EP3163086B1 - Unité d'entraînement de pompes destinée à transporter un fluide de processus - Google Patents

Unité d'entraînement de pompes destinée à transporter un fluide de processus Download PDF

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Publication number
EP3163086B1
EP3163086B1 EP16192508.6A EP16192508A EP3163086B1 EP 3163086 B1 EP3163086 B1 EP 3163086B1 EP 16192508 A EP16192508 A EP 16192508A EP 3163086 B1 EP3163086 B1 EP 3163086B1
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EP
European Patent Office
Prior art keywords
pump
barrier fluid
drive unit
storage chambers
fluid
Prior art date
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Application number
EP16192508.6A
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German (de)
English (en)
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EP3163086A1 (fr
Inventor
Paul Meuter
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Sulzer Management AG
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Sulzer Management AG
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    • 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
    • F04D29/128—Shaft sealings using sealing-rings especially adapted for liquid pumps with special means for adducting cooling or sealing fluid
    • 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
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
    • 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
    • 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
    • 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
    • F04D13/0626—Details of the can
    • 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
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • 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
    • F04D29/043—Shafts
    • 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
    • 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
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine

Definitions

  • the invention relates to a pump drive unit for conveying a process fluid.
  • Pump-drive units in which a pump with an impeller and a drive for the pump are enclosed by a common housing, are often used for applications in which the pump is completely or completely immersed in a liquid, e.g. B. water, or when the pump is operated in hard-to-reach places or under difficult conditions or environmental conditions.
  • a liquid e.g. B. water
  • pumps that are used for fluidized bed or ebullated bed processes in the hydrocarbon processing industry. These methods are used, for example, to remove heavy hydrocarbons, e.g. B. heavy oil, or refinery residues to clean or break up into more usable more volatile hydrocarbons. This is often done by applying hydrogen to the heavy hydrocarbons, the mixed components being swirled around in a reactor and the heavy hydrocarbons being broken up there with the aid of catalysts.
  • process fluid which usually consists mainly of heavy hydrocarbons
  • special pump-drive units are used, for which the term ebullating pump has become established.
  • ebullator pumps are provided as circulation pumps for the process fluid and are usually directly on the reactor Due to the process, designed in such a way that the pump is arranged above the drive with respect to the vertical. Ebullator pumps have to work as reliably as possible and over a long period of time in continuous operation under extremely challenging conditions.
  • the process fluid is typically under a very high pressure of, for example, 200 bar or more, and has a very high temperature of more than 400 ° C., e.g. B. 460 ° C.
  • the housing of such pump-drive units is therefore designed as a pressure housing which can withstand these high operating pressures.
  • the drive is usually designed as an electric motor, which is also exposed to the high operating pressure inside the housing.
  • the motor must be adequately protected against the ingress of process fluid, which is why the motor is usually filled with a barrier fluid or through which it flows, which additionally serves for lubrication and heat dissipation from the motor.
  • Embodiments as completely oil-filled motors or as canned motors or as so-called "cable wound" motors are possible.
  • the barrier fluid must be a dielectric fluid, e.g., a dielectric oil, in order to avoid a short circuit in the motor.
  • a can is provided between the stator and the rotor, which hermetically seals the stator from the rotor, the rotor usually also being protected by a casing.
  • the barrier fluid is usually passed through the gap between the rotor and the canned motor.
  • the electrical lines with which the stator winding is wound are surrounded by an electrically insulating jacket.
  • these Embodiments also use a barrier fluid other than a dielectric fluid. This is advantageous for many applications, among other things for the reason that a barrier fluid with the best possible cooling and lubricating properties can be selected without taking its electrical conductivity properties into account.
  • Embodiments are also known in which the process fluid itself is used as a barrier fluid for cooling and lubricating the motor, but for many applications it is essential that the motor is adequately protected against ingress of the process fluid.
  • the process fluid itself is used as a barrier fluid for cooling and lubricating the motor, but for many applications it is essential that the motor is adequately protected against ingress of the process fluid.
  • heavy hydrocarbons as process fluids which are left over from the distillation of petroleum, very often contain chemically aggressive and / or abrasive substances, so that the process fluid can lead to considerable damage, especially in the drive or in the bearings.
  • the barrier fluid is very often conducted in a cooling circuit.
  • the barrier fluid is introduced into the drive through an inlet, flows through the drive, for example through the gap between the rotor and the can, as well as the pump-side radial bearing of the shaft and is then discharged through an outlet in the area between the drive and the pump. From this outlet, the barrier fluid flows back to the inlet via a heat exchanger.
  • barrier fluid for refilling barrier fluid
  • additional barrier fluid can be introduced either outside the housing into the cooling circuit or directly into the drive through a separate inlet opening.
