EP2961987A1 - Pompe a vis - Google Patents

Pompe a vis

Info

Publication number
EP2961987A1
EP2961987A1 EP14718901.3A EP14718901A EP2961987A1 EP 2961987 A1 EP2961987 A1 EP 2961987A1 EP 14718901 A EP14718901 A EP 14718901A EP 2961987 A1 EP2961987 A1 EP 2961987A1
Authority
EP
European Patent Office
Prior art keywords
outlet channel
longitudinal axis
screw pump
pump housing
medium
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Withdrawn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
EP14718901.3A
Other languages
German (de)
English (en)
Inventor
Eduardo Nuss
Arthur Zinke
Aluisio Loth
Klaus Heizinger
Lorenz Lessmann
Sérgio Krahn
Rui Keunecke
Silvio Beneduzzi
Egon Weege
Nilton André Theilacker
Sidney Guedes
Petra Lutke
Robert Kurz
Josef Strassl
Johann Kreidl
Hisham Kamal
Horst ENGL
George Balcerczyk
Mathias Gradl
Gunther Herr
André Nijmeh
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.)
Netzsch Pumpen and Systeme GmbH
Original Assignee
Netzsch Pumpen and Systeme 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 Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Publication of EP2961987A1 publication Critical patent/EP2961987A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F04C2/165—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type having more than two rotary pistons with parallel axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2250/00—Geometry
    • F04C2250/20—Geometry of the rotor
    • F04C2250/201—Geometry of the rotor conical shape

