EP3884165A1 - Dispositif de pompage - Google Patents

Dispositif de pompage

Info

Publication number
EP3884165A1
EP3884165A1 EP19808976.5A EP19808976A EP3884165A1 EP 3884165 A1 EP3884165 A1 EP 3884165A1 EP 19808976 A EP19808976 A EP 19808976A EP 3884165 A1 EP3884165 A1 EP 3884165A1
Authority
EP
European Patent Office
Prior art keywords
pump
drive
pump device
hydraulic drive
shaft
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.)
Withdrawn
Application number
EP19808976.5A
Other languages
German (de)
English (en)
Inventor
Zoran Vujic
Frank Steiner
Álvaro PÉREZ-SAJADO KAMPS
Felix Sassen
Paul BELZ
Emil Kostov
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Westinghouse Electric Germany GmbH
Original Assignee
Westinghouse Electric Germany GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Westinghouse Electric Germany GmbH filed Critical Westinghouse Electric Germany GmbH
Publication of EP3884165A1 publication Critical patent/EP3884165A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F04D7/08—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being radioactive
    • 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
    • F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
    • F04D13/043—Units comprising pumps and their driving means the pump being fluid driven the pump wheel carrying the fluid driving means
    • 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
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • 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
    • F04D29/106—Shaft sealings especially adapted for liquid pumps
    • F04D29/108—Shaft sealings especially adapted for liquid pumps the sealing fluid being other than the working liquid or being the working liquid treated

Definitions

  • the invention relates to a pumping device for conveying a contaminated liquid with a pump which is driven by a flydraulic drive, the flydraulic drive being drivable by a drive fluid, and the pump and the fluid drive being mechanically connected.
  • Pumping devices for conveying contaminated liquids are very special devices that have to meet a variety of extreme design conditions. For example, such devices are also used at high pressures and high temperatures.
  • the type of contamination of the liquid also plays a role.
  • a nuclear reactor In order to ensure the highest level of safety even in the event of a malfunction, a nuclear reactor is surrounded by a hermetically sealed safety container or a containment / confinement, which means that in the event of a malfunction, the radioactive substances that may escape from the reactor core cannot escape into the environment, but rather be held back in the containment.
  • a safety medium collection area or a so-called reactor sump is usually provided within a security container, in which in the event of a malfunction, for example, radioactive contaminated cooling water escaping from a leaking cooling system is collected, cooled if necessary, and returned to the cooling system or the reactor core or other systems.
  • the heat energy then generated by the nuclear reactor or another heat source in the safety container or in its cooling medium collection area must be conducted outside in the form of heated medium to be cooled. If this does not happen, an increased formation of water vapor could create a dangerous overpressure in the safety container, which should be released directly from the safety container into the environment if a critical level is exceeded, if a failure of the safety container is to be avoided.
  • appropriate cooling systems which typically have a heat exchanger, by means of which it is ensured that radioactive contaminants remain within the containment and are not released into the environment.
  • a heat exchanger is cooled on the primary side in a cooling circuit by the heated one Medium flows through, typically in the event of an accident of radioactively contaminated water.
  • the secondary side of such a heat exchanger is flowed through by a coolant, which absorbs heat energy from the heated to cool the medium and cools it, but does not come into direct contact with it, so that it is not contaminated by it.
  • the uncontaminated coolant in turn emits the thermal energy it absorbs to a heat sink outside the containment.
  • cooling systems must be very powerful and able to transport larger amounts of heat from the cooling medium collecting area of a safety container to the outside even over a long period of time, for example two months or more.
  • the electric motors for the pumps are arranged within the containment.
  • a disadvantage of this prior art is that, especially in the event of a malfunction, the operation of active drive devices such as motors within the containment can be associated with increased uncertainty due to the conditions prevailing in the event of a malfunction, such as elevated temperature and an atmosphere with radioactive contaminated steam. This contradicts the safety endeavor to maintain the highest level of reliability of the safety container cooling system, especially in the event of a malfunction.
