EP3460246B1 - Centrifugal pump for cryogenic feed media - Google Patents
Centrifugal pump for cryogenic feed media Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- roller bearing
- cryogenic
- pump housing
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 239000012526 feed medium Substances 0.000 title 1
- 238000007789 sealing Methods 0.000 claims description 12
- 239000007788 liquid Substances 0.000 claims description 10
- 238000005461 lubrication Methods 0.000 claims description 8
- 229910000831 Steel Inorganic materials 0.000 claims description 6
- 230000004888 barrier function Effects 0.000 claims description 6
- 239000010959 steel Substances 0.000 claims description 6
- 238000001816 cooling Methods 0.000 claims description 5
- 239000004696 Poly ether ether ketone Substances 0.000 claims description 4
- 229920002530 polyetherether ketone Polymers 0.000 claims description 4
- 229910052581 Si3N4 Inorganic materials 0.000 claims description 3
- HQVNEWCFYHHQES-UHFFFAOYSA-N silicon nitride Chemical compound N12[Si]34N5[Si]62N3[Si]51N64 HQVNEWCFYHHQES-UHFFFAOYSA-N 0.000 claims description 3
- 229910001369 Brass Inorganic materials 0.000 claims description 2
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 claims description 2
- 239000010951 brass Substances 0.000 claims description 2
- 239000011248 coating agent Substances 0.000 claims description 2
- 238000000576 coating method Methods 0.000 claims description 2
- 230000005484 gravity Effects 0.000 claims description 2
- 229910001220 stainless steel Inorganic materials 0.000 claims description 2
- 239000010935 stainless steel Substances 0.000 claims description 2
- 238000000034 method Methods 0.000 claims 3
- 229920001343 polytetrafluoroethylene Polymers 0.000 claims 2
- 229910010293 ceramic material Inorganic materials 0.000 claims 1
- 229910052804 chromium Inorganic materials 0.000 claims 1
- 239000011651 chromium Substances 0.000 claims 1
- 239000002783 friction material Substances 0.000 claims 1
- -1 polytetrafluorethylene Polymers 0.000 claims 1
- 241001131688 Coracias garrulus Species 0.000 description 67
- 239000000919 ceramic Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000000314 lubricant Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 229930195733 hydrocarbon Natural products 0.000 description 2
- 150000002430 hydrocarbons Chemical class 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Images
Classifications
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- 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
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.
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
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
Im Austrittsbereich, d.h. auf der Druckseite, der in
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
Eine einstückige Welle, welche sowohl als Motorwelle wie auch als Pumpenwelle fungiert, weist in
Die aus
From
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
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
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
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
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.
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.
- Fig. 1
- a longitudinal section through a preferred embodiment of the centrifugal pump according to the invention.
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
Wie in
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
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
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
Between the roller bearing 21 and the suction side S in the
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
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
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
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
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
Der gegenseitige Abstand der Kugeln 23 im ungeschmierten Rollenlager 21 wird durch einen Käfig (nicht gezeigt in
- 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)
- 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. - 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. - 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). - 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. - 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. - 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. - 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) . - 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. - 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 thatduring 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), andin 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.
- 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). - 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.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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CH01152/17A CH714176A1 (en) | 2017-09-19 | 2017-09-19 | Centrifugal pump for cryogenic fluids. |
Publications (2)
Publication Number | Publication Date |
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EP3460246A1 EP3460246A1 (en) | 2019-03-27 |
EP3460246B1 true EP3460246B1 (en) | 2020-05-27 |
Family
ID=63490322
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Application Number | Title | Priority Date | Filing Date |
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EP18192242.8A Active EP3460246B1 (en) | 2017-09-19 | 2018-09-03 | Centrifugal pump for cryogenic feed media |
Country Status (4)
Country | Link |
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US (1) | US10954952B2 (en) |
EP (1) | EP3460246B1 (en) |
CN (1) | CN209800276U (en) |
CH (1) | CH714176A1 (en) |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH389409A (en) * | 1960-12-05 | 1965-03-15 | Lederle Pumpen & Maschf | Multistage centrifugal pump driven by a canned motor |
US3369715A (en) * | 1966-05-10 | 1968-02-20 | J C Carter Company | Submerged pumping system |
US3494291A (en) | 1967-10-13 | 1970-02-10 | Air Reduction | Bearing assembly |
FR2032189A5 (en) * | 1969-02-21 | 1970-11-20 | Guinard Pompes | |
US3652186A (en) | 1970-05-25 | 1972-03-28 | Carter Co J C | Pressure lubricated, cooled and thrust balanced pump and motor unit |
US3975117A (en) * | 1974-09-27 | 1976-08-17 | James Coolidge Carter | Pump and motor unit with inducer at one end and centrifugal impeller at opposite end of the motor |
JPS51111902A (en) * | 1975-03-26 | 1976-10-02 | Iwaki:Kk | Magnet pump |
JPS5958197A (en) * | 1982-09-28 | 1984-04-03 | Nikkiso Co Ltd | Canned motor pump |
US4684329A (en) * | 1985-01-08 | 1987-08-04 | Nikkiso Co., Ltd. | Canned motor pump |
DE3718560A1 (en) * | 1987-06-03 | 1988-12-22 | Uhde Gmbh | DRY RUNNING ROLLER BEARINGS |
US5248245A (en) * | 1992-11-02 | 1993-09-28 | Ingersoll-Dresser Pump Company | Magnetically coupled centrifugal pump with improved casting and lubrication |
US6722854B2 (en) * | 2001-01-24 | 2004-04-20 | Sundyne Corporation | Canned pump with ultrasonic bubble detector |
AU2009351363B2 (en) * | 2009-08-18 | 2014-09-25 | Halliburton Energy Services, Inc. | Apparatus for downhole power generation |
JP5421826B2 (en) * | 2010-03-10 | 2014-02-19 | 大陽日酸株式会社 | Low temperature liquefied gas pump |
KR101305671B1 (en) * | 2011-11-29 | 2013-09-09 | 현대자동차주식회사 | Electric water pump |
JP2014020491A (en) | 2012-07-19 | 2014-02-03 | Nsk Ltd | Angular ball bearing and pump device for liquid gas |
US10267315B2 (en) * | 2013-11-28 | 2019-04-23 | Acd, Llc | Cryogenic submerged pump for LNG, light hydrocarbon and other electrically non-conducting and non-corrosive fluids |
WO2016049377A1 (en) * | 2014-09-26 | 2016-03-31 | Ebara International Corporation | Multi-fluid cargo pumps |
JP2017150593A (en) * | 2016-02-25 | 2017-08-31 | Ntn株式会社 | Roller bearing for cryogenic environment |
-
2017
- 2017-09-19 CH CH01152/17A patent/CH714176A1/en not_active Application Discontinuation
-
2018
- 2018-09-03 EP EP18192242.8A patent/EP3460246B1/en active Active
- 2018-09-18 US US16/134,260 patent/US10954952B2/en active Active
- 2018-09-19 CN CN201821537374.7U patent/CN209800276U/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
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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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