  • This additional introduction of barrier fluid is primarily used to compensate for losses that arise as a result of the mostly low flow rate of the barrier fluid is provided in the process fluid.
  • the barrier fluid flowing out of the drive flows along the shaft, the barrier fluid is not completely discharged through the outlet, but part of it flows or creeps along the shaft into the pump and mixes there with the process fluid.
  • This process is intended and desirable, because this flow of the barrier fluid into the pump makes it possible to reliably prevent process fluid from flowing from the pump along the shaft in the direction of the drive or from penetrating into the drive.
  • the barrier fluid blocks the opposite path for the process fluid from the pump to the drive.
  • a throttle for generating a controlled leakage flow is provided on the shaft in the vicinity of its entry into the pump.
  • This throttle can be designed, for example, in the form of a mechanical seal, in which, as is known, there is direct physical contact between a part non-rotatably connected to the shaft and a part which is stationary with respect to the housing, or in the form of a throttle, in which there is no direct physical contact between rotating and rotating parts stationary parts exist.
  • This contactless throttle is, for example, a throttle socket.
  • the pump-drive unit can in principle still work without the injection device, but only if there are no changes in the operating state of the Pump-drive unit or occur in the cooling system. A failure or disruption of the barrier fluid injection does not necessarily have to result in the pump-drive unit being switched off. It is entirely possible to continue to operate the unit at least for a certain period of time and to remedy the malfunction in the injection device during this period.
  • a reduction in the volume of the barrier fluid can have several causes: For example, the temperature of the cooling water, which is usually used in the heat exchanger to cool the barrier fluid, can drop, as a result of which the barrier fluid cools down and contracts for thermal reasons. Or if the speed of rotation of the pump is reduced, this also leads to a reduction in the volume of the barrier fluid. Even if the pump-drive unit has to be switched off, this ultimately leads to a reduction in the volume of the barrier fluid. There is therefore a considerable risk that the drive will be damaged or even irreparably destroyed by the process fluid.
  • EP 2 492 511 A2 discloses a generic pump-drive unit.
  • the invention is dedicated to this problem. It is therefore an object of the invention to provide a pump-drive unit for conveying a process fluid, in which, even if there is a disruption in the supply of barrier fluid, it is ensured that the drive will not be damaged by the process fluid.
  • this pump-drive unit should also be able to be used as an ebullator pump.
  • a pump-drive unit for conveying a process fluid with a common housing which a pump with an impeller for rotation about an axial direction and a drive for the pump, with a shaft for driving the impeller, which connects the drive with the pump, and with a throttle which extends around the shaft, and which is provided between the impeller and the drive, the housing having a pump inlet and a pump outlet for the process fluid, an inlet for a barrier fluid through which the barrier fluid can be introduced into the drive, and an outlet for the barrier fluid through which the barrier fluid can be removed from the housing, and a plurality of storage chambers for the barrier fluid are provided on the shaft in the area between the throttle and the drive, which storage chambers are arranged one behind the other with respect to the axial direction, with two adjacent storage chambers being flow-connected to one another.
  • the process fluid begins to exit the pump along the shaft, passes through the throttle and into the first of the storage chambers. Since this is still filled with the pure barrier fluid, the process fluid is mixed with the barrier fluid, which greatly dilutes the process fluid. This mixture of process fluid and barrier fluid then reaches the next storage chamber as contaminated barrier fluid, which is still filled with pure barrier fluid. In this storage chamber, the process fluid is then further diluted by the pure barrier fluid. The process fluid is then most diluted in the last storage chamber, which is closest to the drive. Even if the barrier fluid contaminated with process fluid were to subsequently penetrate the drive, the process fluid is so diluted that the drive will not be damaged.
  • the configuration according to the invention ensures that when the pump is switched off - if at all - only a small amount of highly diluted process fluid in the form of the contaminated barrier fluid can penetrate the drive, but this does not damage the drive. This ensures that the pump-drive unit is switched off safely without the drive being damaged by the ingress of process fluid.
  • the second possibility is that the malfunction can be remedied relatively quickly.
  • the pump-drive unit does not have to be switched off.
  • the process fluid is successively diluted in the storage chambers arranged one behind the other in the axial direction. If the malfunction is now eliminated, a sufficient amount of pure barrier fluid is available again. This then pushes the contaminated barrier fluid out of the storage chambers in the direction of the pump, so that the contaminated barrier fluid is flushed out of the storage chambers into the pump.
  • This also applies analogously to the case that a certain amount of barrier fluid contaminated with process fluid has already penetrated the drive. This is then also removed from the drive by the supply of the pure barrier fluid, so that damage to the drive by the process fluid is effectively prevented.
  • this ensures that if such a malfunction occurs, damage to the drive by the process fluid is prevented, either by resuming the supply of pure barrier fluid or by switching off the pump-drive unit in a controlled and safe manner.