Definitions

  • the present invention relates to a screw pump according to the features of the preamble of claim 1. Furthermore, the invention relates to a method for operating a screw pump according to the features of the preamble of claim 12.
  • the screw pump is a so-called positive displacement pump in which the shape of the rotating displacer is similar to a spindle screw.
  • Screw pump consists of two or more counter-rotating rotors and a pump housing, which encloses the rotors.
  • the rotors are formed with a regular, thread-shaped profiling and engage gear-like in one another.
  • the rotors are also referred to as screw spindles and have at least a first shaft portion and a profile portion with a helical or coiled profile.
  • Construction elements pump housing, first screw and at least second screw are formed, form the delivery chambers for the pumped medium.
  • This type of pump is particularly suitable for incompressible, also viscous media and for generating high pressures.
  • Screw pumps are used both for transporting single-phase and multi-phase liquids.
  • the three-spindle screw pump is mainly used for pumping lubricating fluids that are free of abrasives. It is characterized in particular by the fact that it is possible to produce high pressures of up to 160 bar.
  • the three spindles are usually arranged so that a central drive spindle (also referred to as a main rotor) drives two laterally engaging follower spindles.
  • the drive spindle in turn is connected to a drive motor, which can be designed both as an electric motor and as an internal combustion engine.
  • the torque generated by the drive is transmitted from the drive spindle via the spindle profile on the driven spindles.
  • the interlocking spindle profiles produce closed
  • Delivery chambers in which the fluid is enclosed and transported in the axial direction from the suction to the pressure side.
  • the housing is that part of the pump in which all three spindles are embedded.
  • the delivery chambers on the housing are that part of the pump in which all three spindles are embedded.
  • the object of the invention is to optimize the flow of the transported medium in the pump, in particular in the region of the outlet channel.
  • the formation of vortices, which disturb the transport and lead to flow losses, should be reduced in this area.
  • Claims 1 and 12 include. Further advantageous embodiments are described by the subclaims.
  • the invention relates to a screw pump for conveying fluid media, in particular incompressible or tough media.
  • a screw pump for conveying fluid media, in particular incompressible or tough media.
  • a at least one inlet channel and at least one outlet channel having pump housing are a first drive spindle and at least a second
  • the at least one inlet channel is formed, for example, as a first bore with a first longitudinal axis.
  • the at least one outlet channel is formed, for example, as a second bore with a second longitudinal axis.
  • the drive spindle comprises a third longitudinal axis and consists of a shank portion which at least in some areas rotates about a bearing in the Pump housing is mounted and a profile section which is spindle-shaped or helical.
  • the free outer end of the drive spindle is assigned a drive.
  • at least one second driven spindle is arranged in the pump housing. Preferably, it is a three-spindle
  • Screw pump with one drive spindle and two driven
  • the at least two spindles each comprise a profile section with a spindle-shaped or coiled profile, wherein the profile sections of the at least two spindles are at least partially engaged with each other.
  • the so-called conveying path for the fluid medium is thereby formed.
  • the pump housing and the intermeshing profile sections of the spindles form the delivery chambers, in which the medium between the inlet channel and the outlet channel is transported in the conveying direction parallel to the longitudinal axes of the spindles.
  • the second longitudinal axis of the outlet channel is arranged at an obtuse angle, that is to say at an angle of more than 90 ° to the conveying path. That is, the conveying path and the second longitudinal axis of the outlet channel include an angle which is greater than 90 °. Due to the selected arrangement of inlet channel and outlet channel with respect to the conveying path in the pump housing, the fluid medium flows in a first flow direction through the inlet channel in the
  • Pump housing wherein the first longitudinal axis of the inlet channel is arranged substantially orthogonal to the conveying path.
  • the fluid medium is deflected in a region downstream of the inlet channel and transported in the conveying direction along the conveying path within the delivery chambers. Subsequently, the medium is deflected again and leaves the pump housing in a second flow direction through the outlet channel.
  • Conveyor and outlet channel is greater than 90 °.
  • the opposite angle between an imaginary extension of the conveyor line over the outlet channel and the outlet channel is pointed.
  • the fluid is deflected from the imaginary extension in the acute angle in the outlet channel. That is, the conveying medium is deflected from the conveying direction into the outlet channel by an angle which is smaller than 90 °. Due to the oblique arrangement of the outlet channel with respect to the
  • the drive spindle is formed at least in sections as a cone.
  • the drive spindle is formed at least in sections as a concave rounded cone.
  • the area which is arranged in the mounted pump in the region of the outlet channel is formed at least in sections as a concave rounded cone.
  • the drive spindle comprises a profile section and a shaft section, which is supported in regions in a bearing of the pump housing.
  • the cone-shaped section is a partial section of the shaft section and adjoins directly to the profile section.
  • the cross section of the cone-shaped section, in particular the cross section of the concave, rounded conical section is preferably reduced or tapered in the direction of the profile section.
