EP0540736B1 - Gehäuse einer exzenterschneckenpumpe - Google Patents

Gehäuse einer exzenterschneckenpumpe Download PDF

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Publication number
EP0540736B1
EP0540736B1 EP92923581A EP92923581A EP0540736B1 EP 0540736 B1 EP0540736 B1 EP 0540736B1 EP 92923581 A EP92923581 A EP 92923581A EP 92923581 A EP92923581 A EP 92923581A EP 0540736 B1 EP0540736 B1 EP 0540736B1
Authority
EP
European Patent Office
Prior art keywords
stator
casing
jacket
lining
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.)
Expired - Lifetime
Application number
EP92923581A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0540736A1 (de
Inventor
Günther Hantschk
Jörg EITLER
Johann Kreidl
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
Priority claimed from DE4116697A external-priority patent/DE4116697C1/de
Application filed by Netzsch Pumpen and Systeme GmbH filed Critical Netzsch Pumpen and Systeme GmbH
Publication of EP0540736A1 publication Critical patent/EP0540736A1/de
Application granted granted Critical
Publication of EP0540736B1 publication Critical patent/EP0540736B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
    • F04C2/1075—Construction of the stationary member

Definitions

  • an adjustable stator for eccentric screw pumps is known, one or the like made of metal.
  • the stator jacket is provided with a plurality of beads which are distributed over its circumference and extend in the longitudinal direction of the stator and which have a radially inwardly projecting cross section with a predetermined breaking point.
  • the diameter of this known stator can be reduced by retensioning a clamp acting on it from the outside in order to compensate for wear on the stator lining.
  • the beads in the stator jacket facilitate re-tensioning from the beginning and should enable a stronger re-tensioning by breaking at their predetermined breaking points, whereby the stator jacket is divided into mutually independent jacket segments, so that no further deformation work on the beads has to be applied during further re-tensioning.
  • Stators of eccentric screw pumps are usually arranged between two housing parts which are connected to one another by flanges screwed together or by tie rods and each have a connecting piece which engages over one end of the stator shell.
  • Such arrangements are also known from DE 2331173 C3 and DE 2527141 C3 for adjustable stators.
  • DE 2 618 038 A1 discloses an eccentric screw pump with an adjustable stator, the casing of which can be compressed as a result of a slit running helically over the entire length of the casing.
  • the stator can thus be evenly radially compressed over its entire length by a clamping clamp surrounding it.
  • GB 2 021 199 A discloses a stator for an eccentric screw pump, which has a housing and a stator lining.
  • the stator lining and the housing engage in one another at a large number of points in a positive connection.
  • the connection between the housing and the lining is designed so that the stator lining exposed to wear can be replaced relatively easily.
  • Eccentric screw pumps are generally very good for pumping explosive emulsions. Nevertheless, operating errors or special circumstances can lead to pressure and temperature conditions occurring within such a pump, which can initiate an explosion.
  • Such an explosion begins with an ignition process that is triggered by the supply of energy.
  • the ignited explosive develops gases which cause an increase in pressure that further accelerates the burning rate.
  • Modern explosives containing water - slurries or emulsions - do not burn under normal atmospheric pressure (1 bar).
  • the minimum pressure for automatic combustion is between 5 and 20 bar.
  • a closed vessel filled with emulsion explosive which is ignited under pressure by a short glowing wire (point ignition)
  • point ignition does not detonates when the vessel is secured with a rupture disc.
  • a rupture disk will not be able to prevent detonation if the ignition takes place at many points at the same time, since the rupture disk cannot then reduce the pressure increase quickly enough due to its relatively small cross section.
  • Simultaneous ignition at many points can occur in an eccentric screw pump when it is working against a clogged or blocked outlet for a while.
  • the full drive energy is converted into thermal energy, which heats up the material in the pumping chambers between the rotor and stator. If the temperature rises sufficiently high, auto-ignition occurs at several points in the explosive.
  • the critical time frame for such heating typically ranges from five to twenty minutes.
  • the transition time from rapid combustion (deflagration) to detonation in the delivery chambers depends on the amount of fuel that ignites at the same time and can be between milliseconds and seconds.
  • the invention is therefore based on the object of providing an eccentric screw pump before reaching a critical pressure potential, which can lead to the explosion of a conveyed explosive, for a pressure relief that takes place faster than the possible additional pressure build-up given the drive power and design of the pump.
