EP3767105A1 - Stator pour une pompe à vis sans fin excentrique - Google Patents

Stator pour une pompe à vis sans fin excentrique Download PDF

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Publication number
EP3767105A1
EP3767105A1 EP19186418.0A EP19186418A EP3767105A1 EP 3767105 A1 EP3767105 A1 EP 3767105A1 EP 19186418 A EP19186418 A EP 19186418A EP 3767105 A1 EP3767105 A1 EP 3767105A1
Authority
EP
European Patent Office
Prior art keywords
lining
stator
wall thickness
axial direction
zone
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
EP19186418.0A
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German (de)
English (en)
Other versions
EP3767105B1 (fr
Inventor
Thomas PETERHANSEL
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.)
Arnold Jaeger Holding GmbH
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Arnold Jaeger Holding 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 Arnold Jaeger Holding GmbH filed Critical Arnold Jaeger Holding GmbH
Priority to EP19186418.0A priority Critical patent/EP3767105B1/fr
Priority to PL19186418T priority patent/PL3767105T3/pl
Priority to ES19186418T priority patent/ES2909699T3/es
Priority to CN202080059862.5A priority patent/CN114341496B/zh
Priority to PCT/EP2020/070106 priority patent/WO2021009275A1/fr
Priority to UAA202200674A priority patent/UA130058C2/uk
Publication of EP3767105A1 publication Critical patent/EP3767105A1/fr
Application granted granted Critical
Publication of EP3767105B1 publication Critical patent/EP3767105B1/fr
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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
    • 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
    • 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
    • F04C2250/30—Geometry of the stator