  • a particular advantage of the design according to the invention with the storage chambers is that there is no need for a sealing arrangement on the shaft between the drive or the radial bearing provided on the drive on the pump side, which would result in direct physical contact between a rotating part - that is, a part connected to the shaft in a rotationally fixed manner - and a part that is stationary with respect to the housing, for example a mechanical seal.
  • the throttle and the storage chambers function without contact in the sense that they are the rotating shaft not touched. This is particularly advantageous in those configurations in which the process fluid is under very high pressure, e.g. B. at least 200 bar, and / or has a very high temperature, e.g. B. at least 400 ° C.
  • each storage chamber is designed as an annular space around the axial direction.
  • two adjacent storage chambers are flow-connected by a throttle gap, the shaft in each case forming a boundary surface of the throttle gap.
  • the suitable number of storage chambers depends of course on the particular application or on the specific design of the pump-drive unit, for example on the volume that is available in the drive for the barrier fluid, on the size and performance of the pump or on the conveying process fluid. In practice, it has proven useful if at least three and at most ten storage chambers are provided.
  • At least one of the storage chambers is provided in the housing, for example as an annular groove which extends around the shaft.
  • At least one of the storage chambers is provided in the shaft, for example as an annular groove that extends over the circumference of the shaft.
  • the outlet and the inlet for the barrier fluid are connected to one another by a line, so that a cooling circuit for the barrier fluid is formed, the cooling circuit comprising a heat exchanger.
  • the heat exchanger for the cooling circuit is mounted on the housing.
  • the heat exchanger can be attached to the housing, for example, by means of a flange connection or by means of screwing.
  • an injection device for refilling barrier fluid is provided.
  • the storage chambers naturally depends on the respective design of the pump-drive unit and in particular on the volume available for the barrier fluid and must therefore be determined for the specific application.
  • the storage chambers have a total volume which is at least as large, and preferably twice as large, as the thermally induced change in volume of the barrier fluid in the cooling circuit when the temperature of the barrier fluid decreases by a predeterminable value.
  • the change in volume of the barrier fluid that is caused by such a temperature change can now be calculated with the aid of the thermal expansion coefficient.
  • a value that is at least as large and preferably twice as large as the determined change in volume of the barrier fluid is then selected as the total volume of all storage chambers.
  • the total volume of all storage chambers is at least 0.5% and at most 4%, preferably at most 3% of the volume available in the cooling circuit for the barrier fluid.
  • the housing is designed as a pressure housing, preferably for an operating pressure of at least 200 bar.
  • the pump-drive unit is designed for a process fluid which has a temperature of more than 400 ° C.
  • the embodiment according to the invention is particularly suitable for such a pump-drive unit in which the drive is arranged below the pump with respect to the vertical or is arranged next to the pump with respect to the horizontal. In relation to the normal position of use of the pump-drive unit, this means that the pump is arranged in the common housing above or next to the drive.
  • Fig. 1 shows, in a partially schematic sectional illustration, an exemplary embodiment of a pump-drive unit according to the invention for conveying a process fluid, which is designated as a whole with the reference number 1.
  • the pump-drive unit 1 comprises a pump 2, which is designed as a centrifugal pump, and a drive 3, which is designed as an electric motor.
  • the pump 2 and the drive 3 are arranged in a common housing 4 which encloses the drive 3 and the pump 2.
  • the housing 4 comprises an upper housing part 41 and a lower housing part 42, which are sealingly connected to one another by screw connections (not shown) or a flange connection.
  • the pump-drive unit 1 in this exemplary embodiment is designed as an ebullating pump.
  • ebullator pumps are pump-drive units that are used for fluidized bed or ebullated bed processes in the hydrocarbon processing industry. These processes are used to purify heavy hydrocarbons that remain in the bottom of the separation columns, for example in the oil refinery, for example to desulfurize them and / or break them down into lighter hydrocarbons, which can then be used more economically as distillates.
  • An example of heavy hydrocarbons is heavy oil that remains in the refinery of petroleum. In a known method, the starting substance, so the heavy hydrocarbons such. B. heavy oil, heated, mixed with hydrogen and then as a process fluid in the fluidized bed or boiling bed reactor (ebullated bed reactor).
  • the process fluid is then cleaned or broken up in the reactor with the aid of catalysts that are suspended in the reactor be held in order to ensure the closest possible contact with the process fluid.
  • An ebullator pump which is typically mounted directly on the reactor, is used to supply the reactor with the process fluid or for the circulation of the process fluid.
  • the ebullator pump Since the process fluid is under a very high pressure of, for example, at least 200 bar and under a very high temperature of, for example, over 400 ° C., the ebullator pump must also be designed for such pressures and temperatures.
  • the housing 4 of the ebullator pump 1 designed as a pump-drive unit, which encloses the pump 2 and the drive 3, is designed as a pressure housing that can reliably withstand these high operating pressures of, for example, 200 bar or more.
