EP3832143A1 - Pompe dotée d'un dispositif de levage - Google Patents

Pompe dotée d'un dispositif de levage Download PDF

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Publication number
EP3832143A1
EP3832143A1 EP20204775.9A EP20204775A EP3832143A1 EP 3832143 A1 EP3832143 A1 EP 3832143A1 EP 20204775 A EP20204775 A EP 20204775A EP 3832143 A1 EP3832143 A1 EP 3832143A1
Authority
EP
European Patent Office
Prior art keywords
pump
spring
shaft
pressure
thrust
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Withdrawn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
EP20204775.9A
Other languages
German (de)
English (en)
Inventor
Andreas Wild
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.)
Sulzer Management AG
Original Assignee
Sulzer Management AG
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 Sulzer Management AG filed Critical Sulzer Management AG
Publication of EP3832143A1 publication Critical patent/EP3832143A1/fr
Withdrawn legal-status Critical Current

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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0416—Axial thrust balancing balancing pistons
    • 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
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • 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
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • 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
    • F04D1/06—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/85—Starting

Definitions

  • the invention relates to a pump with a lifting device according to the preamble of the independent claim.
  • Bearings are used wherever forces that act in certain directions have to be compensated or where movements of an object in the undesired directions have to be prevented. Basically two types of bearings are used in pumps, radial and axial bearings.
  • a relief disc is installed on the pressure side of the shaft, the function of which depends on the pump pressure. If the pumped liquid does not have the necessary pressure, e.g. when starting or stopping the pump, the relief disc and counter disc may come into contact. This causes wear, which can ultimately lead to the failure of the system. Lifting devices are used to bridge the critical phases when starting and stopping. Since the relief disks lie on top of one another when the pump unit is at a standstill, contact occurs at low speeds, ie when the pump unit is started up and shut down, and thus signs of wear.
  • a centrifugal pump with a lifting device and an electromagnetic bearing is known.
  • Relief devices have been used for a long time to compensate for axial thrust when a centrifugal pump is running.
  • a typical relief device of a centrifugal pump comprises a rotating relief disc and a stationary counterbalance relief disc, which form a gap running in the radial direction through which part of the fluid under pressure in the centrifugal pump flows to the outside.
  • the shaft of the centrifugal pump is kept in a state of equilibrium in the axial direction, between the force caused by the axial thrust and the counterforce caused by the relief device.
  • transition phases can occur, for example when starting up or shutting down, during which the fluid can have a low pressure so that the shaft cannot be kept in a state of equilibrium.
  • the two disks of the relief device touch each other, which could damage them.
  • a force is exerted on the axial position of the shaft during the transition phase or when the centrifugal pump is at a standstill by means of a controlled electromagnet in such a way that the two disks of the relief device do not touch.
  • This known device has the disadvantage that the axial position of the shaft must be detected with a sensor and regulated with the aid of controllable electromagnets.
  • the known device has the further disadvantage that, on the one hand, the maximum possible displacement path in the axial direction is very small and, on the other hand, the lifting device cannot be in contact with a pumped liquid or a pumped fluid, which means that further seals are required.
  • a relief element which is rotatably coupled to the shaft.
  • a throttle gap is formed with the counter-element in that a device for keeping the relief element spaced from the counter-element is arranged on the counter-element.
  • the facility for Spacer has a force element, preferably a spring, which generates a force in the opposite direction to the axial thrust.
  • This known device has the disadvantage that the device for maintaining a spacing presses against the relief element in the start-up state and in the start-up state and causes wear there.
  • the object of the invention is therefore to provide a pump with a lifting device with a simple structural design which avoids the disadvantageous effects known from the prior art, in particular can be in contact with a pumped fluid and also has reduced wear.
  • the invention relates to a pump with a lifting device for compensating an axial thrust of a shaft of the pump in a predeterminable operating state, in particular during a start-up state and / or a shut-down state of the pump.
  • the pump comprises a housing with an inlet for a fluid on a low-pressure side and an outlet for the fluid on a high-pressure side of the pump, in which housing the shaft is arranged; as well as a relieving element connected non-rotatably to the shaft and a counter element connected to the housing.
  • the pump is characterized in that the lifting device comprises a spring and a thrust element connected non-rotatably to the shaft, and in a start-up state and / or shut-down state of the pump, a spring force opposing the axial thrust can be transmitted to the shaft via the thrust element by means of the spring, so that the Relief element and the corresponding counter element are separated from one another, a contact element being arranged between the spring and the push element.
  • a side of the contact element facing the thrust element is flow-connected to the high-pressure side in this way, as well one side of the contact element facing the spring is fluidically connected to the low-pressure side in such a way that the thrust element and the contact element can be spaced apart by a pressure difference that can be generated between the side of the contact element facing the spring and the side of the contact element facing the thrust element.
