums zurück zur Saugseite im Pumpengehäuse, so dass eine Zirkulation des abgezweigten Teils der kryogenen Fördermediums zwischen Pumpengehäuse und einzig dem pumpengehäuseseitigen Rollenlager gewährleistet wird.According to the invention, a first communicating connection, in particular a direct connection channel, is formed between the pressure side in the pump housing and the roller bearing on the pump housing, for a branched part of the cryogenic delivery medium to the roller bearing, and a second communicating connection is formed for the branched part between the roller housing on the pump housing side and the suction side of the cryogenic delivery medium back to the suction side in the pump housing, so that circulation of the branched-off part of the cryogenic delivery medium between the pump housing and only the roller bearing on the pump housing side is ensured.

Eine solche Zirkulation zwischen der Druckseite und einzig dem pumpengehäuseseitigen Rollenlager innerhalb der erfindungsgemässen Zentrifugalpumpe hat sich als besonders vorteilhaft erwiesen, da sich dadurch eine kryogene Schmierung mit einer einfachen Konstruktion der Pumpe vereinbaren lässt. Beispielsweise kann auf ausserhalb des Pumpengehäuses angeordnete Rohrleitungen - im Gegensatz zu den aus US 3,652,186 und DE 1 801 864 bekannten Zentrifugalpumpen - verzichtet werden, womit das Risiko von Leckverlusten vermieden werden kann.Such a circulation between the pressure side and only the roller bearing on the pump housing side within the centrifugal pump according to the invention has proven to be particularly advantageous since cryogenic lubrication can be reconciled with a simple construction of the pump. For example, in contrast to the pipelines arranged outside the pump housing out US 3,652,186 and DE 1 801 864 known centrifugal pumps - can be dispensed with, with which the risk of leakage losses can be avoided.

Im Sinne der vorliegenden Erfindung wird unter einem direkten Verbindungskanal zwischen Druckseite im Pumpengehäuse und dem pumpengehäuseseitigen Rollenlager als erste kommunizierende Verbindung verstanden, dass im Gegensatz zur Zentrifugalpumpe aus der DE 1801864 keine indirekte Verbindung mit dem pumpengehäuseseitigen Rollenlager über das dem Pumpenrad entferntere, antriebsmotorseitige Rollenlager ausgebildet ist.In the sense of the present invention, a direct connection channel between the pressure side in the pump housing and the roller bearing on the pump housing side is understood as the first communicating connection that, in contrast to the centrifugal pump, consists of the DE 1801864 no indirect connection is made with the roller bearing on the pump housing via the roller bearing on the drive motor side, which is further away from the impeller.

Gemäss der erfindungsgemässen Lösung einer Zentrifugalpumpe für kryogene Fördermedien kann das zur Schmierung und Kühlung abgezweigte, kryogene Fördermedium in einem vergleichsweise kleinräumigen Kreis zirkulieren. Dadurch können Verluste des abgezweigten, kryogenen Fördermediums gering gehalten werden.According to the inventive solution of a centrifugal pump for cryogenic delivery media, the cryogenic delivery medium branched off for lubrication and cooling can circulate in a comparatively small-scale circle. Losses of the branched, cryogenic delivery medium can thereby be kept low.

Im Weiteren ist es notwendig, dass das kryogene Fördermedium im Bereich des ungeschmierten, pumpengehäuseseitigen Rollenlagers nicht verdampft, was vorzugsweise durch Verhinderung des Unterschreitens eines gewissen Mindestdrucks ermöglicht wird. Ein Verdampfen des kryogenen Fördermediums im Bereich der Rollenlager kann die Rollenlager beschädigen. Ein vergleichsweise kleinräumiger Zirkulationskreis ist vorteilhaft, da hierdurch die Aufrechterhaltung des notwendigen Mindestdrucks durch die Konstruktion gewährleistet ist.Furthermore, it is necessary for the cryogenic delivery medium not to evaporate in the region of the unlubricated roller bearing on the pump housing side, which is preferably made possible by preventing the pressure from falling below a certain minimum pressure. Evaporation of the cryogenic medium in the area of the roller bearings can damage the roller bearings. A comparatively small-scale circulation circuit is advantageous since it ensures that the necessary minimum pressure is maintained by the construction.

Im Sinne der vorliegenden Erfindung können als kryogenes Fördermedium beispielsweise Flüssiggase wie flüssige Kohlenwasserstoffe wie beispielsweise flüssiges Methan, flüssiger Stickstoff etc. verwendet werden. Unter Flüssiggas wird ein durch Kühlung und Kompression verflüssigtes Gas verstanden. Es hat sich gezeigt, dass gerade flüssige Kohlenwasserstoffe gute Schmiereigenschaften besitzen und sich deshalb für eine kryogene Schmierung besonders gut eignen.For the purposes of the present invention, liquid gases such as liquid hydrocarbons such as liquid methane, liquid nitrogen etc. can be used as the cryogenic delivery medium. Liquid gas is understood to mean a gas liquefied by cooling and compression. It has been shown that liquid Hydrocarbons have good lubricating properties and are therefore particularly well suited for cryogenic lubrication.