Definitions

  • the invention relates to a stator for an eccentric screw pump having a rotor.
  • Stators of the generic type have a continuous and coiled pump cavity formed by a lining made of an elastomer, in which an eccentrically mounted rotor rotates. Due to the eccentric mounting of the rotor, chambers are formed between it and the coiled lining as it rotates, which in a sense migrate from a suction side of the eccentric screw pump to its pressure side, so that a medium is pushed or conveyed in the axial direction through the pump or the stator .
  • Stators of this type can be used in eccentric screw pumps in particular for conveying media such as plaster, mortar, oil, etc.
  • stators of this type according to, for example DE 195 31 318 A1 , EP 1 522 729 B2 or DE 41 11 166 C2 provided to taper the lining conically starting from the suction side towards the pressure side.
  • the elastic resilience of the lining is adapted to the continuously increasing conveying pressure in the axial direction or conveying direction.
  • Due to the conical shape of the stator an adapted transition piece must also be used for the connection to the next component in the eccentric screw pump, if the wall thickness of the jacket remains the same over the entire stator and this also adapts to the conical taper.
  • the forces acting on the lining are increased by the medium. If the medium has, for example, coarse material components, for example rocks, then these stress the lining more strongly in an elastically less flexible and already tapered area, so that the lining wears faster overall.
  • the object of the invention is therefore to provide a stator with increased delivery capacity, which is easy to manufacture, has a high level of durability and can be easily integrated into an eccentric screw pump.
  • an average wall thickness of the lining of the stator starting from an end wall thickness, which is present in the area of a preferably cylindrical suction side of the stator, continuously, ie according to a continuous function of any degree, in the axial direction down to a lowest average Wall thickness is reduced, and that the mean wall thickness increases again at least in regions after reaching the lowest mean wall thickness, so that a preferably cylindrical widening is formed in the lining up to a pressure side of the stator.
  • a suitable transition can be created on the pressure side.
  • the expansion allowed advantageously also a connection, for example via a conventional flange, to the next component of the eccentric screw pump.
  • the wall thickness can also be adjusted as it prevails on the suction side, so that advantageously the same connections, e.g. flanges, can be used for both sides of the stator if the end wall thicknesses on the pressure side and on the suction side roughly match.
  • the lining becomes more flexible again towards the pressure side, as a result of which the conveyed medium, which is normally under high pressure on the pressure side, can stabilize.
  • the pressure increases only slightly in the expansion of the pressure side when the lining becomes more flexible again.
  • the pumped medium experiences an increased pressure increase in the area of the increasingly harder lining due to the continuous reduction in the mean wall thickness in an area before the expansion, which is also desired for the pumping action in this area. In the area of the expansion, however, there is no longer any increased pressure increase and the medium is thus stabilized.
  • an optimized transfer of the conveyed medium into the next component of the eccentric screw pump can therefore take place overall.
  • the structure of the stator can also achieve an improved retention function if, for example, the eccentric screw pump is switched off.
  • the pumped medium can flow back in the pump cavity if a pressure difference between adjacent chambers in the pump cavity becomes too high. If a harder lining is chosen, the backflow only occurs at higher pressure differences between the chambers.
  • the lining which becomes harder in the axial direction, prevents the conveyed medium from increasing as the pressure increases at the same time there is also a backflow, ie higher pressure differences are possible before the conveyed medium flows back.
  • the stator is therefore divided into different axially spaced zones through the targeted course of the mean wall thickness, the transition preferably being defined by the mean wall thickness of the lining remaining constant at least in the premixing zone and / or in the stabilization zone.
  • the conveyed medium when it enters the stator and / or when it exits the stator, can advantageously be adapted to the changed, tapering shape of the lining in the high pressure zone or the resulting changed delivery rate of the stator.
  • the mean wall thickness can also be constant in parts of the high pressure zone.
  • the mean wall thickness of the lining in a first high pressure area of the high pressure zone decreases continuously in the axial direction down to the lowest mean wall thickness, the first high pressure area adjoining the premixing zone, and approximately constant in a second high pressure area of the high pressure zone the smallest mean wall thickness remains.
  • the medium therefore advantageously has a zone available in which it can be homogenized or comminuted on the suction side and / or stabilized on the pressure side.
  • the respective zone can be set in a targeted manner by selecting a corresponding axial extent or an axial width as well as the wall thickness of the lining in the respective zone.
  • the medium can then be "prepared" in the respective zone for the next area in the stator or in the eccentric screw pump.
  • the lining in the high-pressure zone is less stressed when the flexibility decreases, since the medium has already been comminuted or homogenized in the premixing zone.
  • the lining in the high pressure zone therefore wears less.
  • the medium is stabilized in the stabilization zone so that a smoother transition or a smoother exit from the stator can be achieved.
  • the mean wall thickness of the lining for this purpose starting from the end mean wall thickness in the axial direction at least in some areas, for example in the high pressure zone or in parts of the high pressure zone, decreases linearly in the direction of the pressure side or also following a non-linear function.
  • the lining of the stator tapers in at least some areas in the axial direction, in that a contour of the outer surface of the lining, starting from the end average wall thickness to the lowest average wall thickness, increasingly follows a contour of the inner surface of the lining, which is designed as a double helical thread approximates.
  • the tapering and thus the adaptation of the average wall thickness to the pressure acting in the pump cavity is further increased, the tapering then also being visible from the outside, since the jacket preferably also adapts to this two-thread shape of the outer surface.