  • an axial thrust is generally to be understood as the effect of a force which acts on the shaft of the pump in the axial direction and which is caused by the rotation of the pump wheels of the pump.
  • the spring is generally to be understood as an element which generates a force opposing the axial thrust, for example by expanding an elastic element.
  • a spring is to be understood as a spring which exerts a spring force that correlates with the spring constant.
  • the spring can be designed, for example, as a spiral spring or a plate spring.
  • a start-up state is generally understood to mean the state of the pump in which the pump is started and starts up, in particular the state in which no or an insufficient lubricant film has yet formed between the counter-element and the relief element, in particular the state in which the spring force is so greater than the axial thrust that the relief element and the counter element are separated from one another.
  • a shutdown state is generally understood to mean the state of the pump in which the pump is stopped and shuts down, in particular the state in which the lubricant film between the counter-element and the relief element decreases, in particular the state in which the spring force is so greater than the axial thrust is that the relief element and the counter element are separated from each other.
  • a lubricating fluid is generally to be understood as a substance with lubricating properties; in particular, a lubricating fluid can also be a lubricant. In practice it can Lubricating fluid can be the pumped product / fluid, so that the pump is designed as a product-lubricated pump.
  • a delivery pressure is generated by the rotation of the shaft with the pump wheels, so that the fluid is delivered from the inlet on the low-pressure side to the outlet on the high-pressure side of the pump.
  • This delivery pressure is used in the pump according to the invention to space the contact element and the push element so that wear of the contact element and the push element after the start-up state and / or before the shut-down state (i.e. in the "normal" operating state) can be avoided.
  • the lifting device can thus be protected from wear and tear during the normal operating state by means of the device according to the invention, since the delivery pressure or the pressure difference in the delivery pressure at different points of the pump prevents frictional contact between the contact element and the pusher element. So there is no effect of the spring force on the thrust element.
  • axial pressure on the thrust element (the spring force of the spring) separates the relief element and the counter element from each other in order to prevent wear of the relief element and the counter element due to insufficient lubrication.
  • the spring force acts in particular parallel to an axis of the shaft, so that the axial thrust of the pump shaft can be compensated for in the start-up state and / or in the shut-down state.
  • a film of lubricant forms between the relief element and the counter-element, so that the relief element and counter-element can run on each other essentially without wear, mediated by a lubricating film of a lubricating fluid located between them.
  • the pump according to the invention can preferably be a product-lubricated pump, so that the lubricating fluid corresponds to the fluid conveyed.
  • the pump according to the invention can comprise a relief chamber arranged in the housing, the side of the contact element facing the spring being in flow connection with the low-pressure side via the relief chamber.
  • the spring is preferably designed as a spiral spring, plate spring or as an elastic element.
  • the contact element and the spring can be designed as a single component.
  • the spring could also be designed as a tension spring, which can be transmitted to the shaft via the thrust element by means of a contraction that generates a spring force opposing the axial thrust.
  • the tension spring could be tensioned between the housing and the contact element in order to generate the spring force directed in the opposite direction to the axial thrust.
  • the spring By means of a pressure that can be generated between the push element and the contact element, the spring could be expanded in such a way that the contact element is spaced apart from the push element.
  • the pressure difference that can be generated can correspond to a pressure difference between a suction pressure and a pump pressure of the pump.
  • the suction pressure is a pressure at the inlet of the pump and the pump pressure is a pressure at a pumping stage of the pump.
  • the pressure difference between the pump pressure and suction pressure corresponds to a value such that the contact element is moved in the direction of the thrust element (opposite direction to the axial thrust).
  • There is not a sufficiently large pressure difference to overcome the spring force which means that the contact element is moved in the direction of the spring force and is in contact with the thrust element in order to separate the relief element and the corresponding counter-element from one another.
  • the suction pressure is lower than the pumping pressure, whereby the contact element is moved away from the thrust element (in the direction of axial thrust), i.e. in the opposite direction of the spring force, in order to avoid contact with the thrust element rotating with the shaft.
  • a high pressure chamber, which between the contact element and The thrust element is arranged, is filled with the fluid in the operating state and is under the pumping pressure (flow-connected to the pumping stage).
  • a low-pressure space on the side of the contact element which faces the spring (in which the spring is arranged) is filled with the fluid and is under the suction pressure (in flow connection with the inlet of the pump).
  • the contact element and the spring are arranged on the housing of the pump.
  • a seal can preferably be arranged between the contact element and the housing in order to seal the high-pressure space and the low-pressure space from one another.
  • the seal is thus arranged between the contact element and the housing in such a way that the side of the contact element facing the spring and the side of the contact element facing the pushing element are sealed off from one another.
