EP3295034A1 - Pompe centrifuge à rotor coulissant - Google Patents

Pompe centrifuge à rotor coulissant

Info

Publication number
EP3295034A1
EP3295034A1 EP16733866.4A EP16733866A EP3295034A1 EP 3295034 A1 EP3295034 A1 EP 3295034A1 EP 16733866 A EP16733866 A EP 16733866A EP 3295034 A1 EP3295034 A1 EP 3295034A1
Authority
EP
European Patent Office
Prior art keywords
impeller
main body
centrifugal pump
cover body
impeller main
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.)
Granted
Application number
EP16733866.4A
Other languages
German (de)
English (en)
Other versions
EP3295034B1 (fr
Inventor
Gerald Feichtinger
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.)
Bitter Engineering & Systemtechnik GmbH
Original Assignee
Bitter Engineering & Systemtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bitter Engineering & Systemtechnik GmbH filed Critical Bitter Engineering & Systemtechnik GmbH
Publication of EP3295034A1 publication Critical patent/EP3295034A1/fr
Application granted granted Critical
Publication of EP3295034B1 publication Critical patent/EP3295034B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • 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
    • F04D29/042—Axially shiftable rotors

Definitions

  • the invention relates to a centrifugal pump, in particular water pump, which is designed as a radial pump or Halbaxialpumpe, with a rotatably mounted in a housing about an axis and connected to a drive shaft impeller, which impeller has a rotor blades having impeller main body and a Laufraddeckusion, wherein for adjusting the impeller outlet width the impeller of the impeller main body and the impeller cover body are axially displaceable relative to each other via an adjusting device.
  • Centrifugal pumps which can be regulated by impeller outlet width adjustment, are known.
  • the regulation of the impeller outlet width has the advantage of lower losses and higher efficiency in comparison with a throttle control over split ring valves, as is known, for example, from EP 1 657 446 A2, since no energy is destroyed, but only the energy required in each case Fluid is transferred.
  • the impeller blades are connected to a drive and pressure ⁇ side impeller wheel.
  • the adjustment of the impeller outlet width between an idling position and a pumping position is effected by an intake-side control disk, which has slots corresponding to the impeller blades and co-rotates with the impeller support disk.
  • the US 4,798,517 A discloses a pump with an impeller blades wear ⁇ the impeller whose outlet width is variable by a suction-side control disk, wherein the control disk has the impeller blades corresponding slots to be pushed over the impeller blades.
  • a similar variable geometry centrifugal pump is also known from US 5,169,286 A or US 4,828,455 A, respectively.
  • a disadvantage is that in operating areas of the pump, in which the unneeded ⁇ te impeller blade outlet width through the slots of the control disk protrudes into the water space, relatively high flow losses occur, whereby the efficiency of the pump is deteriorated in these operating areas.
  • Another disadvantage is that this concept applies only to two-dimensional blade Contours, but not for three-dimensional, so spatially curved impeller molds, as they are known for example from AT 506 342 Bl, DE 100 50 108 A or JP S59-165895 A, can use. With three-dimensionally curved impeller blades, the pump efficiency of centrifugal pumps can be significantly improved.
  • the flow rate change is effected by a drive and pressure side axially displaceable control disk.
  • conveying blades are arranged which delimit pump delivery spaces with an axial conveying wall.
  • the pump chambers are axially limited on the axial conveying wall side by the end face of the control disk.
  • US 6,074,167 A discloses a variable geometry centrifugal pump wherein the impeller has an inner disk and an outer ring between which two-dimensional helically-curved impeller blades are interposed. Between the inner disc and the outer ring is an axially displaceable control disc, which has spiral slots for the impeller blades. By axial displacement of the control disc between the inner disc and the outer ring of the impeller by means of a Actuator, the impeller blade length between short impeller blade for low flow rates and long impeller blades for high flow rates can be switched.
  • the invention is therefore an object of the centrifugal pumps - especially with spatially curved impeller geometry - to ensure an active and reliable control with very low drive power over the entire speed and temperature range.
  • the impeller main body is arranged axially displaceable on the drive shaft, wherein the adjusting device is operatively connected to the impeller main body.
  • impeller cover body can deviate from a purely cylindrical disc shape.
  • the front side of the impeller cover body facing the impeller main body may have an area which is concavely curved, for example, which is designed in accordance with the optimum flow conditions in the vane passages.
  • Actively connected means that the adjusting device physically communicates with its function for adjusting the impeller main body with the impeller main body.
  • this compound may be mechanical, hydraulic, pneumatic or electromagnetic type.