  • the ebullator pump is also designed in such a way that it can safely convey a hot process fluid which has a temperature of more than 400 ° C.
  • the pump-drive unit 1 is designed as such an ebullator pump. It goes without saying, however, that the invention is not restricted to such configurations or applications.
  • the pump-drive unit 1 according to the invention can also be designed for other applications, for example as a submersible pump which, during operation, is completely or partially in a liquid, e.g. B. water, is immersed.
  • the invention is suitable for those pump-drive units in which the drive 3 is arranged below the pump 2 with respect to the vertical (vertical pump), or in which the drive 3 is arranged next to the pump 2 with respect to the horizontal (horizontal pump).
  • a representation of an embodiment as a horizontal pump corresponds to z. B. a representation that is changed by rotating the Fig. 1 by 90 °.
  • the illustrated embodiment of the inventive pump drive unit 1 as an ebullator pump is the pump 2 with respect to the normal position of use, which is shown in FIG Fig. 1 is shown, arranged above the drive 3.
  • the pump 2 is designed as a centrifugal pump with an impeller 21, which has several blades and in the operating state around one axial direction A rotates.
  • the housing 4 has a pump inlet 22, which is arranged here above the impeller 21, and a pump outlet 23, which is arranged here on the side of the housing 4.
  • the impeller 21 promotes the process fluid, in this case the fluid with the heavy hydrocarbons, e.g. B. heavy oil, from the pump inlet 22 to the pump outlet 23, which is directly connected to the reactor.
  • the drive 3 is provided, which is designed here in a manner known per se as an electric canned motor.
  • the drive 3 comprises an inner rotor 31 and an outer stator 32 surrounding the rotor 31.
  • a can 33 is provided between the rotor 31 and the stator 32, which hermetically seals the stator from the rotor 31 in a known manner.
  • the rotor 31 is non-rotatably connected to a shaft 5 which extends in the axial direction A and, on the other hand, is non-rotatably connected to the impeller 21 of the pump 2 so that the pump 2 can be driven by the drive 3.
  • a radial bearing 6 is provided for the radial mounting of the shaft 5.
  • An axial bearing 7 for the shaft 5 is provided below the lower radial bearing 6 according to the illustration.
  • a circulation impeller 8 for a barrier fluid is also provided at the lower end of the shaft 5 according to the illustration, which is also non-rotatably connected to the shaft 5 and which is designed as a radial impeller. Its function is explained further below.
  • the circulation impeller 8 can also be provided between the pump 2 and the drive 3 on the shaft 5.
  • this conveys the process fluid from the pump inlet 22 to the pump outlet 23.
  • heavy hydrocarbons such as e.g. B. heavy oil
  • other process fluids for example chemically aggressive substances or contaminated fluids
  • a barrier fluid is provided, for example an oil, in particular a lubricating or cooling oil, one function of which is to prevent process fluid from penetrating into the drive 3.
  • the barrier fluid also fulfills the function of dissipating heat as a cooling fluid and of lubricating the drive 3 as well as the radial bearings 6 and the axial bearing 7 as a lubricant.
  • the heat to be dissipated by the barrier fluid includes both the heat that is generated by the drive 3 during its operation and such heat that is transferred from the hot process fluid to the shaft 5 or to the housing 4. While the process pressure in the drive 3 and in the pump 2 is essentially the same, the operating temperature in the pump 2 is significantly higher than in the drive 3. While, for example, the impeller 21 essentially assumes the same temperature as the process fluid, for example here above 400 ° C, the temperature in the drive 3 is significantly lower, for example in the range of 60 ° C.
  • the barrier fluid thus also has the function of dissipating the heat transferred from the hot impeller 21 to the shaft 5.
  • both an inlet 43 for the barrier fluid, through which the barrier fluid can be introduced into the drive 3, and an outlet 44 for the barrier fluid, through which the barrier fluid can be discharged from the housing 4, are provided on the housing 4.
  • the outlet 44 is fluidly connected to the inlet 43 via a line 91, so that the barrier fluid is guided in a cooling circuit.
  • This cooling circuit further comprises a heat exchanger 9 which is provided outside the housing 4 and in which the barrier fluid gives off its heat to a heat carrier, for example water.
  • the inlet 43 for the barrier fluid is provided at the lower end of the housing 4, as shown, so that the barrier fluid not only flows through the drive 3, but also the two radial bearings 6 and the axial bearing 7, whereby these are lubricated and cooled.
  • the barrier fluid is then led to the outlet 44 and arrives via the line 91 to the heat exchanger 9, where the barrier fluid emits heat. From the heat exchanger 9, the barrier fluid is then through the Line 91 led back to inlet 43, whereby the cooling circuit closes.