  • the pump can be designed as a multi-stage pump with at least a first pump stage and a second pump stage.
  • the side of the thrust element facing the spring is flow-connected to the first or the second pump stage and the side of the contact element facing the spring is flow-connected to the suction side.
  • the pumping pressure corresponds to the pressure of the first or second pumping stage.
  • the side of the contact element facing the spring can be flow-connected to the first pump stage and the side of the contact element facing the thrust element can be flow-connected to a higher pump stage (pump stage with higher pressure in the direction of the outlet).
  • the contact element can be designed as a pressure ring, which is a disk-shaped ring, in particular a disk-shaped circular ring, which is arranged between the thrust element and the spring for power transmission and is usually made of a suitable metal or another suitable material, so that the axially acting spring forces can be suitably transmitted to the shaft by means of the pressure ring via the thrust element.
  • the pump can comprise a plurality of contact elements, each between a spring and the thrust element are arranged.
  • the pump can thus also comprise a multiplicity of springs, preferably an equal number of springs and contact elements.
  • the pump can comprise a single spring which is wrapped around the shaft (or a stub shaft / attachment), in particular around a cylindrical ring in the housing.
  • the shaft of the pump is rotatably mounted in a shaft bearing.
  • the shaft bearing is preferably a pure radial bearing.
  • the radial bearing is particularly preferably product-lubricated.
  • the radial bearing can comprise silicon carbide or consist of silicon carbide.
  • the radial bearing can be a plain bearing.
  • An axial bearing of the pump can preferably take place through the relief element and the counter element.
  • the relief element and / or the counter element can be designed as a disk.
  • the pump according to the invention can therefore in particular be designed as a pump with product-lubricated bearings, which as a rule has a very compact design, since most of the parts are in direct contact with the fluid. As a result, no additional oil-lubricated bearings and thus no mechanical seals are required to separate the bearings from the fluid. Because of this, the lifting device is designed in such a way that it can work in contact with the fluid.
  • the lifting device can be arranged on the drive side and / or on the non-drive side.
  • the lifting device is preferably arranged on the non-drive side at one end of the shaft.
  • the relief element is preferably non-rotatably connected to the shaft and the counter-element is arranged stationary on the housing, i.e. immovably, connected to the pump housing, so that an axial movement of the shaft causes a displacement of the relief element against the counter-element.
  • the spring can wrap around the pump shaft, i.e. be arranged around the pump shaft, in particular around the cylindrical ring in the housing or around an attachment arranged on the end of the shaft (also stub shaft).
  • the lifting device can comprise several springs, in particular three or four springs, which are arranged at the same distance along a circumference of the shaft on the housing.
  • a contact surface of the relief element and / or of the counter-element can be coated, in particular coated with ceramic.
  • the relief element and / or the counter element can comprise a fiber-reinforced composite material or a thermoplastic, in particular a polyether ketone.
  • the relief element and / or the counter element can be made from one or more of these materials, in particular also from a composite material.
  • the relief element and the counter element can also simply be made of steel without having special coatings, since wear of the relief element and counter element is avoided by the lifting device. In this way, the costs of the relief element and the counter element in particular can be reduced without premature wear and tear occurring,
  • Fig. 1 shows a schematic representation of a pump 1 according to the invention.
  • the pump 1 is designed as a product-lubricated multistage pump 1 and comprises a lifting device 10 for compensating for an axial thrust A of a shaft 2 of the pump 1 in a predeterminable operating state, in particular during a start-up state and / or shutdown state of the pump 1.
  • the pump 1 is product-lubricated, a very compact design is made possible, since most of the parts are in direct contact with a fluid.
  • no additional oil-lubricated bearings are required and thus no mechanical seal to separate the bearings from the fluid.
  • the lifting device 10 is also designed in such a way that it can work in contact with the fluid.
  • the pump 1 further comprises a housing 3 in which the shaft 2 is arranged, and which housing 3 comprises an inlet for a fluid on a low-pressure side and an outlet for the fluid on a high-pressure side of the pump 1, the pump also having a rotationally fixed the relief element 5 connected to the shaft 2 and a counter element 6 connected to the housing 3.
  • the lifting device 10 comprises a spring 11 and a thrust element 12 that is non-rotatably connected to the shaft 2.
  • a contact element 13 is arranged between the spring 11 and the thrust element 12, which, like the spring 11, is arranged on the housing 3.
  • the housing 3 can be configured in several parts and comprise a pump housing and a housing part for the lifting device 10.
  • the housing part for the lifting device 10 is arranged, in particular screwed, on the pump housing.
  • a spring force F opposing the axial thrust A is transmitted via the thrust element 12 to the shaft 2 by means of the spring 11, so that the relief element 5 and the corresponding counter-element 6 are separated from one another.
  • the spring 11 is designed as a compression spring.
  • the delivery pressure is generated by the rotation of the shaft 2 with the pump wheels (not shown here), so that the fluid is delivered from the inlet on the low-pressure side to the outlet on the high-pressure side of the pump 1.
  • This delivery pressure is used in the pump 1 to space the contact element 13 and the thrust element 12 apart in a normal operating state, so that wear after the start-up state and / or before the shut-down state (i.e. in the "normal" operating state) is avoided.