  • the inventive design of the impeller results in consequence of the pressure distribution on the impeller a significantly lower axial thrust compared to conventional impeller designs and thus lower adjustment forces.
  • the impeller cover body is rigid, ie non-rotatable and non-displaceable, connected to the pump shaft.
  • the impeller cover body is thus immovably and non-rotatably drivably connected to the drive shaft.
  • the impeller cover body has groove-shaped pockets for receiving the impeller blades on the front side facing the impeller main body, the pockets preferably being closed on the rear side of the impeller cover body facing away from the impeller main body.
  • the depth of the pockets of the impeller cover body is dimensioned so that the pockets when the axial displacement of the impeller main body, the impeller blades completely or - up to a defined minimum impeller outlet width - can accommodate predominantly.
  • the impeller cover body is arranged on the suction side facing away from the impeller main body, and the suction-side impeller main body
  • the impeller main body should be pivotable relative to the impeller cover body about the axis of rotation by at least a defined angular range, to allow a displacement of the impeller blades in and out of the pockets.
  • the angle range is defined by the pitch of the three-dimensionally curved impeller blades. In an axial adjustment of the impeller main body so this is rotated according to the pitch of the impeller blades relative to the angular position of the impeller cover body.
  • the impeller main body is arranged on the side facing away from the drive side of the impeller.
  • the impeller cover body is conveniently arranged on the side facing away from the suction mouth drive side of the impeller.
  • the impeller main body is sealed on the side facing away from the impeller cover body relative to the housing via at least one labyrinth seal. It is particularly advantageous if in each case a labyrinth seal between the impeller main body and the housing of the pump is arranged both in the region of the suction mouth of the impeller, as well as near the exit from the impeller.
  • the labyrinth seal consists in a known manner of intermeshing elements of the impeller main body and the housing, in the simplest case of an annular projection of the one part which engages in a corresponding shaped and dimensioned annular groove of the other part.
  • the adjustment of the impeller main body can be done in various ways mechanically, electromagnetically, pneumatically, hydraulically or thermally.
  • Mechanical adjustments can be realized for example by helical or thrust gear.
  • the adjusting device may comprise a rotatable via an actuator threaded spindle and a spindle nut, wherein the threaded spindle is rotatably mounted within the drive shaft designed as a hollow shaft and the spindle nut is in contact with the impeller main body, and wherein the spindle nut and the Impeller main body in the axial direction immovable, preferably rotatable relative to each other, are connected together.
  • the adjusting device may comprise a sliding gear with a sliding via an actuator push rod, which is connected to a sliding sleeve, wherein the push rod is mounted axially displaceable within the drive shaft designed as a hollow shaft and the push sleeve with the impeller main body is connected, and wherein the thrust sleeve and the impeller main body in the axial direction immovable, preferably rotatable relative to each other, are interconnected.
  • the electromagnetic actuator has at least one electromagnet fixed to the housing and at least one preferably annular permanent magnet fixedly connected to the impeller main body, preferably the at least one permanent magnet in the region of an impeller main body and the housing sealing labyrinth seal is arranged.
  • FIG. 1 shows a centrifugal pump according to the invention in a first embodiment in a longitudinal section.
  • FIG. 2 shows a centrifugal pump according to the invention in a second embodiment in a longitudinal section.
  • FIG. 3 shows a centrifugal pump according to the invention in a third embodiment in a longitudinal section
  • FIG. 4 shows a centrifugal pump according to the invention in a fourth embodiment in a longitudinal section in a first end position.
  • FIG. 6 shows a centrifugal pump according to the invention in a fifth embodiment in a longitudinal section in a first end position.
  • FIG. 7 shows this centrifugal pump in a second end position in a longitudinal section
  • FIGS. 6 and 7 shows an impeller of the centrifugal pump shown in FIGS. 6 and 7 in an oblique view. Functionally identical parts are provided in the embodiments with the same reference numerals.
  • FIGS. 1 to 7 each show a centrifugal pump 1 with a two-part housing 2, in which a multi-part impeller 3 is arranged.
  • the impeller 3 is composed of an impeller main body 4 and an impeller cover body 5, wherein a plurality of three-dimensionally curved impeller blades 6 are fixedly connected to, for example, integral with the impeller main body 4.
  • the impeller cover body 5 is non-rotatably and also non-displaceably connected to a drive shaft 7, which is mounted by means of shaft bearings 9 in the housing 2 rotatably about the axis 8.
  • the drive shaft is driven, for example via a pulley 7a via a traction means not further shown.