  • this type of tapering can be provided in the first high pressure area of the high pressure zone, so that a transition between the preferably cylindrical premixing zone and the second high pressure area of the high pressure zone can be established, with the jacket in the second high pressure area being adapted to the double shape of the outer surface.
  • a type of hybrid stator is formed from a cylindrical premixing zone and a coiled high pressure zone in the second high pressure area.
  • the first high pressure area then acts as a transition with a lining that becomes correspondingly harder due to the continuous adaptation of the mean wall thickness.
  • the mean wall thickness of the lining increases abruptly or continuously after reaching the lowest mean wall thickness and possibly after remaining constant at the lowest mean wall thickness (see second high pressure area) in order to develop the pressure-side expansion.
  • a continuous increase enables a smoother transition between the high pressure zone and the stabilization zone as well as easier production. Nevertheless, an abrupt transition can also be provided in order, for example, to promote stabilization and to keep a further increase in pressure of the conveyed medium within limits.
  • an inside diameter of the jacket corresponds to an outside diameter of the lining, so that the jacket lies flat over the entire stator on the outside surface of the lining and thus assumes the conical or the coiled course corresponding to the outside surface, with the jacket preferably being a Has constant material thickness.
  • the jacket consists of a harder material than the lining, preferably steel.
  • a stator 1 which has a tubular jacket 2, which is preferably made from a steel tube, for example by forming.
  • the jacket 2 encloses an elastically resilient lining 3, the inner surface 4 of which has a coiled or helical contour K4, with a double helical thread being formed.
  • a pump cavity 5 is thereby formed in the interior of the stator 1, into which a rotor 6 ( Figure 1a ) is inserted, the rotor 6 being designed in the manner of a single-start coarse thread and possibly resting against the elastically flexible lining 3 under prestress.
  • the eccentrically mounted rotor can rotate in the pump cavity 5.
  • the stator 1 has a suction side 7 and a pressure side 8, whereby when the stator 1 is installed together with the rotor 6 in an eccentric screw pump (not shown), the medium to be conveyed, for example mud, mortar or plaster, is placed in chambers on the suction side 7 is conveyed through the pump cavity 5 in the axial direction X to the pressure side 8 when the rotor 6 is set in rotation.
  • the pressure in the pump cavity 5 increases steadily towards the pressure side 8 so that a lower pressure acts on the elastically flexible lining 3 on the suction side 7 than on the pressure side 8.
  • the lining 3 is designed conically on its outer surface 9, with an average wall thickness W of the lining 3 from a position near the suction side 7 of the stator 1 in the axial direction X towards the pressure side 8 initially continuously, ie according to a constant function, decreases.
  • a contour K9 of the outer side 9 runs from the position near the suction side 7 in the axial direction X, linearly descending at least in regions, ie according to a linear function. This ensures that the elastic resilience of the lining 3 on the suction side 7 is higher than, for example, in the middle area of the stator 1 or in the area of the stator 1 with the smallest wall thickness WM.
  • the lining 3 becomes harder and harder towards the pressure side 8 (approximately linear).
  • the conical taper can be set in such a way that a mean pump diameter DP remains the same over the entire stator 1, so that no adaptation of the rotor 6 is necessary either.
  • only the outer surface 9 is tapered in the axial direction X towards the pressure side 8.
  • a continuous adaptation of the mean pump diameter DP, in particular a conical taper towards the pressure side 8 can also be provided.
  • the stator 1 has a widening 10 towards the pressure side 8, by means of which the mean wall thickness W is increased to an end wall thickness WE.
  • the end wall thickness WE on the suction side 7 preferably corresponds to the end wall thickness WE on the pressure side 8.
  • an A dimension A and a B dimension B can be specified for the stator 1, each representing the thickness of the lining 3 in a Z-direction Z or in a Y-direction Y.
  • both the A dimension A and the B dimension B decrease continuously in the axial direction X from the corresponding position.
  • the mean wall thickness W is continuously reduced down to the minimum wall thickness WM. Since the jacket 2 rests flat against the lining 3, preferably is adhered or vulcanized, its inner diameter D is also continuously reduced. An outer diameter E of the lining 3 thus corresponds to the inner diameter D of the jacket 2.
  • the stator 1 Due to the conical tapering of the lining 3 starting from the suction side 7 and the subsequent widening 10 on the pressure side 8, the stator 1 is divided into three zones V, H, S or areas: In a premixing zone V, which begins on the suction side 7 of the stator 1, there is a relatively low pressure in the pump cavity 5. At the same time, due to the comparatively high average wall thickness W in the premixing zone V, the lining 3 has high elastic flexibility and low hardness .
  • This premixing zone V is therefore suitable for crushing or pre-compacting a coarse-grained medium, for example mortar, plaster or sludge, which may still contain coarse material components, for example rocks, and mixing it evenly to form a homogeneous medium .
  • this premixing zone V Due to the high elastic resilience in this premixing zone V, the forces acting during the comminution of these coarse material components can be absorbed by the lining 3 without the lining 3 being damaged significantly beyond normal wear. This is supported by the fact that in the premixing zone V there are still low pressures acting in the pump cavity 5 and these are only very different increase slightly. This ensures optimal mixing.
  • the mean wall thickness W in the premixing zone V is constant at the end wall thickness WE. From a certain position in the axial direction X, the premixing zone Z changes into a high pressure zone H, this being initiated by a reduction in the mean wall thickness W of the lining 3. The reduction in the mean wall thickness W reduces the elastic resilience of the lining 3. At the same time, the pressure in the pump interior 5 increases in the axial direction X, so that the conveyed medium also acts on the lining 3 with higher forces. However, since the conveyed medium has already been comminuted and homogenized in the premixing zone V, the lining 3 is less stressed in the high pressure zone H because the material components of the medium tend to have smaller particle sizes.
  • the backflow behavior of the stator 1 can be improved by the conical structure of the high pressure zone H.