  • the lifting device 10 can prevent wear during the normal operating state, since the side of the contact element 13 facing the thrust element 12 is flow-connected to the high-pressure side, and the side of the contact element 13 facing the spring 11 is flow-connected to the low-pressure side in such a way that the thrust element 12 and the contact element 13 can be spaced apart by a pressure difference that can be generated between the side of the contact element 13 facing the spring 11 and the side of the contact element 13 facing the thrust element 12.
  • the fact that the push element 12 and the contact element 13 are spaced apart means that a distance between the spring 11 and the push element 12 is increased and a distance between the contact element 13 and the push element 12 is increased, the spring 11 being compressed.
  • the spring force F is not transmitted to the push element 12 and there is no contact between the push element 12 and the contact element 13.
  • the pressure difference that can be generated corresponds to a pressure difference between a suction pressure and a pump pressure of the pump 1.
  • the suction pressure is a pressure at the inlet of the pump 1 and the pump pressure is a pressure at a pump stage of the pump 1.
  • the pressure difference between the pump pressure and suction pressure corresponds to a value such that the contact element 13 is moved in the direction of the thrust element 12 (opposite direction to the axial thrust A), i.e. is moved in the direction of the spring force F (looking to the left on Fig. 1 ) and is in contact with the thrust element 12 in order to separate the relief element 5 and the corresponding counter element 6 from one another.
  • the spring force F thus overcomes the pressure difference between the pump pressure and the suction pressure.
  • the suction pressure is so lower than the pump pressure (the spring force F is not large enough to overcome the pressure difference between the pump pressure and the suction pressure) that the contact element 13 is moved away from the thrust element 12 (in the direction of the axial thrust A, to the right with a view to Fig. 1 ) is therefore moved in the opposite direction of the spring force F in order to avoid contact with the thrust element 12 rotating with the shaft 2.
  • a high pressure chamber 120 is arranged between contact element 13 and push element 12. In the operating state, the high-pressure space 120 is filled with the fluid and is under the pump pressure, since it is in flow connection with the pump stage via the lines / bores 121.
  • a low-pressure chamber 130 on the side of the contact element 13 facing the spring 11, in which the spring 11 is arranged, is also filled with the fluid and is under the suction pressure, since it is flow-connected to the inlet of the pump 1 via the bore / line 131, is in particular fluidly connected to the inlet of the pump 1 via the relief chamber 4.
  • the contact element 13 and the spring 11 are arranged on the housing 3 of the pump 1.
  • a seal 30 is arranged between the contact element 13 and the housing 3 in order to seal the high-pressure chamber 120 and the low-pressure chamber 130 from one another.
  • the shaft 2 of the pump 1 is rotatably supported in a shaft bearing 20.
  • the shaft bearing 20 is a pure radial bearing 20.
  • the radial bearing 20 is lubricated product and may comprise silicon carbide. Axial mounting of the pump 1 takes place via the relief element 5 and the counter element 6.
  • the lifting device 10 is arranged on the non-drive side of the pump 1 and the thrust element 12 is preferably screwed onto a stub of the shaft 2 by means of a screw 32.
  • Fig. 2 shows a further schematic representation of a pump 1 according to the invention, which has an analogous structure to the pump according to Figure 1 having.
  • the delivery pressure is generated by the rotation of the shaft 2 with the pump wheels 21, so that the fluid is delivered from the inlet on the low-pressure side to the outlet 100 on the high-pressure side of the pump 1. Due to the delivery pressure, the contact element 13 and the thrust element 12 are spaced apart from one another in the normal operating state, so that wear of the spring 11 / the contact element 13 and the thrust element 12 after the start-up state and / or before the shut-down state (i.e. in the "normal" operating state) is avoided .
  • the pressure difference that can be generated corresponds to the pressure difference between the suction pressure and the pump pressure of the pump 1.
  • the suction pressure is the pressure at the inlet of the pump 1 and the pump pressure is the pressure at the pump stage 101 of the pump 1.
  • the pressure difference between the pump pressure and suction pressure corresponds to a value such that the contact element 13 is moved in the direction of the thrust element 12 (opposite direction to the axial thrust A), i.e. is moved in the direction of the spring force F (to the left with Look at Fig. 2 ) and is in contact with the thrust element 12 in order to separate the relief element 5 and the corresponding counter element 6 from one another.
  • the spring force F thus overcomes the pressure difference between the pump pressure and the suction pressure.
  • the suction pressure is so lower than the pump pressure (the spring force F is not large enough to overcome the pressure difference between the pump pressure and the suction pressure) that the contact element 13 is moved away from the thrust element 12 (in the direction of the axial thrust A, to the right with a view to Fig. 2 ) is therefore moved in the opposite direction of the spring force F in order to avoid contact with the thrust element 12 rotating with the shaft 2.
  • the high pressure chamber 120 is arranged between the contact element 13 and the thrust element 12. In the operating state, the high-pressure chamber 120 is filled with the fluid and is under the pump pressure, since it is in flow connection with the pump stage 101 via the lines / bores 121.
  • the low-pressure chamber 130 on the side of the contact element 13 facing the spring 11, in which the spring 11 is arranged, is also filled with the fluid and is under suction pressure, since it is connected to the inlet via the bore / line 131 and the relief chamber 4 Pump 1 is fluidly connected (since the relief chamber is fluidically connected to the suction port of the pump).