Weitere vorteilhafte Ausgestaltungsformen sind in den abhängigen Patentansprüchen angegeben.Further advantageous embodiments are specified in the dependent claims.

Vorzugsweise befindet sich zwischen dem Motorgehäuse und dem Pumpengehäuse ein Zwischenstück in Form eines Gehäusedeckels, wobei der Gehäusedeckel einen Verbindungskanal in Form einer Bohrung zwischen der Druckseite und dem pumpengehäuseseitigen Rollenlager aufweist zur Bildung der ersten kommunizierenden Verbindung.An intermediate piece in the form of a housing cover is preferably located between the motor housing and the pump housing, the housing cover having a connecting channel in the form of a bore between the pressure side and the roller bearing on the pump housing side to form the first communicating connection.

Bevorzugt ist ein Dichtungselement zwischen dem pumpengehäuseseitigen Gehäusedeckel und der Welle derart dichtend angeordnet, um eine Barriere zwischen Pumpengehäuse und dem Motorgehäuse zu erzielen. Im Gegensatz zu den aus US 3,652,186 und DE 1801864 bekannten Zentrifugalpumpen kann es sich beim antriebsmotorseitigen bei der erfindungsgemässen Zentrifugalpumpe vorzugsweise um ein konventionelles, geschmiertes Rollenlager handeln. Das als Barriere für des kryogene Fördermedium dienende Dichtungselement vermeidet damit vorteilhaft die bekannten Probleme, welche bei Inkontaktbringen des kryogenen Fördermediums mit geschmierten Rollenlagern auftreten, und zwingt zudem den abgezweigten Teil über die zweite kommunizierende Verbindung zurück in den Hauptförderstrom des kryogenen Fördermediums.A sealing element is preferably arranged between the housing cover on the pump housing side and the shaft in a sealing manner in order to achieve a barrier between the pump housing and the motor housing. Unlike the ones from US 3,652,186 and DE 1801864 In known centrifugal pumps, the drive motor side in the centrifugal pump according to the invention is preferably a conventional, lubricated roller bearing. The sealing element serving as a barrier to the cryogenic delivery medium thus advantageously avoids the known problems that occur when the cryogenic delivery medium comes into contact with lubricated roller bearings, and also forces the branched part back into the main delivery flow of the cryogenic delivery medium via the second communicating connection.

Vorzugsweise ist die erfindungsgemässe Zentrifugalpumpe für den Gebrauch in einer horizontalen Lage ausgelegt und damit geeignet, um beispielsweise an einem Lastkraftwagen (LKW) angebracht zu werden.The centrifugal pump according to the invention is preferably designed for use in a horizontal position and is therefore suitable for being attached, for example, to a truck (truck).

Bevorzugt weist das Motorgehäuse, insbesondere an einer beim Gebrauch in horizontaler Lage am tiefsten gelegenen Stelle, eine Austrittsbohrung auf, wobei an der Austrittsbohrung eine zur Saugseite verlaufende Druckausgleichsleitung anbringbar ist. Eine solche Austrittsbohrung mit einer daran angebrachten Druckausgleichsleitung erlaubt vorteilhaft ein Entfernen von unerwünscht im Motorgehäuse vorhandenem kryogenem Fördermedium, welches beispielsweise aufgrund einer mangelhaften Barrierewirkung beispielsweise aufgrund einer Beschädigung oder Verschleiss des Dichtungselements zwischen dem pumpengehäuseseitigen Gehäusedeckel und der Welle in das Motorgehäuse gelangt ist.The motor housing preferably has an outlet bore, in particular at a point at the lowest point in use in a horizontal position, one on the outlet bore toward the suction side running pressure equalization line can be attached. Such an outlet bore with a pressure compensation line attached to it advantageously allows removal of undesirable cryogenic delivery medium which is present in the motor housing and which, for example, due to an inadequate barrier effect, for example due to damage or wear of the sealing element between the pump housing-side housing cover and the shaft, has entered the motor housing.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Ein bevorzugtes Ausführungsbeispiel des Erfindungsgegenstandes wird nachstehend im Zusammenhang mit den anliegenden Zeichnungen beschrieben. Es zeigen:

Fig. 1
einen Längsschnitt durch ein bevorzugtes Ausführungsbeispiel der erfindungsgemässen Zentrifugalpumpe.
A preferred embodiment of the subject matter of the invention is described below in connection with the accompanying drawings. Show it:
Fig. 1
a longitudinal section through a preferred embodiment of the centrifugal pump according to the invention.