  • the inlet 43 is arranged opposite the circulation impeller 8, so that the circulation impeller 8 sucks in the barrier fluid in the axial direction A through the inlet 43.
  • the barrier fluid conveyed by the circulation impeller 8 flows through the axial bearing 7 and the lower radial bearing 6, is then introduced into the drive 3, there flows through the gap between the rotor 31 and the can 33, emerges from the drive 3, flows through the upper radial bearing 6 and is then led to outlet 44, from where the barrier fluid is circulated through line 91 and heat exchanger 9 back to inlet 44.
  • the barrier fluid circulating in the cooling circuit prevents process fluid from penetrating into the bearings 6, 7 and in particular into the drive 3, because the flowing barrier fluid blocks the passage for the process fluid along the shaft 5 into the drive 3.
  • an injection device 92 is also provided for refilling or feeding barrier fluid into the cooling circuit.
  • the injection device 92 comprises a source or a storage container for the barrier fluid and is connected to the cooling circuit via a check valve 93. It is possible - as in Fig. 1 - that the injection device 92 is connected to the part of the cooling circuit arranged outside the housing 4, for example with the line 91, or a separate inlet opening is provided on the housing 4, through which the barrier fluid can be introduced from the injection device 92 into the cooling circuit .
  • the injection device 92 is used to generate an intentional and controlled leakage flow of the barrier fluid along the shaft 5 into the pump 2 balance.
  • the barrier fluid emerging from the drive 3 and flowing through the upper radial bearing 6 is not completely discharged through the outlet 44.
  • Part of the barrier fluid generates a leakage flow along the shaft 5 into the pump 2 and mixes there with the process fluid, but this does not have any negative effects.
  • This leakage flow into the pump 2 efficiently prevents process fluid from flowing out of the pump 2 in the opposite direction along the shaft 5.
  • the amount of barrier fluid required for this leakage flow is continuously fed to the cooling circuit through the injection device 92, ie during normal operation the injection device 92 replaces the amount of barrier fluid that is introduced into the process fluid by the leakage flow. Furthermore, the injection device 92 compensates for changes in volume of the barrier fluid located in the cooling circuit. Such changes in volume can occur, for example, when the speed of the pump 2 changes, or when the temperature changes, or when the pump-drive unit 1 is started up or switched off.
  • the leakage flow is usually not particularly strong and is, for example, about 20 to 30 liters / hour in normal operation If there is a malfunction in the injection device 92 or in the injection system for the barrier fluid, for example a failure of the injection device 92 so that the injection device 92 cannot supply any barrier fluid or not enough barrier fluid into the cooling circuit, this does not inevitably lead to the risk of that the drive 3 is damaged by the ingress of process fluid because sufficient barrier fluid is still circulated in the cooling circuit to keep the process fluid away from the drive 3.
  • a device is provided on the shaft 5 in the area between the pump 2 and the drive 3 Combination is provided, which is designated as a whole by the reference number 10 and comprises a throttle 13 and a plurality of storage chambers 11.
  • FIG. 10 shows an enlarged sectional illustration of this combination 10 of the exemplary embodiment from FIG Fig. 1 .
  • the combination 10 comprises a plurality, here five, of storage chambers 11 for the barrier fluid, which are arranged one behind the other with respect to the axial direction A, two adjacent storage chambers 11 being flow-connected. This flow connection is preferably as in Fig.
  • Fig. 2 shown, designed as a throttle gap 12, the shaft 5 each forming a boundary surface of the throttle gap 12.
  • the throttle gap is designated with the reference symbol 12 only for the two upper storage chambers 11 according to the illustration.
  • the other storage chambers 11 are also flow-connected through such a throttle gap 12.
  • the throttle 13 is arranged, which is designed here as a throttle bushing 13, which is in on extends around the shaft 5 in a known manner without touching the shaft 5.
  • the throttle bushing 13 is arranged or mounted in a stationary manner with respect to the housing 4.
  • the throttle bushing 13 is designed in such a way that it limits the volume flow of the barrier fluid into the pump 2 to a controlled leakage flow during normal, ie trouble-free operation of the pump-drive unit 1. It goes without saying that the design of the throttle as a throttle bushing 13 is only to be understood as an example.
  • the throttle 13 Any device known per se with which a controlled leakage flow of the barrier fluid can be generated in a contact-free manner is suitable as the throttle 13. So can for example, the surface of the throttle 13 facing the shaft 5 can be designed to be smooth or unstructured. However, it is also possible that the throttle 13 is designed as a labyrinth throttle 13, which in a known manner has several grooves and webs on its surface facing the shaft, which form a comb-like profile, which is usually referred to as a labyrinth.
  • the five storage chambers 11 are each designed as an annular space that extends around the shaft 5. All of the storage chambers 11 are provided in the housing 4 or in a component that is stationary with respect to the housing and surrounds the shaft 5.