  • Patent document DE 10 2011 107470 A1 discloses a nuclear reactor cooling system, comprising a reactor pressure vessel, which in turn is arranged within a first spatial area surrounded by a first protective wall, and a second spatial area, which is arranged at a similar geodetic height to the first area and is surrounded by a second protective wall since it is intended to collect cooling water emerging from a primary cooling system interacting with the reactor pressure vessel.
  • the nuclear reactor cooling System has means to flood the first spatial area with cooled cooling water in an emergency.
  • a safety container cooling system has a heat exchanger and a pump, the pump being driven by a turbine. In this way, the electric motor-driven pump is avoided.
  • a pump device for conveying a contaminated liquid with a pump which is driven by a hydraulic drive, where the hydraulic drive can be driven by a drive liquid, and the pump and the liquid drive are mechanically connected.
  • the pump device is characterized in that a pump shaft of the pump and a hydraulic drive shaft of the hydraulic drive are supported by slide bearings, that a lubricant for the slide bearings is the drive fluid, that drive fluid is guided to the slide bearings by at least one lubricant medium line, and that the drive fluid after one Flow through the plain bearing can be diverted from the pump device.
  • the pump for conveying a contaminated liquid is driven by a hydraulic drive.
  • a hydraulic drive can be, for example, a drive turbine, a drive pump or a hydraulic motor.
  • a drive of the pump with electrical auxiliary energy is avoided, the electrical auxiliary energy can fail on the one hand during the operating time and on the other hand, electric motors are comparatively prone to failure.
  • the use of an internal combustion engine as a drive for such a pump is also avoided.
  • An internal combustion engine is also unsuitable for the use of the pump according to the invention.
  • the basic idea of the invention is to provide the movable Chen or rotating parts by plain bearings instead of the usual bearing with rolling elements, such as balls in ball bearings.
  • Slide bearings are also significantly more robust against mechanical influences, for example small particles that could penetrate the slide bearing.
  • Plain bearings are usually lubricated with a lubricant that reduces the friction of a moving surface of the plain bearing against a fixed surface of the plain bearing.
  • the invention provides that the drive fluid of the hydraulic drive is used as the lubricant or lubricant.
  • the pump device is only dependent on a supply medium that both operates or drives the hydraulic drive of the pump device and also provides the lubricant for the storage of the pump device. This avoids a further possible source of error for the failure of such a pump device, as a result of which the pump device itself becomes more robust and is suitable for long-term operation.
  • robust is understood to mean that the pumping device can be operated over a long period of time without failure, that is to say in an actionable or functional state.
  • a long period of time, or suitable for long-term operation is, for example, a period of at least two months or possibly an even longer period of, for example, six or twelve months of uninterrupted operation.
  • the pump device provides that the drive fluid is not only passed to the slide bearings as a lubricant, but is also discharged from the pump device after the slide bearings have flowed through.
  • a pressure at which the drive fluid is fed to the hydraulic drive is in any case higher than the pressure at which the contaminated fluid to be conveyed has.
  • a backflow preventer, non-return flaps or the like can also be arranged at a suitable point, for example in the housing of the pump device, in order to prevent the backflow of contaminated liquid even when the pump is at a standstill.
  • the design of a pump impeller ensures that the final pressure of the pump is in any case lower than the pressure prevailing in the drive medium that the hydraulic drive is supplied to. Another constructive possibility to ensure the above-mentioned pressure conditions is also to match the constructive design of the impeller of the hydraulic drive to the design of the pump wheel in such a way that a higher pressure on the outflow side of the pump than the pressure in the drive medium is avoided.
  • An advantageous embodiment of the pump device is characterized in that the pump and the hydraulic drive have a common rotary shaft. This simplifies the construction.