Beschreibungdescription

Fig. 1 zeigt einen Längsschnitt durch ein bevorzugtes Ausführungsbeispiel der erfindungsgemässen Zentrifugalpumpe 1. Die Zentrifugalpumpe 1 hat ein Motorgehäuse für eine elektrische Antriebsmotoreinheit 12 sowie ein Pumpengehäuse 2 zur Aufnahme der Pumpenelemente. Im vorliegenden bevorzugten Ausführungsbeispiel handelt es sich um eine einstufige Impeller-Pumpe mit nur einem Pumpenrad 5, wobei es sich auch um eine mehrstufige Impeller-Pumpe mit mehreren Pumpenrädern 5 handeln kann. Fig. 1 shows a longitudinal section through a preferred embodiment of the centrifugal pump 1 according to the invention. The centrifugal pump 1 has a motor housing for an electric drive motor unit 12 and a pump housing 2 for receiving the pump elements. In the present preferred exemplary embodiment, it is a single-stage impeller pump with only one impeller 5, and it can also be a multi-stage impeller pump with several impellers 5.

Die Antriebsmotoreinheit 12 hat eine Welle 11, die in zwei Rollenlagern 20; 21 gelagert ist. Ein antriebsmotorseitiges, d.h. dem Pumpenrad 5 beziehungsweise Pumpengehäuse 2 entfernteres, Rollenlager 20 ist hierbei in einem antriebsmotorseitigen Gehäusedeckel 9 gelagert. Im vorliegenden, bevorzugten Ausführungsbeispiel handelt es sich bei der Welle 11 um eine einstückige Welle, welche sowohl als Motorwelle wie auch als Pumpenwelle fungiert. Alternativ ist auch eine Bauform der Zentrifugalpumpe 1 mit einer nicht einstückigen Welle denkbar, bei welcher eine Motorwelle mit einer Pumpenwelle über eine Kupplung verbunden werden kann. An dem dem Pumpengehäuse 2 zugewandten freien Ende der Welle 11 sind hier mittels einer Fixierschraube 7 sowohl ein Pumpenrad 5 wie auch ein als Flügelrad ausgestaltetes Laufrad 6 befestigt. Das Pumpenrad 5 ist hier beispielhaft als eine spiralförmige Förderschaufel ausgebildet.The drive motor unit 12 has a shaft 11 which in two roller bearings 20; 21 is stored. A drive motor side, i.e. Roller bearing 20, which is more distant from the pump wheel 5 or pump housing 2, is mounted in a housing cover 9 on the drive motor side. In the present, preferred exemplary embodiment, the shaft 11 is a one-piece shaft which functions both as a motor shaft and as a pump shaft. Alternatively, a design of the centrifugal pump 1 with a shaft that is not in one piece is also conceivable, in which a motor shaft can be connected to a pump shaft via a coupling. On the free end of the shaft 11 facing the pump housing 2, both a pump wheel 5 and an impeller 6 designed as an impeller are fastened here by means of a fixing screw 7. The pump wheel 5 is designed here, for example, as a spiral conveyor blade.

Wie in Fig. 1 ersichtlich ist am Pumpengehäuse 2 auf der Eintrittsöffnung E beziehungsweise Saugseite S ein Saugflansch 4 für die Ansaugung des Hauptförderstroms FH des kryogenen Fördermediums angeordnet. Auf der im Wesentlichen selben axialen Position wie das Pumpengehäuse 2 sowie im Wesentlichen rechtwinklig zur Eintrittsseite E ist hier die Austrittseite mit einem Auslassflansch für den Ausstoss des Hauptförderstroms FH des kryogenen Fördermediums angeordnet (nicht ersichtlich in Fig. 1).As in Fig. 1 a suction flange 4 is arranged on the pump housing 2 on the inlet opening E or suction side S for the suction of the main delivery flow F H of the cryogenic delivery medium. At the essentially same axial position as the pump housing 2 and essentially at right angles to the inlet side E, the outlet side is arranged here with an outlet flange for the discharge of the main delivery flow F H of the cryogenic delivery medium (not visible in FIG Fig. 1 ).

Zwischen Motorgehäuse 10 und Pumpengehäuse 2 befindet sich ein Zwischenstück in Form eines Gehäusedeckels 15, wobei dieser Gehäusedeckel 15 mit geeigneten Fixiermitteln eine feste Verbindung zwischen dem Motorgehäuse 10 und dem Pumpengehäuse 2 herstellt. Der Gehäusedeckel 15 hat Adapter- und Trennfunktion. Im Gehäusedeckel 15 ist das pumpengehäuseseitige, d.h. dem Pumpengehäuse 2 beziehungsweise Pumpenrad 5 näher gelegene, Rollenlager 21 gelagert. Gemäss dem hier gezeigten, bevorzugten Ausführungsbeispiel ist vorzugsweise zwischen dem Gehäusedeckel 15 und dem Motorgehäuse 10 eine Isolierscheibe 19 angeordnet.Between the motor housing 10 and the pump housing 2 there is an intermediate piece in the form of a housing cover 15, this housing cover 15 producing a fixed connection between the motor housing 10 and the pump housing 2 using suitable fixing means. The housing cover 15 has an adapter and separation function. In the housing cover 15, the pump housing side, i.e. the roller housing 21 mounted closer to the pump housing 2 or pump wheel 5. According to the preferred exemplary embodiment shown here, an insulating disk 19 is preferably arranged between the housing cover 15 and the motor housing 10.