  • the conveyed medium can flow back if a pressure difference between adjacent chambers in the pump cavity 5 becomes too high. If a harder lining 3 is selected, the backflow only occurs at higher pressure differences between the chambers.
  • a stabilization zone S follows in the axial direction X in the stator 1 and is located in the area of the pressure side 8 or the widening 10.
  • the mean wall thickness W of the lining 3 is increased again and then runs constant, so that the elastic flexibility of the lining 3 increases again or the hardness of the lining 3 decreases again.
  • the premixing zone V there is a slight pressure build-up in the pump cavity 5 on the outlet side.
  • a connection for example via a flange, to the next component of the eccentric screw pump can be established to be provided.
  • a connection for example via a flange, to the next component of the eccentric screw pump can be established to be provided.
  • identical or standardized flanges or connections can advantageously be used. Due to the external shape of the stator 1, it can be clearly recognized in which orientation the stator 1 is to be mounted in the eccentric screw pump.
  • the reduction in the average wall thickness W in the axial direction X is achieved by continuously adapting the outer surface 9 of the lining 3 to the coiled inner surface 4 of the lining 3.
  • the outer surface 9 accordingly also forms a two-start coarse thread from a certain axial position. Since the jacket 2 rests flat against the outer surface 9 of the lining 3 or is adhered or vulcanized to it, the jacket 2 also follows the shape of the double helical thread of the inner surface 4 from a certain axial position.
  • This also divides the stator 1 in the axial direction X into a premixing zone V, a high pressure zone H and a stabilization zone S, with an approximately constant mean wall thickness W, which corresponds to the end mean wall thickness WE, being formed in the premixing zone V.
  • This achieves a high elastic resilience of the lining 3 over a certain area, whereby the medium provided via the suction side 7 can be comminuted, mixed or homogenized without damaging the lining 3 significantly beyond normal wear.
  • the mean wall thickness W of the lining 3 decreases continuously (dotted line in Fig. 2 ), whereby, as already mentioned, this is achieved in that the outer surface 9 of the lining 3 is attached to the double-helix thread formed by the inner surface 4 is continuously adjusted. This also causes a continuous tapering of the lining 3 in the axial direction starting from the suction side 7 in the direction of the pressure side 8.
  • the reduction in the mean wall thickness W or the increase in hardness takes place according to a different, steeper course, which increases the pumping effect even further, since there is an increased pressure increase.
  • a high pressure zone H is formed by the continuous tapering of the lining in the axial direction X, in which the elastic resilience of the lining 3 decreases continuously while the pressure in the pump cavity 5 increases at the same time.
  • the mean wall thickness W increases in the embodiment according to FIG Figure 2 in the area of the widening 10 and then remains constant, so that a stabilization zone S is also formed here.
  • the pressure in the pump cavity 5 increases only slightly due to the low flexibility, so that a low-wear and smooth transition with a stabilized medium to the next component in the eccentric screw pump can be provided.
  • the end wall thickness WE on the pressure side 8 corresponds to the end wall thickness WE on the suction side 7 in order to create an identical connection on both end sides of the stator 1.
  • Figure 2a shows the section through the stator 1 in the premixing zone V, the A dimension A and the B dimension B at this axial position with the dimensions A, B in Figure 1a essentially coincide with the first embodiment.
  • Figure 2b the section through the stator 1 in the high pressure zone H, ie after the taper, is shown.
  • the A dimension A is compared to the situation in the premixing zone V (see Sect. Figure 2a ) stayed the same. Only the B dimension B has decreased compared to the situation in the premixing zone V.
  • the continuous tapering of the lining 3 in the axial direction is thus achieved solely by adjusting the B dimension.
  • the semiaxes HA1, HA2 of the jacket 2 and the lining 3 behave in a corresponding manner.
  • a first semiaxis HA1 pointing in the Z direction remains constant in the axial direction X, while a second semiaxis pointing in the Y direction is HA2 is continuously tapered. Since the jacket 2 rests flat on the lining 3, the semi-axes HA1, HA2 of the jacket 2 (inner surface) and the lining 3 (outer surface) correspond.
  • a width VB of the premixing zone V in the axial direction X is increased compared to the previous embodiments.
  • it can be determined in a targeted manner, for example as a function of the field of application of the stator 1, over which extent a low-wear homogenization or mixing of the conveyed medium is to take place.
  • the width SB of the stabilization zone S can also be adjusted accordingly in order to give the medium a sufficiently large area for stabilization and thus to optimize the transition, for example depending on the area of application.
  • a width HB of the high pressure area H can also be selected accordingly in order to define the area in which the delivery rate is to be increased by a corresponding adaptation of the pressure gradient. This can be done in mutual coordination with the course of the mean wall thickness W in order to achieve a corresponding pressure increase along the conveying direction.
  • the widths VN, HB, SB can also in the first exemplary embodiment according to FIG Fig. 1 can be variably determined accordingly
  • the high pressure zone H is divided into two high pressure areas H1, H2.
  • the mean wall thickness W initially decreases continuously in the axial direction X until the lowest mean wall thickness WM is reached.
  • the mean wall thickness W remains approximately constant at the lowest mean wall thickness WM.
  • the mean wall thickness W of the lining 3 increases again starting from the lowest mean wall thickness WM towards the pressure side 8 of the stator 1, so that the widening occurs on the pressure side 8 10 forms in the lining 3.
  • a type of “hybrid stator” is provided, which is formed from a cylindrical stator in the premixing zone V and a two-flight coiled stator in the second high-pressure area H2 of the high-pressure zone H.
  • the mean wall thicknesses W within the two hybrid components are different but always constant.
  • the transition between the two hybrid components is ensured by the continuous adjustment of the mean wall thickness W in the first high pressure area H1, which at the same time also adjusts the hardness of the lining as in the first design variants in Fig. 1 and Fig. 2 is achieved.
  • the widening 10 is formed in the stabilization zone S by continuously adapting the mean wall thickness W.