  • the impeller main body 4 is mounted in each case axially displaceable on the impeller cover body 5. A direct connection between the drive shaft 7 and impeller main body 4 is not provided in the examples.
  • the impeller main body 4 is disposed on the suction side 10 of the centrifugal pump 1 and forms the suction port 11.
  • the impeller cover body 5 is arranged on the drive side 12 and has a front side 13 facing the impeller main body 4 which, together with the impeller blades 6 and the inner side 14 of the impeller main body 4, spans closed blade channels 15.
  • the impeller cover body 5 has on the front side 13 groove-like pockets 16, which are formed according to the three-dimensional curvature of the impeller blades 6.
  • the pockets 16 are designed to be closed towards the rear wheel 17 of the wheel cover body 5 facing away from the wheel main body 4 and designed so that the wheel blades 6 can be inserted at least predominantly.
  • the impeller blades 6 and the pockets 16 form a positive fit in the direction of rotation, so that the impeller main body 4 is driven via this form fit by the impeller cover body 5, while the impeller cover body 5 is driven directly by the drive shaft 7.
  • the housing 2 of the centrifugal pump forms an outlet spiral 2a.
  • the suction-side impeller main body 4 is mounted axially displaceably in the hub 5a of the impeller cover body 5.
  • the impeller blades 6 of the impeller main body 4 can dip in the pockets 16, whereby the impeller vane outlet width b between a minimum value and a maximum value can be adjusted by displacing the impeller main body 4.
  • a smooth sliding of the impeller main body 4 on the impeller cover body 5 can be achieved when the impeller material is modified with lubricants.
  • the pockets 16 in the impeller cover body 5 may be covered with a cover 17 forming the back 17 of the impeller cover body 5b in order to avoid pressure-side flow losses.
  • labyrinth seals 20, 21 are arranged between the impeller main body 4 and the housing 2, wherein in the embodiment variants shown in FIGS first labyrinth seal 20 in the region of the suction mouth 11 and an outer second labyrinth seal 21 in the region of the pressure side 18 facing outer diameter 4b of the impeller main body 4 is provided.
  • first labyrinth seal 20 in the region of the suction mouth 11 and an outer second labyrinth seal 21 in the region of the pressure side 18 facing outer diameter 4b of the impeller main body 4 is provided.
  • the first and second labyrinth seals 20, 21 are combined and arranged directly adjacent.
  • Each labyrinth seal 20, 21 consists of intermeshing elements 20a, 20b; 21a, 21b of the impeller main body 4 and the housing 2, that is, for example, an annular projection 20a, 21a of the one part, for example, the impeller main body 4, which engages in a corresponding annular groove 20b, 21b of the other part, for example, the housing 2.
  • the cylindrical projections 20a, 21a form, together with the corresponding annular grooves 20b, 21b of the housing 2, the labyrinth seals 20, 21.
  • the impeller main body 4 is moved via an adjusting device 22 in the axial direction along the axis 8 of the drive shaft 7 - in the embodiment variants shown in FIGS. 1 to 5 against the force of a restoring force formed by a return spring 23.
  • the adjustment of the impeller main body 4 can be effected in various ways mechanically, electromagnetically, pneumatically, hydraulically or thermally.
  • a mechanical adjustment in FIG. 3, an electromagnetic adjustment is provided.
  • Fig. 1 shows a first embodiment of the invention, wherein the adjusting device 22 has a helical gear 24 with a rotatable via an actuator 25 threaded spindle 26 and a spindle nut 27, wherein the threaded spindle 26 and the spindle nut 27 are formed as a coarse thread drive.
  • the threaded spindle 26 is rotatably supported within the formed as a hollow shaft drive shaft 7 via slide bearings 19 and secured axially. Between the threaded spindle 26 and the drive shaft 7, a seal 19 a is arranged.
  • the spindle nut 27 is connected to the impeller main body 4, wherein the spindle nut 27 and the impeller main body 4 are non-slidably and rotatably connected with each other in the axial direction.
  • the threaded spindle 26 can be rotated via the actuator 25 clockwise or counterclockwise.
  • the spindle nut 27 is in unregulated operation, for example in case of failure of the actuator 25, of the bearing in the impeller cover 5, designed as a compression spring return spring 23, the hub 4a of the impeller main body 4 and a thrust bearing 28 moves against a stop 29 on the threaded spindle 26, thereby fail-safe setting the maximum impeller outlet width bmax.
  • the spindle nut 27 In controlled operation, the spindle nut 27, depending on the required function, via the actuator 25 and the threaded spindle 26 against the thrust bearing 28, the hub 4a of the impeller main body 4 and the return spring 23 moves and thus set the desired impeller blade outlet width b.
  • the actuator 25 may be formed by a stepper motor 30 and a spur gear 31, for example.
  • FIG. 2 shows a second variant according to the invention, wherein the adjusting device 22 has a thrust mechanism 32 with a push rod 33 and a push sleeve 34.
  • the push rod 33 is slidably mounted in the hollow drive shaft 7 via slide bearings 19 and sealed by at least one seal 19a.