Zwischen der Druckseite D im Pumpengehäuse 2 und dem pumpengehäuseseitigen Rollenlager 21 ist eine erste kommunizierende Verbindung insbesondere als ein direkter Verbindungskanal 16, ausgebildet für einen abgezweigten Teil FA1 vom Hauptförderstrom FH des kryogenen Fördermediums. Der Verbindungskanal 16 wird hier in Form einer Bohrung im Gehäusedeckel 15 gebildet und erstreckt sich hier beispielhaft zwischen Rollenlager 21 quer nach aussen bis zu einem äusseren radialen Bereich des Pumpengehäuses 2. In Fig.1 wird nur ein Verbindungskanal 16 gezeigt, wobei durchaus eine oder mehrere Verbindungskanäle 16 je nach Bedarf vorhanden sein können.Between the pressure side D in the pump housing 2 and the roller bearing 21 on the pump housing side, there is a first communicating connection, in particular as a direct connection channel 16, designed for a branched part F A1 of the main delivery flow F H of the cryogenic delivery medium. The connecting channel 16 is formed here in the form of a bore in the housing cover 15 and extends here, for example, between roller bearings 21 transversely outwards to an outer radial region of the pump housing 2 Fig. 1 only one connection channel 16 is shown, it being possible for one or more connection channels 16 to be present as required.

Während des Betriebs der Zentrifugalpumpe 1 erhöht sich aufgrund der Zentrifugalkräfte ein Druck P2 auf der Druckseite D im äusseren radialen Bereich des Pumpengehäuses 2 gegenüber einem Druck P1 bei der Saugseite S in einem inneren radialen Bereich des Pumpengehäuses 2. Der Druck P2 auf der Druckseite D entspricht üblicherweise dem zu erzielenden Druck des austretenden Hauptförderstroms FH des kryogenen Fördermediums. Mit anderen Worten bildet sich ein Druckgradient, wobei gilt: P2 > P1. Dieser Druckgradient bewirkt ein Abzweigen eines Teils FA1 vom Hauptförderstrom FH des kryogenen Fördermediums in Richtung des Rollenlagers 21 und dadurch ein Durchströmen beziehungsweise eine kryogene Schmierung und Kühlung des Rollenlagers 21. Mit anderen Worten wird die Zirkulation durch den Druckgradienten beziehungsweise die Druckdifferenz zwischen Druckseite D und Saugseite S gewährleistet. Es hat sich gezeigt, dass in der erfindungsgemässen Zentrifugalpumpe 1 ein Druckgradient bzw. eine Druckdifferenz zwischen P1 und P2 von 0,8 bis 8 bar einstellbar sein kann, wobei dieser Druckgradient insbesondere durch die Pumpengeschwindigkeit sowie den Durchmesser des Laufrades beeinflussbar ist.
Zwischen dem Rollenlager 21 und der Saugseite S im Pumpengehäuse 2 ist eine zweite kommunizierende Verbindung ausgebildet für die Rückführung des abgezweigten Teils FA2 des kryogenen Fördermediums zurück zur Saugseite S im Pumpengehäuse 2 , so dass eine Zirkulation des abgezweigten Teils FA1; FA2 des kryogenen Fördermediums zwischen der Druckseite D im Pumpengehäuse 2 über das pumpengehäuseseitige Rollenlager 21 zurück zur Saugseite S gewährleistet wird. Gemäss der hier in Fig.1 gezeigten, bevorzugten Ausführungsform ist die zweite kommunizierende Verbindung in Form mindestens einer unteren Öffnung O2 des pumpengehäuseseitigen Rollenlagers 21 ausgestaltet und kann so zu einer oberen Saugseite S1 gelangen. Im Weiteren beinhaltet die zweite kommunizierende Verbindung hier beispielhaft gestrichelt angedeutet mindestens eine Bohrung B im Laufrad 6, wodurch der abgezweigte Teil FA2 des kryogenen Fördermediums von einer oberen Saugseite S1 zurück zur Saugseite S gelangen kann. Es hat sich gezeigt, dass zwischen der oberen Saugseite S1 ein leicht höherer Druck existiert als der Druck P1 auf der Saugseite S, wodurch der abgezweigte Teil FA2 des kryogenen Fördermediums wieder in den Hauptförderstrom FH des kryogenen Fördermediums gelangen kann.During operation of the centrifugal pump 1, a pressure P 2 on the pressure side D in the outer radial region of the pump housing 2 increases compared to a pressure P 1 on the suction side S in an inner radial region of the pump housing 2 due to the centrifugal forces. The pressure P 2 on the Pressure side D usually corresponds to the pressure to be achieved of the emerging main delivery flow F H of the cryogenic delivery medium. In other words, a pressure gradient is formed, where: P 2 > P 1 . This pressure gradient causes a part F A1 to branch off from the main delivery flow F H of the cryogenic delivery medium in the direction of the roller bearing 21 and thereby Flow or cryogenic lubrication and cooling of the roller bearing 21. In other words, the circulation is ensured by the pressure gradient or the pressure difference between pressure side D and suction side S. It has been shown that a pressure gradient or a pressure difference between P 1 and P 2 of 0.8 to 8 bar can be adjustable in the centrifugal pump 1 according to the invention, this pressure gradient being able to be influenced in particular by the pump speed and the diameter of the impeller.
Between the roller bearing 21 and the suction side S in the pump housing 2, a second communicating connection is formed for the return of the branched part F A2 of the cryogenic conveying medium back to the suction side S in the pump housing 2, so that a circulation of the branched part F A1 ; F A2 of the cryogenic delivery medium between the pressure side D in the pump housing 2 via the roller housing 21 on the pump housing back to the suction side S is ensured. According to the one in here Fig. 1 In the preferred embodiment shown, the second communicating connection is designed in the form of at least one lower opening O 2 of the roller bearing 21 on the pump housing side and can thus reach an upper suction side S 1 . Furthermore, the second communicating connection contains at least one bore B in the impeller 6, which is indicated here by dashed lines, as a result of which the branched part F A2 of the cryogenic delivery medium can return from an upper suction side S 1 to the suction side S. It has been shown that there is a slightly higher pressure between the upper suction side S 1 than the pressure P 1 on the suction side S, as a result of which the branched part F A2 of the cryogenic delivery medium can get back into the main delivery flow F H of the cryogenic delivery medium.

