EP3936726A1 - Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens - Google Patents

Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens Download PDF

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Publication number
EP3936726A1
EP3936726A1 EP20184583.1A EP20184583A EP3936726A1 EP 3936726 A1 EP3936726 A1 EP 3936726A1 EP 20184583 A EP20184583 A EP 20184583A EP 3936726 A1 EP3936726 A1 EP 3936726A1
Authority
EP
European Patent Office
Prior art keywords
flow
balance
pump
impeller
centrifugal pump
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Withdrawn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
EP20184583.1A
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English (en)
French (fr)
Inventor
Marc Widmer
Arnaldo Rodrigues
Daniele Cimmino
Thomas Welschinger
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
Priority to EP20184583.1A priority Critical patent/EP3936726A1/de
Publication of EP3936726A1 publication Critical patent/EP3936726A1/de
Withdrawn legal-status Critical Current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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D29/0416—Axial thrust balancing balancing pistons

Definitions

  • the invention relates to a centrifugal pump for conveying a fluid and to a method for controlling a discharge flow of a fluid conveyed by a centrifugal pump in accordance with the preamble of the independent claim of the respective category.
  • Centrifugal pumps for conveying a fluid for example a liquid such as water
  • a fluid for example a liquid such as water
  • Centrifugal pumps have a hydraulic unit comprising at least one impeller and in many cases a volute or a diffuser.
  • a shaft is provided for rotating the impeller(s).
  • the at least one impeller may be configured for example as a radial impeller or as an axial or semi-axial impeller or as a helicoaxial impeller.
  • the impeller may be configured as an open impeller or as a closed impeller, where a shroud is provided on the impeller, said shroud at least partially covering the vanes of the impeller.
  • a centrifugal pump may be designed as a single stage pump having only one impeller mounted to the shaft or as a multistage pump comprising a plurality of impellers, wherein the impellers are arranged one after another on the shaft e.g. in an inline arrangement or in a back-to-back arrangement.
  • the balancing device may comprise a balance drum for at least partially balancing the axial thrust that is generated by the rotating impellers.
  • the balance drum is fixedly connected to the shaft of the pump in a torque proof manner. In an inline arrangement of the impellers the balance drum is usually, arranged at the discharge side of the pump between the last stage impeller and a shaft sealing device.
  • the balance drum defines a front side and a back side. The front side is the side facing the last stage impeller.
  • the back side is the side facing the shaft sealing device.
  • a relief passage is provided between the balance drum and a stationary part being stationary with respect to the pump housing.
  • the back side is usually connected to the suction side or an intermediate stage of the pump by means of a balance line.
  • a balance line At the front side of the balance drum the high pressure or the discharge pressure prevails, and at the back side essentially the suction pressure prevails.
  • the pressure difference between the front side and the back side results in a axial force or an axial thrust which is directed in the opposite direction as the axial thrust generated by the rotating impeller(s).
  • the axial thrust that has to be carried by the axial or thrust bearing is at least considerably reduced.
  • the leakage flow along the balance drum results in a decrease of the hydraulic performance or efficiency of the pump.
  • the balance drum is usually arranged between an intermediate stage impeller and the drive end or the non-drive end of the shaft. In any case the pressure at the front side is higher than the pressure at the back side.
  • the performance curve or pump curve of a centrifugal pump for a particular speed is usually given by the H-Q-curve showing the relationship between the head H generated by the pump and the flow Q generated by the pump.
  • the head H is also referred to as the discharge pressure at the outlet of the pump.
  • the centrifugal pump is operated at or very close to the best efficiency point, which is the point on the H-Q-curve, where the hydraulic efficiency of the pump is at maximum.
  • the discharge flow of a centrifugal pump for a given head H is defined and adjusted by the geometry of the hydraulic unit, such as the geometry of the impeller(s) and/or the geometry of the diffuser, e.g. the diffuser throat(s), or the geometry of the volute(s).
  • the geometry of the hydraulic unit is specifically adapted and adjusted. Therefore, changes in the desired discharge flow typically require an adaption of the geometry of the hydraulic unit of the pump. This issue is addressed by the invention.