  • the conveyed medium is advantageously conducted via the preferably concave rounded cone-shaped portion of the drive spindle in the predetermined by the arrangement of the outlet channel second flow direction.
  • the second flow direction includes with the conveyor line an angle not equal to 90 °, in particular an obtuse angle, that is an angle which is greater than 90 °.
  • it is a three-spindle screw pump with a first drive spindle and two Mauläufindeleln, wherein the longitudinal axes of the three spindles are arranged in parallel and in a plane.
  • the longitudinal axes of the three spindles are arranged in parallel and in a plane.
  • the invention further relates to a method for operating a
  • a screw pump for conveying a fluid medium wherein the fluid medium is introduced through at least one inlet channel in a first flow direction in the pump housing.
  • the first flow direction is largely orthogonal to the conveying direction of the medium in the pump housing.
  • the medium is deflected in an area downstream of the at least one inlet channel region in about 90 ° and in Transport direction along the longitudinal axes of the spindles transported through the pump housing.
  • the medium is deflected from its conveying direction into an outflow direction into the outlet channel.
  • the resulting due to the arrangement of the outlet channel deflection angle is less than 90 °, that is, the medium is deflected by less than 90 ° from the conveying direction.
  • the medium leaves the pump housing via the at least one outlet channel in the second flow direction.
  • the medium is thus less deflected in the region upstream of the at least one outlet channel than in the conventionally known pumps.
  • the vortex formation in the region of the at least one outlet channel is reduced or completely prevented.
  • the advantageous deflection of the fluid medium takes place within a previously described
  • the solution according to the invention is based in particular on a change in the shape and position of the outlet channel in the pump housing and a change in the shape of the spindle shaft of the drive spindle in the region of the outlet channel.
  • Screw pump is achieved.
  • the change on the pump housing in particular provides an oblique position of the outlet channel both in the axial direction and in the radial direction to the drive spindle.
  • the drive spindle further comprises a tapering at least partially concave in the direction of the profile section cone, which deflects the flow of the pumped medium laterally into the oblique outlet channel. Due to the obliquely employed outlet channel on the pump housing and the flow-guiding, preferably concave rounded cone on the drive rotor, the flow resistance is advantageously reduced, in particular for highly viscous fluids, which in turn has a positive effect on the efficiency of the pump. The positive effect achieved by the optimized flow guidance on the outlet channel of the screw pump is detectable by means of computer-aided dynamic fluid simulation.
  • Screw pump compared to the prior art can be significantly increased. figure description
  • FIGS 1 show a screw pump according to the invention.
  • FIGS. 2 show a drive spindle with a modification according to the invention.
  • FIGS. 3 each show a cross section through the outlet region of a screw pump.
  • Figures 4 show schematically the arrangements of different longitudinal axes in the pump housing.
  • FIG. 5 shows a further illustration of a partial region of a
  • FIGS 1A and 1B show a screw pump 1 according to the invention with pump housing 2.
  • a drive spindle 5 a first secondary rotor spindle 6 and a second secondary rotor spindle 6 * (hardly visible, see Figure 5) are arranged.
  • the second secondary rotor spindle 6 * is at an angle of 180 ° to the first secondary rotor spindle 6, starting from the axis of rotation D of the drive spindle 5
  • Pump housing 2 arranged, that is, the longitudinal axes or axes of rotation of the three spindles 5, 6, 6 * lie in a plane.
  • the pumped medium flows in
  • the drive spindle 5 is hydraulically mounted in the pump housing 2 over the entire length of the turns, that is, in its entire profile section P (see FIG. 2).
  • the pump housing 2 comprises a receiving housing 22 for a
  • Shaft section A partially exits through an opening 15 from the pump housing 2.
  • sealing elements 21 are arranged as shaft seal 20 on the drive spindle to the pump housing 2 in the region of
  • Seal shaft outlet opening 15 In a shaft section A adjacent to the profile section P, the drive spindle 5 is again mechanically mounted in a zone of low pressure by means of ball bearings 26.
  • the shaft seal 20 is done in particular by means of sealing elements 21, which rotate the drive spindle 5 relative to the
  • Pump housing 2 allow, for example, mechanical seals, shaft seals or stuffing box packings.
  • Another sealing system is assigned to a shaft section AD of the shaft shaft of the drive spindle 5 with an enlarged diameter (cf., FIG. 2) as a labyrinth seal 28. This is able to reduce the pressure from the high pressure side to the low pressure side. The thereby adjusting
  • Slit flow prevents the drive spindle 5 in the pump housing 2 and simultaneously lubricates the ball bearing 26.
  • the widened portion AD of the shaft shaft of the drive spindle 5 designed as a hydraulically acting compensation piston 28 reduces the axial bearing forces by acting on the screw profile
  • the continuous leakage flow exiting to the low pressure side is responsible for the heat exchange and the lubrication of the sealing elements 21 of the shaft seal 20, for example the mechanical seals.
  • the leakage flow is discharged via a channel to the suction side and thus prevents a gradual increase in pressure in the seal chamber.
  • the cavities which are formed by the pump housing 2, the drive spindle 5 and the secondary rotor spindles 6, 6 *, form the delivery chambers for the conveyed medium.
  • the conveyed medium flows through the inlet channel 7 largely orthogonal to the longitudinal axis of the spindles 5, 6, 6 * in the pump housing 2 and is in
  • Inlet area 8 is deflected. Subsequently, the pumped medium on the