Ein ringförmig ausgestaltetes, die Welle 11 umschliessendes Dichtungselement 18 ist zwischen dem Gehäusedeckel 15 und der Welle 11 derart dichtend angeordnet, um eine Barriere zwischen Pumpengehäuse 2 und dem Motorgehäuse 10 zu erzielen. Dieses Dichtungselement 18 zwingt - wie in Fig. 1 ersichtlich in die dem Motorgehäuse 10 abgewandte Richtung - den abgezweigten Teil FA2 des kryogenen Fördermediums über die zweite kommunizierende Verbindung zurück in den Hauptförderstrom FH des kryogenen Fördermediums. Das in Fig. 1 gezeigte, bevorzugte Ausführungsbeispiel weist zudem beispielhaft - zusätzlich zum Dichtungselement 18 - eine Labyrinthdichtung 17 zwischen dem ungeschmierten Rollenlager 21 und dem Dichtungselement 18 auf. Die erfindungsgemässe Zentrifugalpumpe 1 erlaubt durch einen Spalt zwischen der Labyrinthdichtung 17 und dem Rollenlager 21 einen Durchfluss des abgezweigten Teils FA1 des kryogenen Fördermediums, so dass der abgezweigte Teil FA1 des kryogenen Fördermediums über mindestens eine obere Öffnung O1 in das Rollenlager 21 gelangen und anhand des kryogenen Fördermediums geschmiert werden kann.A ring-shaped sealing element 18, which surrounds the shaft 11, is arranged between the housing cover 15 and the shaft 11 so as to seal around a barrier between the pump housing 2 and the motor housing 10 to achieve. This sealing element 18 forces - as in Fig. 1 evident in the direction facing away from the motor housing 10 - the branched-off part F A2 of the cryogenic delivery medium via the second communicating connection back into the main delivery flow F H of the cryogenic delivery medium. This in Fig. 1 The preferred exemplary embodiment shown also has, by way of example - in addition to the sealing element 18 - a labyrinth seal 17 between the unlubricated roller bearing 21 and the sealing element 18. The centrifugal pump 1 according to the invention allows the branched part F A1 of the cryogenic conveying medium to flow through a gap between the labyrinth seal 17 and the roller bearing 21, so that the branched part F A1 of the cryogenic conveying medium reaches the roller bearing 21 via at least one upper opening O 1 and can be lubricated using the cryogenic fluid.