  • the pump device is made compact and also has fewer parts that could fail during operation of the pump device. This advantageously reduces possible sources of error. This promotes trouble-free long-term operation.
  • a common bearing housing in which the common rotary shaft is arranged also simplifies the construction of the pumping direction and enables an even more compact design. For example, this reduces the number of seals required on shafts. This technical measure also favors long-term operation.
  • the pump device can also be configured such that an axis of rotation of the rotary shaft is arranged vertically, as seen in the geodetic direction. In this way, an intake port of the pump can be positioned at a position that is as low as possible in the geodetic direction.
  • the pump device is arranged in a pump sump or liquid sump, so that inlet conditions for the liquid to be pumped into the suction side of the pump are most favorable at this geodetically located point.
  • Such pumps which are at least partially immersed in the liquid to be pumped, are then also referred to as submersible pumps, for example.
  • Another advantage of the pump device is obtained if an impeller of the pump and / or a drive wheel of the flydraulic drive are mounted on the fly, i.e. Both the impeller and the drive wheel are attached to one shaft end, in particular to the shaft ends of a common rotary shaft.
  • This provides the constructive possibility of providing both the pump and the hydraulic drive with a common bearing for the common rotary shaft.
  • a very compact construction is possible, which at the same time is particularly robust because it has the smallest possible number of components.
  • a lubricant medium line is designed as a recess or bore in the bearing housing.
  • the lubricant line is therefore integrated in the bearing housing. This also serves to further simplify the construction and compact design.
  • the pumping device is designed in such a way that a first end of a lubricant medium line is arranged at a point in the bearing housing which is enclosed by a hydraulic drive housing.
  • the drive liquid is taken directly from a pressure side of the hydraulic drive, that is to say a point in which the pressure of the supplied drive liquid prevails, and directed to a point in the region of the slide bearings, so that the drive flow liquid is fed to the plain bearings as a lubricant and serves as a lubricant for the plain bearings.
  • the supply of the sliding bearing with lubricant is particularly simple and insensitive to failure. This configuration also makes a contribution to trouble-free long-term operation.
  • a seal or a sealing system is arranged between the bearing housing and the rotary shaft, by means of which the penetration of contaminated liquid into the bearing housing is prevented. In this way, even when the pump device is at a standstill or when it is not in operation or in a transient operating state during starting or stopping the pump device, it is ensured that no contaminated liquid passes through a space between the bearing housing and the rotary shaft penetrates into the inner area of the bearing housing.
  • a further embodiment of the seal of the pump device provides that the seal is a spring-loaded mechanical seal, that the mechanical seal is closed by spring forces of the spring-loaded mechanical seal when the hydraulic drive is out of operation, that the mechanical seal is opened slightly against a spring force of the spring when the hydraulic drive is in operation, and that a small partial flow of the drive fluid from an inner region of the bearing housing passes through a gap between the slide ring and the counter ring of the mechanical seal into an interior of the pump housing when the hydraulic drive is in operation. In this way, the ingress of contaminated liquid into the inner region of the bearing housing of the pump device is reliably avoided when the pump device is out of operation.
  • a further embodiment of the seal of the pump device provides that the seal is a spring-loaded mechanical seal, that the mechanical seal is constantly closed by spring forces of the spring-loaded mechanical seal, regardless of whether the hydraulic drive is in operation or not, and that a partial flow of the drive fluid from one Inside the bearing housing through radial holes in the rotating shaft (and rotating components) and a connected axial hole in the rotating shaft enters a low-pressure interior of the hydraulic drive housing when the hydraulic drive is in operation. Due to the permanently sealed mechanical seal, the penetration of contaminated liquid into the inner area of the bearing housing of the pump device is reliably avoided, regardless of whether the pump device is in operation or not.