  • the known adjustable stators for eccentric screw pumps are neither provided nor suitable for solving this problem.
  • the devices arranged for readjustment around the stator casing for example Clamping clamps oppose any diameter expansion of the stator even if predetermined breaking points provided on the stator casing have already broken or the stator casing is divided into several separately adjustable shell-like sections from the outset.
  • the stator lining radially within the separating areas provided in the stator jacket for retensioning is too thick for it to burst in time under the influence of a dangerous internal overpressure.
  • DE 2718120 A1 discloses a piston pump for delivering low-stability, in particular explosive, fluids, in which a pump piston and a motor piston that can be driven with compressed air are arranged axially one behind the other and telescopically guided one inside the other in two cylinders arranged side by side.
  • a relative displacement between the pump piston and the engine piston is prevented by radial shear pins.
  • the shear pins between the affected pump piston and the associated engine piston are sheared off, so that the pump piston partially shifts into the engine piston, thereby increasing the volume of the cylinder space delimited by it and finally radial outlets in the Releases cylinders through which the medium can flow out.
  • the object is achieved in that at least one separating region of the stator casing and the region of the stator lining arranged radially within it and the connections of the connecting pieces are designed with the stator casing in such a way that the pump stator bursts in at least one separation area when a predetermined internal overpressure is exceeded.
  • the invention can be used with particular advantage in a housing for an eccentric screw pump in which the stator lining has a two-start internal thread surface with profile sections which are arcuate in cross-sectional profile and each include an apex.
  • at least one separation area of the stator casing extends along a vertex with a pitch that corresponds to the thread pitch of the internal thread surface of the stator lining.
  • the stator jacket is preferably divided into two essentially rigid jacket parts along two separation regions. This has the advantage that the bursting forces which arise when the pressure rises are concentrated in two separating areas, so that after the stator casing has burst, the stator lining in the separating areas is also rapidly loaded beyond its tensile strength limit and is thereby caused to burst.
  • the two jacket parts can be held together by transverse tensioning elements, each of which has a predetermined breaking point.
  • the stator is preferably connected to the two associated housing parts in that the stator casing has two annular ends, with which it surrounds the connecting piece of one of the two housing parts.
  • This deviation from the usual connection between the ends of the stator casing and the associated connecting piece has the advantage that the stator casing can burst open up to its two ends without being hindered by the connecting pieces by positive locking.
  • the two housing parts are held at a certain distance from one another by stud bolts and the ends of the stator sheath are guided in an axially floating manner on the connecting piece.
  • the separation areas in the stator casing and in the stator lining are preferably dimensioned such that the internal overpressure at which the pump stator bursts is 5 to 10 bar above the operating overpressure of the pump.
  • the stator jacket preferably consists of a material with an elongation at break of at most 1.0%.
  • materials are, for example, gray cast iron with a usual elongation at break of 0.3 to 0.8% and ceramic materials with a normal elongation at break of 0.1 to 0.2% and certain types of glass.
  • stator liner If the stator liner is to have a substantially constant thickness, the stator jacket itself must form an internally threaded surface. If such a stator sheath is circular cylindrical on the outside, then it is rather stiff in the areas between two helical outer grooves, so that considerable internal pressure is required in order to burst the stator along the helical grooves. In addition, axially parallel grooves of constant depth worked into the outside of such a stator casing can only insignificantly reduce the rigidity of the sections of the stator casing delimited by two helical grooves and therefore do not contribute too much to the desired explosion safety.
  • the separation areas of the stator jacket are according to the invention bounded radially inwards by an inner, axially parallel groove, the depth of which, measured from the stator axis, is at least approximately constant.
  • Such inner axially parallel grooves can be produced with conventional manufacturing methods, for example by broaching or butting, without particular difficulties with very small depth tolerances. Therefore, the thickness of the separating areas of the stator sheath that remain radially outside the axially parallel inner grooves can be precisely adapted to the requirements, provided that the outer surface of the stator sheath has low diameter and roundness tolerances.