  • the push rod 33 protrudes centrally through the bearing 35 of the actuator 25, wherein at the first end 33 a of the push rod 33, a stop 29, which may be secured against rotation, is fixedly connected to the push rod 33.
  • the push rod 33 can be moved via the actuator 25 in the direction of the pulley 7a.
  • the push sleeve 34 is fixedly connected to the push rod 33.
  • the push rod 33 In unregulated operation, for example in case of failure of the actuator 25, the push rod 33 is moved by the mounted in the impeller cover body 5 return spring 23, the hub 4a of the impeller main body 4 and the thrust bearing 28 in the suction side until the stop 29 on the bearing 35 of the actuator 25th is present, which fails to set the maximum impeller blade outlet width bmax.
  • the push rod 33 In controlled operation, the push rod 33, depending on the required function, is moved via the actuator 25 in the direction of the pulley 7a and thus deflected via the push sleeve 34, the thrust bearing 28 and the hub 4a of the impeller main body 4 against the spring formed as a compression spring 23 and thus the desired impeller outlet width b set.
  • the actuator 25 may be, for example, a pneumatic, hydraulic or electric lifting element.
  • FIG. 3 shows a third variant according to the invention, wherein the adjusting device 22 has an electromagnetic actuator 25.
  • the adjusting device 22 has at least one permanently connected to the impeller main body 4 permanent magnet 36 and a fixedly connected to the housing 2 electromagnet 37.
  • the permanent magnets 36 and corresponding electromagnets 37 can in the area of the outer labyrinth seal 21 be arranged.
  • the impeller main body 4 In uncontrolled operation, for example, in the event of failure of the actuator 25, the impeller main body 4 is moved by the return spring 23 and the hub 4a of the impeller main body 4 mounted in the impeller cover body 5, for example as a compression spring, toward the suction side 10 until the hub 4a of the impeller main body 4 is present at the arranged on the drive shaft 7 stop 29, wherein failsafe sets the maximum impeller vane outlet width bmax.
  • the impeller main body 4 In controlled operation, by appropriate energization of the electromagnet 37, depending on the required function, the impeller main body 4 is moved against the return spring 23 in the direction of the drive side 12 and thus set the desired impeller blade outlet width b.
  • the adjusting device 22 has a helical gear 24 with a threaded spindle 26 which can be rotated via an actuator 25 and a spindle nut 27.
  • the threaded spindle 26 is rotatably supported within the formed as a hollow shaft drive shaft 7 via slide bearings 19 and secured axially. Between the threaded spindle 26 and the drive shaft 7, a seal 19 a is arranged.
  • the spindle nut 27 is connected to the impeller main body 4, wherein the spindle nut 27 and the impeller main body 4 are non-slidably and rotatably connected with each other in the axial direction.
  • the threaded spindle 26 can be rotated via the actuator 25 clockwise or counterclockwise.
  • the spindle nut 27 is moved in unregulated operation, for example in case of failure of the actuator 25, of the bearing in the impeller cover body 5, designed as a compression spring return spring 23 in the end position shown in Fig. 4 with maximum impeller blade outlet width bmax.
  • the spindle nut 27, depending on the required function, via the actuator 25 and the threaded spindle 26 moves against the return spring 23 and thus set the desired impeller blade outlet width b.
  • the actuator 25 may be formed by a stepper motor 30 and a spur gear 31, for example.
  • FIGS. 6 and 7 show a fifth embodiment variant according to the invention, wherein the adjusting device 22 has a thrust mechanism 38 with a push rod 33 and a push sleeve 34.
  • the push rod 33 is slidably mounted in the hollow drive shaft 7 via slide bearings 19 and sealed by at least one seal 19a.
  • the push rod 33 is connected at a first end 33a via a linkage 38 with the actuator 25 and can be moved via this in the direction of the pulley 7a.
  • the push sleeve 34 is fixedly connected to the push rod 33.
  • the push rod 33 is moved, depending on the required function, via the actuator 25 in the direction of the pulley 7a and therewith with deflected over the thrust sleeve 34, the thrust bearing 28 and the hub 4a of the impeller main body 4 and thus set the desired impeller vane outlet width b.
  • the actuator 25 may be, for example, a pneumatic, hydraulic or electric lifting element.
  • Fig. 8 shows an impeller main body 4 of the impeller 3 of the centrifugal pump 1 shown in Figs. 6 and 7.
  • the impeller main body 4 includes a plurality of three-dimensionally curved impeller blades 6, in the embodiment each blade 6 having a first portion 6a and a substantially axial one having subsequent second section 6b.
  • the first section 6a is substantially two-dimensional, ie in a normal plane ⁇ on the axis 8 of the drive shaft 7 and push rod 33, curved and formed so that it can dip into the groove-shaped pockets 16 of the impeller cover body 5.
  • the impeller blades 6 are curved three-dimensionally. This second section 6b also remains outside the pockets 16 in the second end position shown in FIG.
  • an active and reliable control of the centrifugal pump 1 with very low drive power can be achieved over the entire speed and temperature range.