  • An advantageously configured pump device is also characterized in that the volume flow of the drive fluid flowing from the hydraulic drive housing through the lubricant medium lines into the bearing housing of the pump device is dimensioned for a defined operating state in such a way that the heat flow resulting from the friction on the slide bearings is generated by this volume flow and / or the heat flow transferred from an environment to the pump device is conveyed through the gap into the pump housing or through the bores in the rotary shaft into the hydraulic drive housing.
  • the pump device is in partially designed robust and has a correspondingly long trouble-free operating time with full functionality.
  • a further embodiment of the pump device is achieved if the seal is made of a material and is designed such that it can function with a liquid contaminated by a predetermined radioactive radiation during an operating time of at least two months, but also up to six or twelve months or that it can function as a contaminated liquid during a period of operation of at least two months, but also up to six or twelve months, with a predetermined load of an acid or an alkali.
  • An important property of the pump device is to have a robust design, that is to guarantee a long operating time, although the contaminated liquid to be conveyed often places high demands on the material, in particular the material of the seal.
  • Flier Solutions proposes to choose a sealing material that can withstand the contaminated liquid to be pumped for a correspondingly long time and at the same time ensures the technical function of the tightness.
  • Fig. 1 is a schematic diagram of an exemplary safety container cooling system
  • FIG 2 shows an exemplary pump device for use in a safety container cooling system.
  • FIG. 1 shows a schematic diagram of an exemplary first safety container cooling system 10 according to a prior art as an application example for an inventive pump device.
  • a security container 12 in this case a con- tainment / confinement made of concrete or steel for a nuclear reactor, encloses an atmospheric area 14 and a cooling medium collecting area 18, for example a reactor sump.
  • the cooling medium collecting area 18 is filled with a medium 16 to be cooled, in this case with cooling water, the surface of which is indicated by a line in the figure.
  • the medium to be cooled is heated by a heat source 40, in this example a nuclear reactor located at least partially in the cooling medium collecting area 18, which in the event of a specific malfunction releases its decay power to the medium 16 to be cooled.
  • Typical pressures and temperatures of the medium to be cooled are, for example, in the range from 1 bar to 4 bar or in the range from 50 ° C. to 110 ° C.
  • the medium 16 to be cooled is guided in a first cooling circuit through the primary side 22 of a heat exchanger 20 located above the cooling medium collecting area 18.
  • a first pump arrangement 38 is arranged in the cooling medium collecting area 18, which presses the medium to be cooled from below into the primary side 22 of the first heat exchanger 20 via a line 26.
  • There the medium is cooled and exits again as a cooled medium via a line 28.
  • the line 28 can either be returned directly to the cooling medium collection area, but in the drawing it is indicated that the line 28 ends in the atmospheric area 14 and the medium 16 is distributed via crushing or spraying devices, not shown, and is then collected again in the cooling medium collection area 18 .
  • the secondary side 24 of the heat exchanger 20 is flowed through by a coolant, which is supplied via a second pump arrangement 34 through a line 30 from outside of the security container 12.
  • the second pump arrangement 34 sets the coolant in such a way that a turbine 36 arranged in the line 30 is driven thereby.
  • the first pump arrangement 38 is coupled to the turbine 36 in such a way that it is driven by it.
  • the first pump arrangement 38 and the turbine 36 are mechanically coupled to one another by a common rotary shaft.
  • the medium to be cooled in the first cooling circuit is indirectly caused to flow by a motor arranged outside the security container 12 or another drive device of the second pump arrangement 34.
  • an active electric motor such as a Internal combustion or electric motor for driving the first pump arrangement 38 within the containment 12 is advantageously avoided.
  • the then heated coolant is passed via a line 32 to the outside of the containment 12, where the thermal energy is then given to any heat sink.
  • the first safety container cooling system 10 shown in the figure is only intended to serve as an example of how a pump device according to the invention is used in a field of technology which, in the event of a corresponding accident in a nuclear power plant, contaminates liquid, namely essentially water, the radioactive particles or May contain components is used.