  • stator casing has a particularly tough outer skin
  • stator casing has an outer, axially parallel groove, radially opposite the inner axially parallel grooves.
  • the inner grooves have a sharp-edged groove base profile. This results in notch stresses, which can cause the stator jacket to burst particularly quickly in the event of a critical internal overpressure.
  • outer and inner axially parallel grooves can be further developed in that the outer axially parallel grooves have a tapering profile to their groove base and the groove base profile of the inner axially parallel grooves is rectangular and symmetrical with respect to the associated outer groove.
  • the inner axially parallel grooves can be filled with the elastomer forming the stator lining. This improves the anchoring of the stator lining in the stator jacket.
  • the elastomer of the stator lining is not vulcanized onto the walls of the inner axially parallel grooves. This can easily be achieved by refraining from introducing the adhesion promoter required for vulcanizing the stator lining onto the stator jacket in the axially parallel inner grooves.
  • the eccentric screw pump partially shown in Fig. 1 is designed for an operating pressure (compared to the ambient pressure) of 20 bar. It has a pump stator 10 with a stator jacket 12 made of gray cast iron, which has predetermined breaking points designed as helical separating areas 14 and as axially parallel separating areas 16.
  • the radial thickness of the stator sheath is in the separation regions 14 and 16 12 is reduced by an externally worked-in, for example cast-in or milled groove in such a way that the stator jacket bursts into a plurality of jacket parts 18 at an internal overpressure of the order of 5 to 10 bar above the operating overpressure.
  • the stator jacket 12 has two annular ends 20 which also burst at such an internal excess pressure.
  • a rubber-elastic stator lining 22 is fastened, preferably vulcanized, in the stator jacket 12.
  • the stator lining 22 forms a two-start thread, the cross section of which is composed over the entire length of the stator lining from two arc-shaped profile sections 24, each with an apex 26 and two straight profile sections 28 lying between them.
  • the stator lining 22 has two flange-like end regions 30 which protrude into one of the annular ends 20 of the stator casing 12.
  • the pump stator 10 designed in this way is arranged between two rigid housing parts 32 and 34, each of which has a connecting piece 36.
  • the two connecting pieces 36 each engage in one of the annular ends 20 of the stator sheath 12, and are therefore enclosed by the latter.
  • an annular seal 38 is embedded, which seals against the inner lateral surface of the associated annular end 20 of the stator sheath 12.
  • the two housing parts 32 and 34 are connected to one another by a plurality of stud bolts 40 parallel to the axis A of the pump stator 10 and are held at such a distance from one another that the stator casing 12 has a small axial play, that is to say is not clamped between the housing parts 32 and 34.
  • the two connecting pieces 36 should, if at all, only lie loosely against one of the flange-like end regions 30 of the stator lining 22.
  • a radial pin 42 is fastened, which engages in an axially parallel slot 44 of the upper end 20 of the stator sheath 12 and thus prevents it from rotating.
  • the stator sheath 12 has a circular outer contour in cross section, which is particularly suitable for the production of the stator sheath by casting.
  • the stator jacket can also be cast with the oval cross section shown in FIG. 3.
  • Elliptical cross-sectional shapes that lie between the circular shape and the oval shape are also possible.
  • the helical separating regions 14 of the stator casing, which follow the apexes 26 of the stator liner 22, can also be formed by flats, as shown in FIG. 4 are.
  • the stator lining 22 has a constant thickness over its entire circumference and essentially also over its entire length, which is dimensioned so small that the stator lining in the regions radially within that in the stator jacket 12 formed separating areas 14 and possibly also 16 bursts when the stator sheath 12 bursts even in these separating areas due to internal excess pressure.
  • stator lining 22 is also weakened in its zones radially within the separating regions 14 by the fact that it has a reduced thickness in these zones.
  • 5 may have a constant course or may be formed in accordance with FIG. 6 in that the stator casing 12 projects radially inwards in the region of the apex 26.
  • a reduction in thickness with a continuous course can also be achieved, as is known per se from DE 3525529 C1, by virtue of the fact that the inner and outer contours of the stator lining 22 are geometrically similar, but rotated with respect to one another by a small angle of, for example, 5 ° to 15 °.