  • the conveying direction FR is largely parallel to the longitudinal axis L3 of the drive spindle 5. Subsequently, the conveyed medium is deflected again and leaves the pump housing 2 by flowing out through the outlet channel 9.
  • the track which is the medium within the
  • Pump housing covers is also referred to as a conveyor line FS.
  • the longitudinal axis L2 of the outlet channel 9 in the pump housing 2 at an angle not equal to 90 ° to the longitudinal axis L3 of the drive spindle 5 is arranged.
  • the outlet channel 9 is formed obliquely such that an obtuse angle is formed between the profile section P of the drive spindle 5 and the longitudinal axis L2 of the outlet channel 9.
  • the medium leaves the pump housing 2 through the outlet channel 9 in a second flow direction SR2.
  • This second flow direction SR2 or the second longitudinal axis L2 of the outlet channel 9 forms an obtuse angle with the conveying path FS.
  • the longitudinal axis L1 of the inlet channel 7 is preferably arranged orthogonal to the longitudinal axis L3 of the drive spindle 5, it follows that the first longitudinal axis L1 of the inlet channel 7 and the second longitudinal axis L2 of the
  • Outlet channels 9 are arranged in a common plane at an angle to each other.
  • first longitudinal axis L1 of the inlet channel 7 and the third longitudinal axis L3 of the drive spindle 5 define a first plane and that the second longitudinal axis L2 of the outlet channel 9 is not arranged in this plane.
  • the second longitudinal axis L2 of the outlet channel 9 is arranged in a different plane and at an angle to the first longitudinal axis L1 of the inlet channel.
  • FIGS. 2A and 2B show a drive spindle 5 with a modification according to the invention. This consists of a profile section P with a trained
  • the drive spindle 5 has a shank portion S.
  • This comprises a shaft section A with storage section AL.
  • the bearing portion AL in the ball bearing 26 of the housing formed as a shaft outlet opening 15 22 and part of
  • a cone-shaped section K is arranged between the axis section A and the profile section P.
  • This is located in the mounted screw pump 1 within the pump housing 2 in the region of the outlet channel 9.
  • the diameter of the cone-shaped portion K tapers counter to the conveying direction FR of the medium within the pump housing 2.
  • the cone-shaped portion K is formed as a concave rounded cone .
  • the additional cone-shaped portion K on the drive spindle 5 generates a twist of the pumped medium and leads to a better introduction of the pumped medium on the stator or in the outlet channel 9 (see Figures 1A and 1B).
  • the concave rounded cone-shaped portion K continues to perform the additional function of an axial displacement of the secondary rotor spindles 6, 6 *
  • FIG. 2B shows a detail area of the drive spindle 5.
  • the cone-shaped section K tapers concavely (see reference numeral kV) at least in sections in the direction of the profile section P. This effects the advantageous deflection of the flow of the conveyed medium laterally into the oblique outlet channel 9 (see FIG Figures 1 and 3).
  • FIGS. 3A and 3B each show a cross section through the outlet region of a screw pump 1, 1A.
  • FIGS. 4A and 4B schematically show the arrangements from the first longitudinal axis L1 of the inlet channel 7, the second one
  • FIGS. 3A and 4A show the state of the art of a screw pump 1A, in which the outlet channel 9A is arranged orthogonal to the longitudinal axis L3 of the drive spindle 5 (see FIG. 1) and thus a deflection of the conveyed medium from the conveying direction FR into the second
  • Flow direction SR2A (see Figures 1A and 1B) caused by about 90 °.
  • first inflow SR1A and the second outflow direction SR1A are aligned in anti-parallel to each other.
  • longitudinal axis L1 of the inlet duct 7 and the third longitudinal axis L3 of the drive spindle 5 form a plane.
  • the second longitudinal axis L2A of the outlet channel 9A is also in this plane, i. the first longitudinal axis L1 of the inlet channel 7 and the second
  • Longitudinal axis L2A of the outlet channel 9A are arranged parallel to each other.
  • the first longitudinal axis L1 of the inlet channel 7 and the second longitudinal axis L2A of the outlet channel 9A in the prior art may each be arranged orthogonal to the third longitudinal axis L3 of the drive spindle 5, but not parallel to one another. This means that the two longitudinal axes L1, L2 are skewed to each other and in particular do not intersect.
  • the conveyed medium from the conveying direction FR in the second flow direction SR2A (see Figures 1A and 1B) is deflected by approximately 90 °.
  • the computer-assisted dynamic fluid simulation shows a strong vortex formation of the medium flowing out through the outlet channel 9A in the flow direction SR2A.
  • the outlet channel 9 is arranged at an obtuse angle ⁇ to the conveying path FS within the pump housing 2 parallel to the longitudinal axis L3 of the drive spindle 5.
  • the conveyed medium in the region of the outlet channel 9 is deflected only by an angle ⁇ in the second flow direction SR2, where ß is smaller than 90 °.
  • the longitudinal axes L1 of the inlet channel 7 and the longitudinal axis L3 of the drive spindle 5 are thus always arranged at an angle not equal to 90 ° to each other, wherein the intersection of the longitudinal axes L1 and L3 is usually outside of the pump housing.
  • the computer-assisted dynamic fluid simulation shows a greatly reduced vortex formation of the medium flowing out through the outlet channel 9 in the flow direction SR2.
  • FIG. 5 shows a further illustration of a partial region of a
  • FIG. 5 shows the spindles 5, 6, 6 * comprehensive portion of the pump housing 2 with the outlet channel 9 comprehensive outlet region.
  • the portion of the pump housing 2 which surrounds the inlet region 8 and the inlet channel 7 has not been shown for better illustration of the arrangement of the drive spindle 5 and the driven secondary rotor spindles 6, 6 * .
  • a conveying chamber for the transport of the fluid medium is characterized by the intermeshing profile areas of the spindles 5, 6, 6 * is formed.