  • a centrifugal pump for conveying a fluid comprising a pump housing with an inlet at a suction side and an outlet at a discharge side, a hydraulic unit with at least one impeller for conveying the fluid from the inlet to the outlet, a shaft for rotating the impeller about an axial direction, a balance drum fixedly connected to the shaft and arranged adjacent to the at least one impeller, wherein the balance drum defines a front side facing the at least one impeller and a back side, wherein a relief passage is provided between the balance drum and a stationary part configured to be stationary with respect to the pump housing, wherein the relief passage extends from the front side to the back side, wherein a balance line is provided, configured for discharging the fluid from the back side, wherein the hydraulic unit is configured to generate a presettable hydraulic flow, being larger than a presettable discharge flow passing through the outlet, wherein the relief passage is configured such that a balance flow passes through the relief passage, and wherein the balance flow is adjusted to
  • the balance flow passing along the balance drum through the relief passage is used to reduce the hydraulic flow, which is generated by the hydraulic unit, to the discharge flow passing through the outlet of the pump.
  • This measure has the considerable advantage that a universal hydraulic unit may be used for generating different discharge flows. If a second centrifugal pump is required, which shall generate a different discharge flow with preferably the same head than a first centrifugal pump, it is no longer necessary to modify the geometry of the hydraulic unit of the second centrifugal pump, i.e. for the second centrifugal pump the same hydraulic unit may be used as for the first centrifugal pump. Rather than modifying the hydraulic flow generated by the hydraulic unit to change the discharge flow, the balance flow is modified to change the discharge flow.
  • a change of the balance flow may be achieved for example by modifying the geometry of the relief passage extending along the balance drum.
  • the length of the balance drum in the axial direction and therewith the length of the relief passage may be changed and/or the width of the relief passage in the radial direction perpendicular to the axial direction is modified, i.e. the distance between the radially outer surface of the balance drum and the stationary part delimiting the relief passage.
  • the universal hydraulic unit may be used to produce different discharge flows, it is possible to realize various pump curves (H-Q-curves) with the same hydraulic unit.
  • the balance line is configured for connecting the back side with the suction side.
  • the balance line may be in fluid communication with the inlet of the centrifugal pump, e.g. open into the inlet, or the balance line is connected with a reservoir such as a tank at the suction side, from where the fluid is supplied to the inlet.
  • the centrifugal pump comprises a flow control element, which is configured for controlling the balance flow.
  • a flow control element configured for controlling the balance flow.
  • the flow control element is provided in the balance line, because this is a very simple measure to control the balance flow through the balance line.
  • the flow control element is arranged outside of the pump housing, so that the flow control element can be easily accessed.
  • the flow control element is configured as an adjustable valve.
  • This measure has the advantage that the discharge flow may be tuned or adjusted in a very simple manner, namely by only adjusting the flow control element for modifying the balance flow. Furthermore, this measure allows for less tight tolerances with respect to the manufacturing of thy hydraulic components such as the diffuser(s) or the impeller(s). It might even render possible to omit machining operations , for example because the cast accuracy is sufficient.
  • a further advantage is that the discharge flow of the centrifugal pump may be tuned without installing a throttle or any other flow restricting device directly to the discharge. Thus, the requirements of international norms such as API 610 are fulfilled.
  • the tuning of the discharge flow by means of modifying the balance flow is in particular advantageous for applications requiring a very low discharge flow and high heads (discharge pressures). In such applications the sensitivity of the discharge flow both on the geometry of the hydraulic unit and on the balance flow is very high.
  • modifying the balance flow i.e. only one parameter, it becomes possible to adjust the discharge flow to the desired value.
  • the flow control element is configured for changing the balance flow during operation of the centrifugal pump. This measure allows for a readjustment of the discharge flow during operation of the centrifugal pump.
  • the pump is configured as a multistage pump having a plurality of impellers, wherein the impellers are arranged one after another on the shaft (6).
  • the pump is configured as a between-bearing pump.
  • the pump may be configured as a barrel type pump comprising an outer barrel casing, in which the pump housing is arranged.