  • a corresponding example can, however, also be found easily for a chemical plant in which chemical fluids collect at a geodetically low-lying point and contaminate this area accordingly.
  • the pumping device is designed to convey the contaminated liquid, which also includes the conveyance of normal, ie non-contaminated liquid.
  • FIG. 2 shows an exemplary pump device 50 that has a shaft 52 that rotates about an axis of rotation 54.
  • a drive wheel 56 is attached to an upper shaft end.
  • a centrifugal pump wheel is selected as the drive wheel 56 and a screw connection is selected as the connection between the drive wheel 56 and the upper shaft end.
  • a hydraulic turbine with a turbine wheel or another type of pump with an impeller or impeller is used as the hydraulic drive.
  • a tongue and groove connection or a form-fitting connection type can also be selected as the type of connection between the drive wheel 56 of the shaft 52.
  • a pump impeller 58 is also attached to a lower shaft end.
  • a centrifugal pump is shown as the type of pump in the exemplary embodiment shown, which means for the pump impeller 58 that it is a centrifugal pump wheel. Both the drive wheel 56 and the pump impeller 58 are attached to one of the shaft ends, so they are overhung.
  • the shaft 52 is arranged in a bearing housing 60, the bearing being carried out by means of a slide bearing system which transfers both axial and radial bearing forces from the shaft 52 into the bearing housing 60.
  • the bearing housing 60 has fastening means with which it can be connected, attached or mounted on the floor or on a fixed component at the installation location. However, this is not shown in the figure.
  • the plain bearing system has a plain bearing sleeve 62 which has the shape of a tube piece, the inner diameter of which is adapted to an outer diameter of the shaft 62.
  • the slide bearing sleeve 62 is connected to the shaft 52, so that both components rotate together when the pump device 50 is operating.
  • the plain bearing system has a first 64 and egg NEN second plain bearing ring 66, which are each connected to the bearing housing 60. Accordingly, the plain bearing rings 64, 66 remain stationary at their installation location in the bearing housing 60, even when the shaft 52 rotates.
  • the slide bearing system has a third slide bearing ring 100 and a fourth slide bearing ring 102, which are each connected to the shaft 62, so that these slide bearing rings rotate together with the shaft when the pump device 50 is in operation.
  • a length of long-term operation with the pump device 50 can be influenced by selecting the diameter of the shaft 52 to be larger than would be necessary according to a design based on the minimum values of a calculated shaft diameter. In the same way, the length of long-term operation can be increased by selecting the slide bearing system to be larger than would be necessary for the slide bearing system as a minimum size according to a calculation.
  • a first shoulder 68 is attached to the bearing housing 60.
  • the first paragraph 68 is provided as a connection point for a drive housing, which is not shown in the figure.
  • two indicated screws 70 are intended to show that the drive housing can be connected, for example, with screws to the first shoulder 68 and thus to the bearing housing 60.
  • the drive wheel 56 With a mounted drive housing, the drive wheel 56 is completely enclosed by an interior of the drive housing.
  • the drive housing itself has an inlet and at suitable points a drain opening for a drive medium, such as water, oil or other liquids. For use in the nuclear field for the example shown in the figure, however, water is generally used as the driving fluid.
  • the bearing housing 60 also has a first 72 and a second bore 74.
  • Each of the bores 72, 74 is closed on its side facing the external environment with a screw plug 76. For example, this can be opened temporarily for ventilation purposes. Otherwise, they serve for the liquid-tight sealing of the bores 72, 74.
  • the bores 72, 74 also each have a further opening on the side opposite the locking screws 76 to the inside of the bearing housing 60. The further opening is between the first 64 and second slide bearing rings 66 arranged.
  • first bore 72 is connected to a first end of a first lubricant medium line 78, a second end of the first lubricant medium line 78 ending at a point in the bearing housing 60 which faces the interior of the drive housing, so that the interior of the drive housing is hydraulically connected to the other Opening is connected.