Landscapes

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

Abstract

La présente invention concerne une pompe à vis (1) destinée au refoulement de substances fluides, comprenant un boîtier de pompe (2) qui présente un canal d'entrée (7) doté d'un premier axe longitudinal (L1) et un canal de sortie (9) doté d'un deuxième axe longitudinal (L2). Le boîtier de pompe (2) comprend au moins par zones une première vis d'entraînement (5) ayant un troisième axe longitudinal (L3) et au moins une deuxième vis entraînée (6, 6*). Les vis (5, 6, 6*) comprennent entre le canal d'entrée (7) et le canal de sortie (9) respectivement une section profilée (P), les sections profilées (P) des au moins deux vis (5, 6, 6*) venant au moins partiellement en prise mutuelle et formant avec le boîtier de pompe (2), entre le canal d'entrée (7) et le canal de sortie (9), une trajectoire de refoulement (FS) parallèle à l'axe longitudinal (L3) de la vis d'entraînement (5), comportant des compartiments de refoulement (F) destinés à la substance fluide. Selon l'invention, le deuxième axe longitudinal (L2) du canal de sortie (9) forme un angle obtus (α) avec la trajectoire de refoulement (FS) dans le boîtier de pompe (2). L'invention concerne aussi un procédé pour faire fonctionner une pompe à vis (1).
EP14718901.3A 2013-03-01 2014-02-25 Pompe a vis Withdrawn EP2961987A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013102030.5A DE102013102030B3 (de) 2013-03-01 2013-03-01 Schraubenspindelpumpe
PCT/DE2014/000087 WO2014131392A1 (fr) 2013-03-01 2014-02-25 Pompe a vis

Publications (1)

Publication Number Publication Date
EP2961987A1 true EP2961987A1 (fr) 2016-01-06

Family

ID=50543408

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14718901.3A Withdrawn EP2961987A1 (fr) 2013-03-01 2014-02-25 Pompe a vis

Country Status (10)

Country Link
US (1) US9869314B2 (fr)
EP (1) EP2961987A1 (fr)
JP (1) JP6069530B2 (fr)
KR (1) KR101775806B1 (fr)
CN (1) CN105121854A (fr)
AR (1) AR094937A1 (fr)
BR (1) BR112015020468A2 (fr)
DE (1) DE102013102030B3 (fr)
RU (1) RU2015141530A (fr)
WO (1) WO2014131392A1 (fr)

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US9850906B2 (en) 2011-03-28 2017-12-26 Tc1 Llc Rotation drive device and centrifugal pump apparatus employing same
US10052420B2 (en) 2013-04-30 2018-08-21 Tc1 Llc Heart beat identification and pump speed synchronization
US10117983B2 (en) 2015-11-16 2018-11-06 Tc1 Llc Pressure/flow characteristic modification of a centrifugal pump in a ventricular assist device
US10166318B2 (en) 2015-02-12 2019-01-01 Tc1 Llc System and method for controlling the position of a levitated rotor
US10245361B2 (en) 2015-02-13 2019-04-02 Tc1 Llc Impeller suspension mechanism for heart pump
US10371152B2 (en) 2015-02-12 2019-08-06 Tc1 Llc Alternating pump gaps
US10506935B2 (en) 2015-02-11 2019-12-17 Tc1 Llc Heart beat identification and pump speed synchronization

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CN106194719A (zh) * 2016-08-26 2016-12-07 黄山艾肯机械制造有限公司 一种低粘度高压力的螺杆泵
CN106122000A (zh) * 2016-08-26 2016-11-16 黄山艾肯机械制造有限公司 一种液压平衡的螺杆泵组件
DE102018130472A1 (de) * 2018-11-30 2020-06-04 Nidec Gpm Gmbh Schraubenspindelpumpe
DE102019118086A1 (de) * 2019-07-04 2021-01-07 Nidec Gpm Gmbh Integrierte Schraubenspindel-Kühlmittelpumpe
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DE102013102030B3 (de) 2014-07-03
CN105121854A (zh) 2015-12-02
JP2016508574A (ja) 2016-03-22
US9869314B2 (en) 2018-01-16
BR112015020468A2 (pt) 2017-08-22
AR094937A1 (es) 2015-09-09
JP6069530B2 (ja) 2017-02-01
RU2015141530A (ru) 2017-04-06
KR20150121220A (ko) 2015-10-28
KR101775806B1 (ko) 2017-09-06
US20150369241A1 (en) 2015-12-24
WO2014131392A1 (fr) 2014-09-04

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