  • the storage chambers 11 can be produced in the housing 4, for example, by machining processes.
  • all five storage chambers 11 have the same volume, so the total volume of all storage chambers 11 is five times the volume of a storage chamber 11. It is understood that it is not necessary that all storage chambers 11 have the same volume, it is entirely possible design the storage chambers 11 with different volumes.
  • the barrier fluid is circulated in the cooling circuit by means of the circulation impeller 8, the return of the barrier fluid to the outlet 44, for example - as in FIG Fig. 1 shown schematically - takes place from that storage chamber 11 which is closest to the drive 3.
  • the return at another point, for example between the drive 3 and the storage chamber 11 closest to it.
  • the barrier fluid is not completely returned through the outlet 44, but there is a controlled leakage flow of the barrier fluid from the drive 3 through the five storage chambers 11 and the throttle bushing 13 into the pump 2.
  • This leakage flow reliably prevents process fluid from flowing in the opposite direction from the pump 2 along the shaft 5 in the direction of the drive.
  • the Volume of barrier fluid that is introduced into the pump 2 and thus into the process fluid by the controlled leakage flow is lost to the cooling circuit, but is replaced by means of the injection device 92 by new barrier fluid that is introduced into the cooling circuit.
  • the embodiment according to the invention with the storage chambers 11 for the barrier fluid protects the drive 3 in a sufficient manner against the penetration of the barrier fluid, as in the following with reference to FIG Fig. 2 is explained.
  • a failure of the subsequent delivery of barrier fluid combined with a decrease in volume of the barrier fluid in the cooling circuit means that the process fluid can now exit the pump 2 along the shaft 5 or, depending on the circumstances, is sucked in the direction of the drive 3.
  • This is in Fig. 2 indicated by the arrows provided with the reference character P.
  • the process fluid then first reaches the first storage chamber 11, which is closest to the pump 2. Like all other storage chambers 11, this storage chamber 11 is still filled with pure barrier fluid, which is locked there. As a result, the process fluid is mixed with the barrier fluid in this first storage chamber 11, as a result of which the process fluid is greatly diluted.
  • the process fluid is in Fig. 2 symbolically represented by the small lines (without reference symbols) in the storage chambers 11.
  • the process fluid which is now clearly diluted, reaches the next storage chamber 11 via the throttle gap 12, which is initially still completely filled with pure barrier fluid.
  • the already diluted process fluid is further diluted by the barrier fluid before this further diluted mixture can advance through the next throttle gap 12 into the adjacent storage chamber 11.
  • This process continues into the storage chamber 11 which is closest to the drive 3.
  • the process fluid is most diluted in this last storage chamber 11 in front of the drive 3. Only from this last storage chamber 11, the highly diluted process fluid such as the one indicated by the arrow with the reference symbol P1 in FIG Fig. 2 indicates get through the radial bearing 6 in the drive 3.
  • the process fluid in the last storage chamber 11 in front of the drive 3, which can possibly penetrate into the drive 3, is already diluted to such an extent that it cannot cause any damage to the drive 3 for the time being.
  • the barrier fluid contaminated with the process fluid is removed from the drive 3 (if it has penetrated there) as well as from the newly supplied barrier fluid also successively pushed out of the storage chambers 11 and conveyed into the pump 2. After this flushing of the drive 3 and the storage chambers 11, the drive 3 and the storage chambers 11 are again filled with pure barrier fluid, so that normal operation can be continued.
  • Fig. 5 illustrates the mode of operation of the configuration according to the invention of the combination 10 with the storage chambers 11 when a fault occurs.
  • the malfunction is that the injection device fails, so that no more barrier fluid can be introduced into the cooling circuit.
  • the barrier fluid in the cooling circuit is cooled by 10K, for example by reducing the speed of the drive 3 and / or by a temperature change in the heat transfer medium, e.g. B. cooling water, the heat exchanger 9.
  • the five storage chambers 11 see Fig.
  • the cooling circuit 2 have a total volume that is approximately 1.3% of the volume of the cooling circuit, the volume of the cooling circuit being composed of the volume that is available to the barrier fluid in drive 3 and the volumes in heat exchanger 9, line 91 and all connections between the inlet 43 and the outlet 44.
  • An oil is used as the barrier fluid which has a thermal expansion coefficient of 0.7 ⁇ 10 -3 / K in relation to the volume.
  • the diagram in Fig. 5 shows the development over time of the relative volume VP of the process fluid for the five storage chambers 11 (see Fig. 2 ).
  • the time T is plotted on the horizontal axis and the relative volume VP of the process fluid in one of the storage chambers 11 on the vertical axis.
  • the curve K1 shows the relative volume VP for the first storage chamber 11, which is the storage chamber 11, that of the pump 2 or the impeller 21 is closest. In Fig. 2 this is the uppermost storage chamber 11 according to the illustration.