  • the separation areas 14 and, if present, also the separation areas 16, are areas in which the stator sheath 12 has a reduced thickness and is thereby weakened
  • the separation areas 14 can also, as in FIGS. 7 to 9 shown, be areas in which from the start separate halves of the stator sheath 12 lie against each other and are held together by tensioning devices.
  • the clamping devices are formed by clamping clips 46 with flanges 48 and associated clamping screws 50.
  • the tensioning screws 50 each have a predetermined breaking point 52.
  • the flanges 48 can, instead of being formed on tensioning clamps 46, also be formed directly on the two halves of the stator sheath 12, for example by casting.
  • the pump stator 10 shown in FIGS. 10 to 13 belongs to an eccentric screw pump which is designed for an operating pressure of, for example, 20 bar. If this pressure is exceeded, the pump stator 10 should burst.
  • the pump stator 10 has a stator jacket 12 which is circular-cylindrical on the outside so that it defines a stator axis A and which has the shape of a double-start spiral on the inside.
  • inner axially parallel grooves 15 are incorporated into the stator jacket 12, each with a central plane D containing the stator axis A and two each have parallel side walls and are referred to as inner axially parallel grooves. These grooves 15 are offset from one another by 90 ° and are thus arranged diametrically opposite one another in pairs.
  • the depth c of the inner axially parallel grooves 15 is dimensioned such that these grooves define separation regions 16 in which the stator sheath 12 bursts along at least one of these grooves at a critical internal overpressure and deforms along the other inner axially parallel grooves at least in such a way that the inner one Overpressure is suddenly reduced.
  • an outer, axially parallel groove 17 is additionally provided in each separation region 16.
  • the outer axially parallel grooves 17 have a triangular profile, the apex of which lies in the central plane D of the associated inner axially parallel groove 15.
  • stator sheath 12 disintegrates into four identical sheath parts 18 as soon as possible when the critical internal overpressure is exceeded, when the outer axially parallel grooves 17 are incorporated, their depth, like the depth c of the inner axially parallel grooves 15, is related to the stator axis A and not approximately the outer surface of the stator sheath. In this way it is ensured that each individual separation area 16 has a radial thickness which is constant with high accuracy over its entire length and which is equally large in all four separation areas 16 with likewise high accuracy.
  • the stator casing 12 can additionally have one or more outer annular grooves 19 so that the sheath parts 18 that separate from one another in the event of bursting are subdivided into smaller pieces that are thus harmless to the environment, or at least consume a certain additional energy as deformation work.
  • stator sheath 12 has two annular ends 20 which each enclose a connecting piece in the installed state in such a way that they can easily separate radially outwards from them in the event of bursting.
  • the connecting pieces belong to housing parts, not shown, between which the pump stator 10 is arranged. For details of this arrangement, reference is made to FIG. 1.
  • a rubber-elastic stator lining 22 is fastened, preferably vulcanized, in the stator jacket 12.
  • the stator lining 22 has a constant thickness in all cross sections through the pump stator 10, and thus, like the inner surface of the stator casing 12, forms a double-start internal thread, to which a single-start rotor, not shown, is assigned, as is customary in eccentric screw pumps.
  • the rubber or elastomer material from which the stator lining 22 is made has filled the inner axially parallel grooves 15 during vulcanization and thus forms ribs 23 of the same rectangular cross-section as these grooves.
  • the ribs 23 themselves should not adhere to the stator jacket 12 or only with negligibly little force.
  • the grooves 15, in contrast to the surface of the stator sheath 12 lying against the actual stator lining 22, have not been coated with an adhesion promoter before the rubber or elastomer material is introduced.
  • Separation areas 16 of the type described above can be provided in eccentric screw machines of any type, for example also in pumps or motors, the stator of which forms a three-thread or multi-thread internal thread surface.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP92923581A 1991-05-22 1992-05-21 Gehäuse einer exzenterschneckenpumpe Expired - Lifetime EP0540736B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4116697A DE4116697C1 (en) 1991-05-22 1991-05-22 Casing for eccentric worm pump with split stator jacket - has stator arranged to burst on excess of preset inner overpressure in split region
DE4116697 1991-05-22
DE4134853 1991-10-22
DE4134853A DE4134853C1 (xx) 1991-05-22 1991-10-22
PCT/EP1992/001139 WO1992020923A1 (de) 1991-05-22 1992-05-21 Gehäuse einer exzenterschneckenpumpe