Landscapes

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

Abstract

L'invention concerne une pompe centrifuge (1), notamment une pompe à eau, se présentant sous la forme d'une pompe radiale ou d'une pompe semi-axiale comprenant un rotor (3) monté rotatif autour d'un axe (8) et raccordé à un arbre d'entraînement (7), ledit rotor (3) présentant un corps principal de rotor (4) pourvu d'une aube (6) et un corps de recouvrement de rotor (5), le corps principal de rotor (4) et le corps de recouvrement de rotor (5) pouvant coulisser axialement l'un par rapport à l'autre par l'intermédiaire d'un dispositif de réglage (22). L'objectif de l'invention est de permettre d'obtenir une régulation active et fiable de la pompe centrifuge (1) avec une faible puissance d'entraînement sur toute la plage de vitesses de rotation et de températures. À cet effet, le corps principal de rotor (4) est agencé de manière à pouvoir coulisser axialement sur l'arbre d'entraînement (7) ou sur le corps de recouvrement de rotor (5), le dispositif de réglage (22) étant en liaison fonctionnelle avec le corps principal de rotor (4).
EP16733866.4A 2015-05-13 2016-05-06 Pompe centrifuge à rotor coulissant Active EP3295034B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA50398/2015A AT517163B1 (de) 2015-05-13 2015-05-13 Kreiselpumpe
PCT/AT2016/050129 WO2016179619A1 (fr) 2015-05-13 2016-05-06 Pompe centrifuge à rotor coulissant

Publications (2)

Publication Number Publication Date
EP3295034A1 true EP3295034A1 (fr) 2018-03-21
EP3295034B1 EP3295034B1 (fr) 2021-01-20

Family

ID=56296437

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16733866.4A Active EP3295034B1 (fr) 2015-05-13 2016-05-06 Pompe centrifuge à rotor coulissant

Country Status (3)

Country Link
EP (1) EP3295034B1 (fr)
AT (1) AT517163B1 (fr)
WO (1) WO2016179619A1 (fr)

Families Citing this family (8)

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Publication number Priority date Publication date Assignee Title
CN106968964B (zh) * 2017-05-08 2023-01-24 浙江奇峰泵业有限公司 一种直线式弹簧磁强电泵
FR3071278B1 (fr) * 2017-09-18 2020-02-21 Sogefi Air & Cooling Dispositif de pompe a debit variable et circuit comprenant une telle pompe
CN108119395A (zh) * 2017-12-10 2018-06-05 安徽银龙泵阀股份有限公司 一种可变叶宽的离心泵用叶轮
CN108302061B (zh) * 2018-02-06 2019-12-13 宁波吉利罗佑发动机零部件有限公司 一种可变流量式水泵
CN111648965B (zh) * 2020-06-01 2021-09-24 安徽凯润泵阀科技有限公司 一种离心水泵
DE102021120618A1 (de) 2021-08-09 2023-02-23 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung eingetragener Verein Selbstadaptive Pumpe mit Formgedächtniselement
CN115263763B (zh) * 2022-07-11 2023-05-16 长沙昌佳智慧流体科技有限公司 一种矿用多级离心泵
CN118482039A (zh) * 2024-07-15 2024-08-13 宁波方太厨具有限公司 一种循环水泵和热水器

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Also Published As

Publication number Publication date
AT517163A1 (de) 2016-11-15
WO2016179619A1 (fr) 2016-11-17
AT517163B1 (de) 2019-08-15
EP3295034B1 (fr) 2021-01-20

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