  • a method for controlling a discharge flow of a fluid conveyed by a centrifugal pump having a pump housing with an inlet at a suction side and an outlet at a discharge side comprising the steps of: providing a hydraulic unit with at least one impeller for conveying the fluid from the inlet to the outlet, providing a shaft for rotating the impeller about an axial direction, providing a balance drum fixedly connected to the shaft and arranged adjacent to the at least one impeller, wherein the balance drum defines a front side facing the at least one impeller and a back side, providing a relief passage between the balance drum and a stationary part configured to be stationary with respect to the pump housing, wherein the relief passage extends from the front side to the back side, providing a balance line, configured for discharging the fluid from the back side, defining the discharge flow, configuring the hydraulic unit to generate a presettable hydraulic flow, being larger than the discharge flow passing through the outlet, and configuring the relief passage such that a balance flow passes through the relief
  • Fig. 1 shows a schematic cross-sectional view of an embodiment of a centrifugal pump according to the invention, which is designated in its entity with reference numeral 1.
  • the pump 1 is designed as a centrifugal pump for conveying a fluid, for example a liquid such as water.
  • the centrifugal pump 1 comprises a pump housing 2 having an inlet 3 and an outlet 4 for the fluid to be conveyed.
  • the inlet 3 is arranged at a suction side S, where a suction pressure prevails, and the outlet 4 is arranged at a discharge side D, where a discharge pressure prevails.
  • the suction pressure is also referred to as low pressure, and the discharge pressure is also referred to as high pressure.
  • the centrifugal pump 1 further comprises a hydraulic unit 5 with at least one impeller 51, 52 for conveying the fluid from the inlet 3 to the outlet 4 as well as a shaft 6 for rotating each impeller 51, 52 about an axial direction A.
  • the axial direction A is defined by the axis of the shaft 6.
  • Each impeller 51 is mounted to the shaft 6 in a torque proof manner.
  • the shaft 6 has a drive end 61, which may be connected to a drive unit (not shown) for driving the rotation of the shaft 6 about the axial direction A.
  • the drive unit may comprise, for example, an electric motor.
  • the other end of the shaft 6 is referred to as non-drive end 62.
  • a direction perpendicular to the axial direction A is referred to as radial direction.
  • the centrifugal pump 1 is configured as a multistage pump 1 having a plurality of impellers 51, 52, wherein the impellers 51, 52 are arranged one after another on the shaft 6.
  • the reference numeral 52 designates the last stage impeller 52, which is the impeller 52 closest to the outlet 4.
  • the last stage impeller 52 pressurizes the fluid to the discharge pressure.
  • the embodiment shown in Fig. 1 has nine stages, which has to be understood exemplary.
  • the plurality of impellers 51, 52 may be arranged in an inline configuration as shown in Fig. 1 or in a back-to-back configuration.
  • Each impeller 51, 52 is designed as a radial impeller.
  • the hydraulic unit 5 further comprises a plurality of stationary diffusers 53, which are stationary with respect to the pump housing 2. Between each pair of adjacent impellers 51, 52 a diffuser 53 is provided for redirecting the generally radial flow exiting from the particular impeller 51 in a generally axial direction A towards the next stage impeller 51, 52.
  • the hydraulic unit 5 comprises the entirety of all impellers 51, 52 and all diffusers 53.
  • the multistage centrifugal pump 1 shown in Fig. 1 is designed as a horizontal pump, meaning that during operation the shaft 6 is extending horizontally, i.e. the axial direction A is perpendicular to the direction of gravity.
  • the centrifugal pump 1 shown in Fig. 1 may be designed as a horizontal barrel casing multistage pump 1, i.e. as a double-casing pump.
  • the multistage pump 1 may be designed, for example, as a pump 1 of the pump type BB5 according to API 610.
  • the centrifugal pump 1 comprises an outer barrel casing 100, in which the pump housing 2 is arranged.
  • the centrifugal pump may be configured without an outer barrel casing, for example as a BB4 type pump, or as an axially split multistage pump, or as a single stage pump, or as a vertical pump, meaning that during operation the shaft 6 is extending in the vertical direction, which is the direction of gravity, or as any other type of centrifugal pump.
  • the centrifugal pump 1 comprises bearings on both sides of the plurality of impellers 51, 52 (with respect to the axial direction A), i.e. the centrifugal pump 1 is designed as a between-bearing pump.
  • a first radial bearing 81, a second radial bearing 82 and an axial bearing 83 are provided for supporting the shaft 6.