  • a correspondingly designed second lubricant medium line 80 also connects the second bore 74 to the interior of the drive housing.
  • the lubricant lines 78, 80 are designed as bores in the bearing housing 60.
  • a connecting line 82 is shown, which in the exemplary embodiment shown is also designed as a bore in the bearing housing 60, which connects the first bore 72 hydraulically with an inner region of the housing interior of the bearing housing 60 facing the pump impeller 58.
  • a second shoulder 84 is formed on the bearing housing 60, the second paragraph 84 being provided for positioning and flanging a pump housing which completely surrounds the pump impeller 58.
  • the connection between the pump housing and the second shoulder 84 is indicated by connecting screws 86.
  • the pump housing is not shown in the figure, but has a suction opening and a pressure-side outlet opening for the liquid to be pumped.
  • An essential area of application of the pump device 50 is the conveyance of contaminated liquid.
  • Contaminated liquid is to be understood as a contamination with radioactive substances, as occurs, for example, in the event of a serious accident in a nuclear power plant.
  • a contaminated liquid can also be a contaminated nation with chemical substances, for example acids or alkalis or otherwise harmful substances or poisons or liquids.
  • the materials used for the pumping device must then also be designed in particular for the type of contamination. This means that the materials used endure a radioactive radiation of a fixed amount for a certain period of time, for example 2 or 3 months, but up to six or twelve months, in such a way that the function of the pump device is retained. The same applies to a contamination of the material by chemical contamination.
  • a functional operation of the pump device of at least two months is already considered as trouble-free long-term operation.
  • An important property of the pump device 50 is to prevent contaminated liquid from getting into the drive liquid.
  • a drive fluid is introduced into the interior of the housing via the inlet opening in the drive housing, and the drive wheel 56 is thereby set into a rotational movement by the movement of the drive fluid to be directed. Together with the drive wheel 56, the shaft 52 and the pump impeller 58 rotate.
  • the drive fluid under a predetermined drive pressure passes from the housing interior of the drive housing via the lubricant medium lines 78, 80 into the bores 72, 74.
  • a partial flow of the drive fluid in the bores 72, 74 reaches an area formed by the slide bearing sleeve 62, the slide bearing rings 64, 66 and the bearing housing 60.
  • the drive fluid under the drive pressure also flows in the area of sliding surfaces between the plain bearing rings 64, 66 and the plain bearing sleeve 62, or in the area of sliding surfaces between the plain bearing rings 64 and 100, or 66 and 102, so that a lubricating medium film is formed in the sliding bearings by the drive fluid, which is independent of the rotational movement of the shaft 52.
  • the friction or wear due to friction in the slide bearings is advantageously reduced, regardless of the operation or the rotational movement of the shaft.
  • Even in the operating case of the pump device 50 sufficient lubrication of the sliding surfaces as a whole is ensured by a steady inflow of drive fluid which serves as a lubricant for the sliding bearing system.
  • Another partial flow of the drive fluid passes via the connecting line 82 into the inner region 88 of the bearing housing facing the pump impeller 58. ses 60. Contaminated liquid could get into this inner region, which is sucked in by the pump with its pump impeller 58 during operation and is then in contact with the side of the bearing housing 60 facing the pump impeller 58. However, this is prevented by the further partial flow of the drive fluid.
  • the further partial flow is namely under the same pressure as the drive fluid, which is selected to be higher than the pressure prevailing on the side of the bearing housing 60 facing the pump runner 58. In this way, a steady, low fluid flow of drive fluid from the drive side of the pump device 50 through the bearing housing 60 to the pump side is ensured.
  • the volume flow of the further partial flow is united by the choice of the diameter of the connecting line 82 and by the choice for the pressure of the drive fluid
  • Another application of the pump device 50 is the use as a submersible pump device. Then the case may arise that the pump device 50 is in contaminated liquid while the pump device 50 is not in operation. In this case, too, it is expedient for contaminated liquid to penetrate into the inner region 88, that is to say the inside of the bearing housing 60, and thus for possible mixing of contaminated liquid with the drive liquid to be avoided.