Idealerweise ist die Zentrifugalpumpe 1 ausgelegt beziehungsweise dazu geeignet, um in horizontaler Lage, d.h. bei einer horizontal ausgerichteten Längsachse der Welle 11, für den Gebrauch beispielsweise an einem LKW betrieben zu werden. Beispielsweise ist die Zentrifugalpumpe 1 vorzugweise derart ausgestaltet, so dass die in Fig.1 gezeigte, Austrittsbohrung 13 im Motorgehäuse 10 an einer in Schwerkraftrichtung betrachtet am tiefsten gelegenen Stelle ausgerichtet und angeordnet ist, wodurch unerwünscht sich im Motorgehäuse 10, befindliches flüssiges kryogenes Fördermedium an dieser Stelle sammeln kann. Wie in Fig.1 durch eine gestrichelte Linie angedeutet ist bevorzugt eine Druckausgleichsleitung 14 an der Austrittsbohrung 13 sowie an einer Bohrung 3 im Saugflansch 4 des Pumpengehäuses 2 dichtend angebracht. Eine derart angebrachte Druckausgleichsleitung 14 ist vorteilhaft, da das flüssige, kryogene Fördermedium aus dem Inneren des Motorgehäuses 10 in Richtung Saugseite S bei der Eintrittsöffnung E gezwungen wird. Eine solche Austrittsbohrung 13 mit einer daran angebrachten Druckausgleichsleitung 14 erlaubt vorteilhaft ein Entfernen von unerwünscht im Motorgehäuse 10 vorhandenem flüssigem kryogenem Fördermedium, welches beispielsweise aufgrund einer mangelhaften Barrierewirkung beispielsweise aufgrund einer Beschädigung oder Verschleiss des Dichtungselements 18 zwischen dem pumpengehäuseseitigen Gehäusedeckel 15 und der Welle 11 in das Motorgehäuse 10 gelangt ist.The centrifugal pump 1 is ideally designed or suitable to be operated in a horizontal position, ie with a horizontally oriented longitudinal axis of the shaft 11, for use on a truck, for example. For example, the centrifugal pump 1 is preferably configured such that the in Fig. 1 shown, exit bore 13 in the motor housing 10 is aligned and arranged at a lowest point viewed in the direction of gravity, whereby undesired liquid cryogenic delivery medium located in the motor housing 10 can collect at this point. As in Fig. 1 indicated by a dashed line, a pressure compensation line 14 is preferably sealingly attached to the outlet bore 13 and to a bore 3 in the suction flange 4 of the pump housing 2. Such a pressure equalization line 14 is advantageous because the liquid, cryogenic delivery medium is forced out of the interior of the motor housing 10 in the direction of the suction side S at the inlet opening E. Such an outlet bore 13 with a pressure compensation line 14 attached to it advantageously allows removal of liquid cryogenic that is undesirably present in the motor housing 10 Delivery medium, which has reached the motor housing 10 between the pump housing-side housing cover 15 and the shaft 11, for example due to a defective barrier effect, for example due to damage or wear of the sealing element 18.

Das ungeschmierte Rollenlager 21 im Gehäusedeckel 15 umfasst hier eine Vielzahl von Kugeln 23, einen inneren Laufring 25 sowie einen äusseren Laufring 27 jeweils mit Laufflächen, zwischen denen die Kugeln 23 angeordnet sind, wobei hier die Kugeln 23 aus Keramik gefertigt sein können. Die Laufringe 25; 27 sind bevorzugt aus Stahl gefertigt und weisen idealerweise im Bereich der Laufflächen eine chrombasierte Beschichtung auf.The unlubricated roller bearing 21 in the housing cover 15 here comprises a plurality of balls 23, an inner race 25 and an outer race 27 each with running surfaces between which the balls 23 are arranged, in which case the balls 23 can be made of ceramic. The races 25; 27 are preferably made of steel and ideally have a chrome-based coating in the area of the treads.

Ein solches ungeschmiertes Rollenlager 21 beziehungsweise Kugellager wird auch als ein Hybridlager bezeichnet, bei dem für die Laufringe 25; 27 und die Kugeln 23 (auch Wälzkörper genannt) unterschiedliche Materialien eingesetzt werden. Die häufigste Bauart ist die des Rillenkugellagers mit herkömmlichen Laufringen 25; 27 aus Stahl und Kugeln 23 aus einer hochfesten Keramik, meistens Siliciumnitrid.Such an unlubricated roller bearing 21 or ball bearing is also referred to as a hybrid bearing, in which for the races 25; 27 and the balls 23 (also called rolling elements) different materials are used. The most common type is that of a deep groove ball bearing with conventional races 25; 27 made of steel and balls 23 made of a high-strength ceramic, mostly silicon nitride.

Beim Rollenlager 20 im antriebsmotorseitigen Gehäusedeckel 9 kann identisch wie das Rollenlager 21 gefertigt sein, es kann sich aber aus Kostengründen vorteilhaft auch um ein konventionelles, geschmiertes Rollenlager handeln.The roller bearing 20 in the housing cover 9 on the drive motor side can be manufactured identically to the roller bearing 21, but for cost reasons it can also advantageously be a conventional, lubricated roller bearing.