  • the first radial bearing 81 is arranged adjacent to the drive end 61 of the shaft 6.
  • the second radial bearing 82 is arranged adjacent to or at the non-drive end 62 of the shaft 6.
  • the axial bearing 83 is arranged between the plurality of impellers 51, 52 and the first radial bearing 81 adjacent to the first radial bearing 81.
  • the bearings 81, 82, 83 are configured to support the shaft 6 both in the axial direction A and in a radial direction, which is a direction perpendicular to the axial direction A.
  • the radial bearings 81 and 82 are supporting the shaft 6 with respect to the radial direction
  • the axial bearing 83 is supporting the shaft 6 with respect to the axial direction A.
  • the first radial bearing 81 and the axial bearing 83 are arranged such that the first radial bearing 81 is closer to the drive end 61 of the shaft 6.
  • it is also possible to exchange the position of the first radial bearing 81 and the axial bearing 83 i.e. to arrange the first radial bearing 81 between the axial bearing 83 and the plurality of impellers 51, 52, so that the axial bearing 83 is closer to the drive end 61 of the shaft 6.
  • a radial bearing such as the first or the second radial bearing 81 or 82 is also referred to as a "journal bearing” and an axial bearing, such as the axial bearing 83, is also referred to as an "thrust bearing”.
  • the first radial bearing 81 and the axial bearing 83 may be configured as separate bearings as shown in Fig. 1 , but it is also possible that the first radial bearing 81 and the axial bearing 83 are configured as a single combined radial and axial bearing supporting the shaft both in radial and in axial direction.
  • the second radial bearing 82 is supporting the shaft 6 in radial direction.
  • an axial bearing for the shaft 6 is provided at the non-drive end 62.
  • a second axial bearing may be provided at the drive end 61 or the drive end 61 may be configured without an axial bearing.
  • the centrifugal pump 1 further comprises two sealing devices, namely a first sealing device 91 for sealing the shaft 6 at the suction side S and a second sealing device 92 for sealing the shaft 6 at the discharge side D.
  • first sealing device 91 is arranged between the hydraulic unit 5 and the second radial bearing 82
  • second sealing device 92 is arranged between the last stage impeller 52 and the axial pump bearing 83.
  • Both sealing devices 91, 92 seal the shaft 6 against a leakage of the fluid along the shaft 6 e.g. into the environment.
  • the sealing devices 91 and 92 the fluid may be prevented from entering the bearings 81, 82, 83.
  • each sealing device 91, 92 comprises a mechanical seal.
  • a mechanical seal is a seal for a rotating shaft 6 and comprises a rotor part fixed to the shaft 6 and rotating with the shaft 6, as well as a stationary stator part fixed with respect to the pump housing 2.
  • the rotor part and the stator part are sliding along each other - usually with a liquid as lubricant and coolant there between - for providing a sealing action to prevent the fluid from escaping to the environment or entering the bearings 81, 82, 83.
  • a separate bearing isolator is provided which prevents liquids or solids to enter the bearings 81, 82, 83.
  • the sealing devices 91, 92 e.g. the mechanical seals prevent the fluid from leaking into the environment.
  • the centrifugal pump 1 further comprises a balance drum 7 for at least partially balancing the axial thrust that is generated by the impellers 51, 52 during operation of the centrifugal pump 1.
  • the balance drum 7 is fixedly connected to the shaft 6 in a torque proof manner.
  • the balance drum 7 is arranged at the discharge side D between the last stage impeller 52 and the second sealing device 92.
  • the balance drum 7 defines a front side 71 and a back side 72.
  • the front side 71 is the side facing the last stage impeller 52.
  • the back side 72 is the side facing the second sealing device 92.
  • the balance drum 7 is surrounded by a stationary part 21, so that a relief passage 73 is formed between the radially outer surface of the balance drum 7 and the stationary part 21.
  • the stationary part 21 is configured to be stationary with respect to the pump housing 2.
  • the relief passage 73 forms an annular gap between the outer surface of the balance drum 7 and the stationary part 21 and extends from the front side 71 to the back side 72.
  • the front side 71 is in fluid communication with the outlet 4, so that the axial surface of the balance drum 7 facing the front side 71 is exposed essentially to the discharge pressure prevailing at the outlet 4 during operation of the pump 1.