  • a mechanical seal 90 is arranged according to the invention between a static component of the bearing housing 60 and a rotating component of the shaft 52 or a rotating shaft. The secure closing between rotating and standing parts of the pump device 50 is shown in FIG. 2 in the view shown on the right half of the figure.
  • a slide ring system has a plurality of springs, of which a spring 92 is shown.
  • the spring 92 is arranged in a cover 94 and a slide ring holder 96 in such a way that the spring force of the spring 92 causes the mechanical seal 90 against the shaft 52 or against the shaft 52 rotating component is pressed. In this way, the sealing effect of the mechanical seal 90 is improved.
  • the situation is shown on the right half of the figure when the pump device 50 is out of operation. Then the inner region 88 is depressurized, so that penetration of contaminated liquid into the inner region 88 is prevented by the spring-loaded mechanical seal 90.
  • the mechanical load on the mechanical seal 90 is advantageously prevented or at least reduced during operation of the pump device 50, for example due to friction or abrasion.
  • the mechanical seal 90 is thus lubricated at least in the period of starting the pump device 50 and in the transient phase from the start of the pump device 50 to continuous operation.
  • the mechanical seal only has to have its sealing effect when the pump device 50 is out of operation or in the transient phase described when starting or ending the operation.
  • the sealing effect is then supported by the spring action of the springs.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne un dispositif de pompage (50) pour le refoulement d'un liquide contaminé au moyen d'une pompe qui est entraînée au moyen d'un entraînement hydraulique, l'entraînement hydraulique pouvant être entraîné par un liquide d'entraînement et la pompe et l'entraînement hydraulique étant reliés mécaniquement. En outre, un arbre de la pompe et un arbre de l'entraînement hydraulique sont logés par des paliers lisses (62, 64, 66, 100, 102). Le liquide d'entraînement est un lubrifiant pour les paliers lisses (62, 64, 66). Du liquide d'entraînement est guidé à travers au moins une conduite de lubrifiant (78, 80) vers les paliers lisses (62, 64, 66, 100, 102) et le liquide d'entraînement, après avoir traversé les paliers lisses (62, 64, 66, 100, 102), est guidé à l'extérieur du dispositif de pompage.
EP19808976.5A 2018-11-24 2019-11-13 Dispositif de pompage Withdrawn EP3884165A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018009260.8A DE102018009260A1 (de) 2018-11-24 2018-11-24 Pumpvorrichtung
PCT/EP2019/000313 WO2020104050A1 (fr) 2018-11-24 2019-11-13 Dispositif de pompage

Publications (1)

Publication Number Publication Date
EP3884165A1 true EP3884165A1 (fr) 2021-09-29

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19808976.5A Withdrawn EP3884165A1 (fr) 2018-11-24 2019-11-13 Dispositif de pompage

Country Status (4)

Country Link
EP (1) EP3884165A1 (fr)
DE (1) DE102018009260A1 (fr)
UA (1) UA126030C2 (fr)
WO (1) WO2020104050A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102019004244B3 (de) 2019-06-14 2020-10-01 Westinghouse Electric Germany Gmbh Reaktordruckbehälterkühlsystem

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JPS6011198A (ja) * 1983-07-01 1985-01-21 株式会社日立製作所 原子炉内蔵型再循環ポンプ
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FR2782544B1 (fr) * 1998-08-19 2005-07-08 Air Liquide Pompe pour un liquide cryogenique ainsi que groupe de pompage et colonne de distillation equipes d'une telle pompe
DE102011107470A1 (de) 2011-07-16 2013-01-17 Westinghouse Electric Germany Gmbh Kernreaktorkühlsystem

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