Der gegenseitige Abstand der Kugeln 23 im ungeschmierten Rollenlager 21 wird durch einen Käfig (nicht gezeigt in Fig.1) gewährleistet, welcher für jede Kugel 23 eine separate Kammer aufweist. Die Innenflächen der Kammern sind vorzugsweise zylindrisch und der Zylinderdurchmesser wird etwas grösser als der Durchmesser der Kugeln 23 gewählt, so dass die Kugeln frei in dem Käfig rotieren können. Bevorzugt ist dieser Käfig aus verstärktem PTFE (Polytetrafluorethylen) gefertigt. Alternativ oder zusätzlich kann dieser Käfig auch aus Edelstahl, Polyetheretherketon (PEEK), Messing oder beliebige Kombinationen hiervon hergestellt sein.The mutual spacing of the balls 23 in the unlubricated roller bearing 21 is determined by a cage (not shown in FIG Fig. 1 ) which has a separate chamber for each ball 23. The inner surfaces of the chambers are preferably cylindrical and the cylinder diameter is chosen to be somewhat larger than the diameter of the balls 23, so that the balls can rotate freely in the cage. Preferably, this cage is made of reinforced PTFE (P oly t etra f luor e Thylen). Alternatively or additionally, this cage can also be made of stainless steel, polyether ether ketone (PEEK), brass or any combination thereof.

BezugszeichenlisteReference symbol list

11
Zentrifugalpumpecentrifugal pump
22nd
PumpengehäusePump housing
33rd
Bohrung (im Pumpengehäuse)Hole (in the pump housing)
44th
SaugflanschSuction flange
55
PumpenradImpeller
66
LaufradWheel
77
FixierschraubeFixing screw
99
antriebsmotorseitiger Gehäusedeckelhousing cover on the drive motor side
1010th
MotorgehäuseEngine housing
1111
Wellewave
1212
AntriebsmotoreinheitDrive motor unit
1313
Austrittsbohrung (im Motorgehäuse)Outlet hole (in the motor housing)
1414
Druckausgleichsleitung (zwischen Saugseite und Druckseite)Pressure equalization line (between suction side and pressure side)
1515
pumpengehäuseseitiger GehäusedeckelPump cover on the housing side
1616
Verbindungskanal (für abgezweigtes, kryogenes Medium)Connection channel (for branched, cryogenic medium)
1717th
LabyrinthdichtungLabyrinth seal
1818th
DichtungselementSealing element
1919th
IsolierscheibeInsulating washer
2020th
antriebsmotorseitiges Rollenlagerroller bearing on the drive motor side
2121st
pumpengehäuseseitiges RollenlagerRoller bearing on the pump housing side
2222
Kugel (oberes Rollenlager)Ball (upper roller bearing)
2323
Kugel (unteres Rollenlager)Ball (lower roller bearing)
2424th
innerer Laufring (oberes Rollenlager)inner race (upper roller bearing)
2525th
innerer Laufring (unteres Rollenlager)inner race (lower roller bearing)
2626
äusserer Laufring (oberes Rollenlager)outer race (upper roller bearing)
2727th
äusserer Laufring (unteres Rollenlager)outer race (lower roller bearing)
AA
AustrittsöffnungOutlet opening
BB
Bohrung (im Laufrad)Bore (in the impeller)
DD
DruckseitePrinted page
EE
EintrittsöffnungEntrance opening
FA1 F A1
Abgezweigtes, kryogenes Fördermedium (Druckseite zum Rollenlager)Branched, cryogenic medium (pressure side to the roller bearing)
FA2 F A2
Abgezweigtes, kryogenes Fördermedium (Rollenlager zur Druckseite)Branched, cryogenic medium (roller bearing to the pressure side)
FH F H
Hauptförderstrom kryogenes FördermediumMain flow cryogenic medium
LL
LängsachseLongitudinal axis
O1 O 1
Obere Öffnung (des pumpengehäuseseitigen Rollenlagers)Upper opening (of the roller bearing on the pump housing)
O2 O 2
Untere Öffnung (des pumpengehäuseseitigen Rollenlagers)Lower opening (of the roller bearing on the pump housing)
SS
SaugseiteSuction side
S1 S 1
Obere SaugseiteUpper suction side

Claims (11)