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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 And Applications Of Rotary Liquid Pumps (AREA)
EP20204775.9A 2019-12-02 2020-10-29 Pompe dotée d'un dispositif de levage Withdrawn EP3832143A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19213013 2019-12-02

Publications (1)

Publication Number Publication Date
EP3832143A1 true EP3832143A1 (fr) 2021-06-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20204775.9A Withdrawn EP3832143A1 (fr) 2019-12-02 2020-10-29 Pompe dotée d'un dispositif de levage

Country Status (3)

Country Link
US (1) US20210164484A1 (fr)
EP (1) EP3832143A1 (fr)
CN (1) CN112983889A (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP4538534A1 (fr) 2023-10-10 2025-04-16 Sulzer Management AG Pompe rotative pour transporter un fluide de traitement

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EP0355796A2 (fr) 1988-08-22 1990-02-28 Ebara Corporation Pompe centrifuge possédant un palier magnétique
DE19927135A1 (de) * 1999-06-15 2000-12-21 Ksb Ag Entlastungseinrichtung für mehrstufige Kreiselpumpen
WO2015074903A1 (fr) 2013-11-21 2015-05-28 Ksb Aktiengesellschaft Dispositif de décharge
EP3447302A1 (fr) * 2017-08-23 2019-02-27 Sulzer Management AG Dispositif formant palier d'arbre doté du dispositif de levage

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US8061970B2 (en) * 2009-01-16 2011-11-22 Dresser-Rand Company Compact shaft support device for turbomachines
DE102013208460A1 (de) * 2013-05-08 2014-11-13 Ksb Aktiengesellschaft Pumpenanordnung mit einer Gleitlageranordnung
DE102017127574B3 (de) * 2017-11-22 2019-02-21 Nidec Gpm Gmbh Kühlmittelpumpe mit anwendungsoptimiertem Aufbau und verbessertem Wärmehaushalt
EP3805570A1 (fr) * 2019-10-09 2021-04-14 Sulzer Management AG Pompe centrifuge permettant de transporter un fluide

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EP0355796A2 (fr) 1988-08-22 1990-02-28 Ebara Corporation Pompe centrifuge possédant un palier magnétique
DE19927135A1 (de) * 1999-06-15 2000-12-21 Ksb Ag Entlastungseinrichtung für mehrstufige Kreiselpumpen
WO2015074903A1 (fr) 2013-11-21 2015-05-28 Ksb Aktiengesellschaft Dispositif de décharge
EP3447302A1 (fr) * 2017-08-23 2019-02-27 Sulzer Management AG Dispositif formant palier d'arbre doté du dispositif de levage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4538534A1 (fr) 2023-10-10 2025-04-16 Sulzer Management AG Pompe rotative pour transporter un fluide de traitement

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