Publications (2)

Publication Number Publication Date
EP0540736A1 EP0540736A1 (de) 1993-05-12
EP0540736B1 true EP0540736B1 (de) 1995-08-09

Family

ID=25903807

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92923581A Expired - Lifetime EP0540736B1 (de) 1991-05-22 1992-05-21 Gehäuse einer exzenterschneckenpumpe

Country Status (6)

Country Link
US (1) US5318416A (xx)
EP (1) EP0540736B1 (xx)
JP (1) JPH06500615A (xx)
AU (1) AU643621B2 (xx)
DE (2) DE4134853C1 (xx)
WO (1) WO1992020923A1 (xx)

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JP5889553B2 (ja) * 2011-06-28 2016-03-22 古河産機システムズ株式会社 一軸偏心ねじポンプ
US8888474B2 (en) 2011-09-08 2014-11-18 Baker Hughes Incorporated Downhole motors and pumps with asymmetric lobes
FR2991402B1 (fr) * 2012-05-29 2014-08-15 Christian Bratu Pompe a cavites progressives
US8967985B2 (en) * 2012-11-13 2015-03-03 Roper Pump Company Metal disk stacked stator with circular rigid support rings
DE102013003833A1 (de) 2013-03-07 2014-09-11 Wilo Se Pumpe mit Überdruckschutz
US9610611B2 (en) 2014-02-12 2017-04-04 Baker Hughes Incorporated Method of lining an inner surface of a tubular and system for doing same
US11148327B2 (en) 2018-03-29 2021-10-19 Baker Hughes, A Ge Company, Llc Method for forming a mud motor stator
JP7138383B1 (ja) * 2022-01-18 2022-09-16 兵神装備株式会社 一軸偏心ねじポンプ
JP7138382B1 (ja) * 2022-01-18 2022-09-16 兵神装備株式会社 一軸偏心ねじポンプ
JP7199128B1 (ja) * 2022-01-18 2023-01-05 兵神装備株式会社 一軸偏心ねじポンプ
DE202022104701U1 (de) * 2022-08-19 2023-11-22 Vogelsang Gmbh & Co. Kg Verdrängerkörper und Pumpengehäuse für eine Verdrängerpumpe

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DE3641855A1 (de) * 1986-12-08 1988-06-16 Allweiler Ag Werk Bottrop Verstellbarer stator fuer exzenterschneckenpumpen
HU204116B (en) * 1989-01-23 1991-11-28 Hidromechanika Szivattyu Es An Arrangement for the standing part of eccentric worm pump
DE4116697C1 (en) * 1991-05-22 1992-03-12 Netzsch-Mohnopumpen Gmbh, 8264 Waldkraiburg, De Casing for eccentric worm pump with split stator jacket - has stator arranged to burst on excess of preset inner overpressure in split region

Also Published As

Publication number Publication date
DE4134853C1 (xx) 1992-11-12
WO1992020923A1 (de) 1992-11-26
US5318416A (en) 1994-06-07
JPH06500615A (ja) 1994-01-20
EP0540736A1 (de) 1993-05-12
AU1878692A (en) 1992-12-30
AU643621B2 (en) 1993-11-18
DE59203216D1 (de) 1995-09-14

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