  1. A rotating, directly-driven single or multi-stage centrifugal pump (1) for cryogenic liquids, with a pump housing (2) for the pump (1) and an electric drive motor unit (12), serving as the pump drive, in a motor housing (10),
    wherein a shaft (11) of the drive motor unit (12) is borne on two bearings, more particularly roller bearings (20; 21), and wherein at least one roller bearing (20; 21) is an unlubricated roller bearing,
    characterised in that
    between the pressure side (D) in the pump housing (2) and the roller bearing (21) on the pump housing side, at least one first communicating connection, in particular a direct communication channel (16), is formed for a branched-off part (FA1) of the main flow (FH) of the cryogenic conveyed medium to the roller bearing (21), and
    in that between the roller bearing (21) on the pump housing side and the suction side (S), a second communicating connection is formed for the branched-off part (FA2) of the cryogenic conveyed flow back to the suction side (S) into the main flow (FH) of the cryogenic conveyed medium,
    so that a circulation of the branched part-off part (FA1; FA2) of the cryogenic medium is guaranteed between the pressure side (D) in the pump housing (2) and solely the roller bearing (21) on the pump housing side.
  2. The pump (1) according to claim 1,
    characterised in that
    between the motor housing (10) and the pump housing (2) there is an intermediate piece in the form of a housing lid (15), wherein the housing lied (15) comprises a connection channel (16) in the form of a drilled hole between the pressures side (D) in the pump housing (2) and the roller bearing (21) in the pump housing side for creating the first communicating connection.
  3. The pump (1) according to claim 2,
    characterised in that a sealing element (18) is arranged in a sealing manner between the housing lid (15) and the shaft (11) in such a way as to create a barrier between the pump housing (2) and the motor housing (10).
  4. The pump (1) according to any one of the preceding claims,
    characterised in that
    the pump (1) is designed to be used in a horizontal position.
  5. The pump (1) according to any one of the preceding claims,
    characterised in that
    the motor housing (10) comprises an outlet boring (13), in particular at the lowest point in the direction of gravity during use in the horizontal position, wherein at the outlet boring (13) a pressure equalisation line (14) between the motor housing (10) and the suction side (S) can be applied.
  6. The pump (1) according to any one of the preceding claims,
    characterised in that
    at least one roller bearing (20; 21), more particularly the unlubricated roller bearing (21) of the pump housing side is a hybrid bearing made of low-friction materials.
  7. The pump (1) according to claim 6,
    characterised in that
    inner and outer raceways (24; 25; 26; 27) of the roller bearing (20; 21), in particular of the roller bearing (21) on the pump housing side, are made of steel and in the area of the running surfaces have a chromium-based coating, and the balls (22; 23) of the roller bearing (20; 21), more particularly of the roller bearing (21) on the pump side, are made of ceramic material, in particular of silicon nitride (Si3N4) .
  8. The pump (1) according to claim 7,
    characterised in that
    the roller bearings (20; 21), more particularly the roller bearing (21) on the pump housing side, comprise a cage for spacing the balls (22; 23) with regard to each other, wherein through the cage a separate chamber is created for each ball (22; 23) and wherein the cage is made of reinforced polytetrafluorethylene (PTFE), stainless steel or polyether-ether ketone (PEEK) or brass or any combination thereof.
  9. A method of operating a pump (1) according to any one of the preceding claims comprising at least the procedural steps:
    starting up of the pump (1) for conveying a main flow (FH) of the cryogenic conveyed medium from an inlet opening (E) to an outlet opening (A),
    characterised in that
    during operation, between the pressure side (D) in the pump housing (2) and the roller bearing (21) on the pump housing side, a branched-off part (FA1) of the main flow (FH) of the cryogenic conveyed medium is conveyed to the roller bearing (21) via at least one first communicating channel, in particular a direct connection channel (16), and
    in that, via second communicating channel formed between the roller bearing (21) on the pump housing side and the suction side (S), the branched-off part (FA2) of the cryogenic conveyed medium back to the suction side (S) is conveyed into the main flow (FH),
    so that a circulation of the branched-off part (FA1; FA2) of the cryogenic conveyed medium is guaranteed between the pressure side (D) in the pump housing (2) and solely the roller bearing (21) on the pump housing side.
  10. The method according to claim 9,
    characterised in that
    during the operation of the centrifugal pump (1), on the basis of the centrifugal forces a pressure (P2) on the pressures side (D) in the outer radial area of the pump housing (2) increases compared with a pressure (P1) at the roller bearing (21) arranged in an inner radial area of the pump housing (2), so that this pressure gradient brings about a branching off of a part (FA1) of the main flow (FH) of the cryogenic conveyed medium in the direction of the roller bearing (21) via the at least one first communicating connection, and as a result a flow through or cryogenic lubrication and cooling of the roller bearing (21).
  11. The method according to any one of the claims 9 or 10,
    characterised in that
    on starting up, the pump (1) is installed in a horizonal position.
EP18192242.8A 2017-09-19 2018-09-03 Centrifugal pump for cryogenic feed media Active EP3460246B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH01152/17A CH714176A1 (en) 2017-09-19 2017-09-19 Centrifugal pump for cryogenic fluids.

Publications (2)

Publication Number Publication Date
EP3460246A1 EP3460246A1 (en) 2019-03-27
EP3460246B1 true EP3460246B1 (en) 2020-05-27

Family

ID=63490322

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18192242.8A Active EP3460246B1 (en) 2017-09-19 2018-09-03 Centrifugal pump for cryogenic feed media

Country Status (4)

Country Link
US (1) US10954952B2 (en)
EP (1) EP3460246B1 (en)
CN (1) CN209800276U (en)
CH (1) CH714176A1 (en)

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Also Published As

Publication number Publication date
CH714176A1 (en) 2019-03-29
US20190085858A1 (en) 2019-03-21
CN209800276U (en) 2019-12-17
US10954952B2 (en) 2021-03-23
EP3460246A1 (en) 2019-03-27

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