  • the pressure prevailing at the axial surface of the balance drum 7 facing the front side 71 may be somewhat smaller than the discharge pressure.
  • the considerably larger pressure drop takes place over the balance drum 7.
  • a chamber 74 is provided, which is connected by a balance line 10 with the suction side S, e.g. with the inlet 3.
  • the pressure in the chamber 74 at the back side 72 is somewhat larger than the suction pressure due to the pressure drop over the balance line 10 but considerably smaller than the discharge pressure.
  • the balance line 10 is provided for recirculating the fluid from the chamber 74 at the back side 72 to the suction side S. A part of the pressurized fluid passes from the front side 71 through the relief passage 73 to the back side 72, enters the balance line 10 and is recirculated to the suction side S of the centrifugal pump 1.
  • the balance line 10 constitutes a flow connection between the back side 72 and the suction side S at the pump inlet 3.
  • the balance line 10 may be arranged - as shown in Fig. 1 - outside the pump housing 2 and outside the barrel casing 100. In other embodiments the balance line 10 may be designed as internal line completely extending within the pump housing 2. In still other embodiments the balance line may be arranged outside the pump housing 2 and inside the barrel casing 100.
  • the balance line 10 may be connected with a reservoir 110 such as a tank 110 at the suction side S, from where the fluid is supplied to the inlet 3 by means of a supply line 111.
  • a reservoir 110 such as a tank 110 at the suction side S
  • the fluid is supplied to the inlet 3 by means of a supply line 111.
  • Fig. 1 This alternative is indicated in Fig. 1 by the dashed line 11.
  • the fluid is recirculated from the chamber 74 at the back side 72 to the tank 110.
  • the balance line is connected to an intermediate stage, for example to the discharge side of one of the impellers 51 or to one of the diffusers 53, so that the pressurized fluid is recirculated from the chamber 74 at the back side 72 to on of the intermediate stages of the pump.
  • the hydraulic unit 5 is configured to generate a presettable hydraulic flow QH.
  • the hydraulic flow QH is the flow, which leaves the last stage impeller 52 (see also Fig. 2 ). In case there is no intermediate take-off at any of the impellers 51, the hydraulic flow QH equals the flow, which is passing through the inlet 3 at the suction side S, where the suction pressure prevails.
  • the generated hydraulic flow QH depends on the geometry of the hydraulic unit 5, e.g. the geometry of the impeller(s) 51, 52 and/or the geometry of the diffuser(s) 53, in particular the diffuser throat.
  • the centrifugal pump 1 shall generate a presettable discharge flow QD at the discharge side D, where the discharge pressure prevails.
  • the discharge flow QD is the flow, which passes through the outlet 4 of the centrifugal pump 1.
  • the hydraulic unit 5 is configured to generate an hydraulic flow QH, which is larger than the desired discharge flow QD.
  • a balance flow QB which is the flow passing through the relief passage 73, is adjusted to reduce the hydraulic flow QH to the discharge flow QD. This will be explained in more detail hereinafter.
  • FIG. 2 shows a cross-sectional view illustrating a configuration of the balance drum 7 and the balance line 10. Since it is sufficient for the understanding, in Fig. 2 only two impellers 51, 52 are shown, which may be for example the first stage impeller 51 and the last stage impeller 52 of a two stage pump 1. It has to be noted that there may be more impellers 51, so that the centrifugal pump is configured as a multistage pump 1 having more than two stages.
  • the balance line 10 is represented partially as a single line in Fig. 2 , wherein the direction of flow through the balance line 10 is indicated by the arrows in the balance line 10 without reference numeral. The flow of the fluid flowing through the pump 1 is indicated in Fig. 2 by the dashed arrows without reference numeral.
  • the hydraulic flow QH is divided into the discharge flow QD, which leaves the centrifugal pump 1 through the outlet 4, and the balance flow QB, which passes through the relief passage 73 into the chamber 74 at the back side 72.
  • the balance flow 10 is recycled from the chamber 74 through the balance line 10 to the inlet 3 at the low pressure side L or to the reservoir 110, respectively.
  • the balance flow QB is adjusted such that it equals the difference between the hydraulic flow QH and the discharge flow QD.