  • the curves K2, K3, K4, K5 show in an analogous manner the relative volume of the process fluid in the adjacent storage chambers 11, the numbering of the storage chambers 11 in their in Fig. 2 corresponds to the order shown.
  • the curve K2 indicates the relative volume VP of the process fluid in the second storage chamber 11, which is arranged immediately adjacent to the first storage chamber 11, etc.
  • the curve K5 indicates the relative volume VP of the process fluid in the storage chamber 11 which is closest is on drive 3.
  • t1 indicates the point in time at which the process fluid begins to enter the first storage chamber 11 when the above-described malfunction occurs, i.e. shortly before point in time t1, all five storage chambers 11 are just filled with pure barrier fluid. From the point in time t1, the process fluid penetrates the first storage chamber 11 at a constant flow rate. This flow rate is approximately such that a quantity of process fluid enters the first storage chamber 11 per time interval t2-t1, which amount corresponds to approximately a quarter of the volume of the first storage chamber 11.
  • FIG. 5 clearly illustrates the dilution effect, which increases from storage chamber to storage chamber, which results from the mixing of the process fluid with the barrier fluid.
  • the relative volume fraction of the process fluid in the first storage chamber 11 has already risen to more than 90%
  • the relative volume fraction of the process fluid in the last storage chamber 11 is only about a quarter, i.e. about 25%.
  • a particular advantage of the configuration according to the invention is that no sealing arrangement is necessary between the drive 3 or the upper radial bearing 6 and the pump 2, which is based on direct physical contact between rotating and stationary parts.
  • mechanical seals can be dispensed with here, which have proven to be problematic and prone to failure, especially at high temperatures and / or high process pressures.
  • a total of four storage chambers 11 are arranged one behind the other with respect to the axial direction, each of which is designed as an annular space around the axial direction A.
  • all of the storage chambers 11 are provided in the shaft 5.
  • the second in Fig. 4 In the variant shown, a total of six storage chambers 11 are arranged one behind the other with respect to the axial direction, each of which is designed as an annular space around the axial direction A.
  • the storage chambers 11 are provided alternately in the housing 4 or in a part which is stationary with respect to the housing and in the shaft 5.
  • the storage chambers 11 provided in the housing 4 have a different volume, here a larger volume, than those provided in the shaft 5.
  • the storage chambers 11 designed as an annular space in the shaft 5 or in the housing 4 are in the Fig. 2-4 each shown with a rectangular cross section in a section along the axial direction A.
  • This cross section can of course also have other shapes, for example the cross section can be U-shaped or V-shaped.
  • the storage chambers 11 can also be designed as sector-shaped recesses in the housing 4 and / or in the shaft, i.e. the storage chambers 11 do not have to extend over the entire circumference around the shaft 5.
  • the volumes of the individual storage chambers 11 can also be different (see e.g. Fig. 3 ), also the volume of those storage chambers 11 which are arranged in the housing 4 or those storage chambers 11 which are arranged in the shaft.
  • a suitable choice of the number of storage chambers 11 depends on the particular application. For a large number of configurations it is advantageous if at least three storage chambers 11 and a maximum of ten storage chambers 11 are provided.
  • the total volume of all storage chambers 11 can also be adapted to the respective application. According to the invention, the total volume of the storage chambers 11 is determined on the basis of the volume reduction of the barrier fluid in the cooling circuit to be expected during operation or in the event of a malfunction. For many applications it has proven to be advantageous if the total volume of all storage chambers 11 is at least 0.5% and at most 4%, preferably at most 3% and especially at most 2% of the volume available in the cooling circuit for the barrier fluid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (14)

  1. Une unité d'entraînement de pompe pour pomper un fluide de processus, avec un boîtier commun (4) renfermant une pompe (2) ayant une roue (21) pour la rotation autour d'une direction axiale (A) et un entraînement (3) pour la pompe (2), avec un arbre (5) pour entraîner la roue (21), qui relie l'entraînement (3) à la pompe (2), et avec un étranglement (13) qui s'étend autour de l'arbre (5) et qui est prévu entre la roue (21) et l'entraînement (3), dans laquelle le boîtier présente une entrée de pompe (22) et une sortie de pompe (23) pour le fluide de processus, dans laquelle une entrée (43) pour un fluide de barrage est prévue, par laquelle le fluide de barrage peut être introduit dans l'entraînement (3), et une sortie (44) pour le fluide de barrage, par laquelle le fluide de barrage peut être déchargé du boîtier (4), dans laquelle la sortie (44) et l'entrée (43) pour le fluide de barrage sont reliées entre elles par un conduit (91) de manière à former un circuit de refroidissement pour le fluide de barrage, dans laquelle le circuit de refroidissement comprend un échangeur de chaleur (9), dans laquelle une pluralité de chambres de stockage (11) pour le fluide de barrage est prévue sur l'arbre (5) dans la zone entre l'étranglement (13) et l'entraînement (3), lesquelles chambres de stockage (11) sont disposées les unes derrière les autres par rapport à la direction axiale (A), et dans laquelle deux chambres de stockage adjacentes (11) sont respectivement en communication fluidique l'une avec l'autre, et dans laquelle les chambres de stockage (11) présentent un volume total qui est au moins aussi grand que le changement de volume du fluide de barrage induit thermiquement dans le circuit de refroidissement en cas de diminution de la température du fluide de barrage d'une valeur prédéterminable.