  • the discharge flow QD is tuned to the desired value by adjusting the balance flow QB.
  • the balance flow QB may be adjusted by the geometry of the relief passage 73, which constitutes a throttle.
  • the balance flow QB can be adjusted by the length L of the relief passage 73, which is the extension of the relief passage 73 in the axial direction A, and the width W of the relief passage 73, which is the extension of the relief passage in the radial direction.
  • the length L is given by the extension of the balance drum 7 in the axial direction A.
  • the width W is given by the clearance between the balance drum 7 and the stationary part 26.
  • the balance flow QB may be adjusted such that the balance flow corresponds to the difference between the hydraulic flow QH generated by the hydraulic unit 5 and the desired discharge flow QD passing through the outlet 4 of the centrifugal pump.
  • the centrifugal pump 1 comprises in addition to the relief passage 73 a flow control element 45, which is configured for controlling the balance flow QB.
  • the flow control element 45 may be designed as a throttle or as a orifice or as a valve such as a flow control valve or any other adjustable valve.
  • the flow control element 45 is arranged in the balance line 10. Furthermore, it is preferred that the flow control element 45 is arranged outside of the pump housing 2. In embodiments, where the centrifugal pump 1 comprises the outer barrel casing 100, the flow control element is preferably arranged outside the outer barrel casing 100. Providing the flow control element 45 outside the pump housing 2 or outside the outer barrel casing 100 has the considerable advantage that the flow control element 45 may be modified or replaced by another flow control element in a very simple manner.
  • the flow control element 45 may be configured as a adjustable throttle or as an adjustable valve. This renders possible that the balance flow may be modified online, i.e. when the centrifugal pump 1 is in operation.
  • the discharge flow QD may be modified or tuned during operation of the centrifugal pump 1 by modifying the balance flow by means of the flow control element 45.
  • the flow control element may be configured for a remote control, so that the discharge flow QD may be tuned by means of modifying the balance flow from a remote location, i.e. without physically contacting the centrifugal pump 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP20184583.1A 2020-07-07 2020-07-07 Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens Withdrawn EP3936726A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20184583.1A EP3936726A1 (de) 2020-07-07 2020-07-07 Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens

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Application Number Priority Date Filing Date Title
EP20184583.1A EP3936726A1 (de) 2020-07-07 2020-07-07 Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens

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EP3936726A1 true EP3936726A1 (de) 2022-01-12

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EP20184583.1A Withdrawn EP3936726A1 (de) 2020-07-07 2020-07-07 Anpassung der ausströmmenge einer mehrstufigen pumpe durch einstellung des spiels des entlastungskolbens

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1094592B (de) * 1958-11-10 1960-12-08 Klein Schanzlin & Becker Ag Kreiselpumpe mit konstanter Entlastungsfluessigkeitsmenge
DE1184642B (de) * 1961-04-06 1964-12-31 Klein Schanzlin & Becker Ag Einrichtung zum Schutz von Kreiselpumpen bei Schwach- oder Nullastbetrieb
EP1378667A2 (de) * 2002-07-04 2004-01-07 HERMETIC-PUMPEN GmbH Pumpstand
WO2011078680A1 (en) * 2009-12-23 2011-06-30 William Paul Hancock Turbo-machine thrust balancer
US10215185B2 (en) * 2015-07-23 2019-02-26 Sulzer Management Ag Pump for the conveyance of a fluid with varying viscosity

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1094592B (de) * 1958-11-10 1960-12-08 Klein Schanzlin & Becker Ag Kreiselpumpe mit konstanter Entlastungsfluessigkeitsmenge
DE1184642B (de) * 1961-04-06 1964-12-31 Klein Schanzlin & Becker Ag Einrichtung zum Schutz von Kreiselpumpen bei Schwach- oder Nullastbetrieb
EP1378667A2 (de) * 2002-07-04 2004-01-07 HERMETIC-PUMPEN GmbH Pumpstand
WO2011078680A1 (en) * 2009-12-23 2011-06-30 William Paul Hancock Turbo-machine thrust balancer
US10215185B2 (en) * 2015-07-23 2019-02-26 Sulzer Management Ag Pump for the conveyance of a fluid with varying viscosity

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