  2. Une unité d'entraînement de pompe selon la revendication 1, dans laquelle chaque chambre de stockage (11) est conçue comme un espace annulaire autour de la direction axiale (A).
  3. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle deux chambres de stockage adjacentes (11) sont respectivement en communication fluidique par une fente d'étranglement (12), dans laquelle l'arbre (5) forme respectivement une surface limite de la fente d'étranglement (12).
  4. Une unité d'entraînement de pompe selon l'une des revendications précédentes avec au moins trois et aux plus dix chambres de stockage (11).
  5. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle au moins une des chambres de stockage (11) est prévue dans le boîtier (4).
  6. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle au moins une des chambres de stockage (11) est prévue dans l'arbre (5).
  7. Une unité d'entraînement de pompe selon l'une des revendications 1 à 5, dans laquelle toutes les chambres de stockage (11) sont prévues dans le boîtier (4).
  8. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle un dispositif d'injection (92) est prévu pour remettre de fluide de barrage.
  9. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle le volume total de toutes les chambres de stockage (11) est au moins deux fois plus grand que le changement de volume du fluide de barrage induit thermiquement dans le circuit de refroidissement en cas de diminution de la température du fluide de barrage de la valeur prédéterminable.
  10. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle le volume total de toutes les chambres de stockage (11) est au moins de 0,5 % et au plus de 4 %, de préférence au plus de 3 %, du volume disponible dans le circuit de refroidissement pour le fluide de barrage.
  11. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle le boîtier (4) est conçu comme un boîtier de pression, de préférence pour une pression de service d'au moins 200 bars.
  12. Une unité d'entraînement de pompe selon l'une des revendications précédentes, conçue pour un fluide de processus ayant une température supérieure à 400°C.
  13. Une unité d'entraînement de pompe selon l'une des revendications précédentes, dans laquelle l'entraînement (3) est disposé en dessous de la pompe (2) par rapport à la verticale, ou est disposé à côté de la pompe (2) par rapport à l'horizontale.
  14. Une unité d'entraînement de pompe selon l'une des revendications précédentes, conçue comme une pompe ebullator pour la circulation d'un fluide de processus.
EP16192508.6A 2015-11-02 2016-10-06 Unité d'entraînement de pompes destinée à transporter un fluide de processus Active EP3163086B1 (fr)

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US10584713B2 (en) 2018-01-05 2020-03-10 Spectrum Brands, Inc. Impeller assembly for use in an aquarium filter pump and methods
DE102018206012A1 (de) * 2018-04-19 2019-10-24 Zf Friedrichshafen Ag Flüssigkeitskühlsystem für eine elektrische Maschine
CN108512343B (zh) * 2018-06-15 2023-12-01 博远机电（嘉兴）有限公司 永磁电动机及潜水泵
JP7202596B2 (ja) * 2018-06-19 2023-01-12 株式会社アガツマ 軸受パッキン及び給水ポンプ
SG10201912904SA (en) * 2019-02-18 2020-09-29 Sulzer Management Ag Process fluid lubricated pump and seawater injection system
EP4012186A1 (fr) * 2020-12-08 2022-06-15 Sulzer Management AG Pompe lubrifiée par fluide de processus et système de pompage de fluide

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ES2862205T3 (es) 2021-10-07
MX367092B (es) 2019-08-05
SG10201608398XA (en) 2017-06-29
CN106837809B (zh) 2020-10-30
BR102016024334A2 (pt) 2017-05-02
CN106837809A (zh) 2017-06-13
KR20170051267A (ko) 2017-05-11
RU2728509C2 (ru) 2020-07-30
AU2016244242B2 (en) 2021-06-03
KR102565709B1 (ko) 2023-08-09
AU2016244242A1 (en) 2017-05-18
US10634155B2 (en) 2020-04-28
RU2016140729A (ru) 2018-04-18
MX2016013665A (es) 2017-08-09
US20170122324A1 (en) 2017-05-04
CA2944273A1 (fr) 2017-05-02
EP3163086A1 (fr) 2017-05-03
RU2016140729A3 (fr) 2020-03-02

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