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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)
EP19186418.0A 2019-07-16 2019-07-16 Stator pour une pompe à vis sans fin excentrique Active EP3767105B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP19186418.0A EP3767105B1 (fr) 2019-07-16 2019-07-16 Stator pour une pompe à vis sans fin excentrique
PL19186418T PL3767105T3 (pl) 2019-07-16 2019-07-16 Stojan do pompy ślimakowej mimośrodowej
ES19186418T ES2909699T3 (es) 2019-07-16 2019-07-16 Estator para una bomba helicoidal excéntrica
CN202080059862.5A CN114341496B (zh) 2019-07-16 2020-07-16 用于偏心螺杆泵的定子
PCT/EP2020/070106 WO2021009275A1 (fr) 2019-07-16 2020-07-16 Stator pour pompe à vis sans fin excentrique
UAA202200674A UA130058C2 (uk) 2019-07-16 2020-07-16 Статор для ексцентрикового гвинтового насоса

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19186418.0A EP3767105B1 (fr) 2019-07-16 2019-07-16 Stator pour une pompe à vis sans fin excentrique

Publications (2)

Publication Number Publication Date
EP3767105A1 true EP3767105A1 (fr) 2021-01-20
EP3767105B1 EP3767105B1 (fr) 2021-12-29

Family

ID=67303409

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19186418.0A Active EP3767105B1 (fr) 2019-07-16 2019-07-16 Stator pour une pompe à vis sans fin excentrique

Country Status (6)

Country Link
EP (1) EP3767105B1 (fr)
CN (1) CN114341496B (fr)
ES (1) ES2909699T3 (fr)
PL (1) PL3767105T3 (fr)
UA (1) UA130058C2 (fr)
WO (1) WO2021009275A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA3114159A1 (fr) 2020-04-02 2021-10-02 Abaco Drilling Technologies Llc Stators coniques dans des moteurs a deplacement direct pour corriger les effets de l'inclinaison du rotor
US11421533B2 (en) * 2020-04-02 2022-08-23 Abaco Drilling Technologies Llc Tapered stators in positive displacement motors remediating effects of rotor tilt

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0358789A1 (fr) * 1988-09-14 1990-03-21 FOREG Aktiengesellschaft Stator pour pompe à vis excentrique
DE19531318A1 (de) 1995-08-25 1997-02-27 Artemis Kautschuk Kunststoff Stator für Exzenterschneckenpumpen
DE4111166C2 (de) 1991-04-06 1999-03-18 Gummi Jaeger Kg Gmbh & Cie Exzenterschneckenpumpe
EP1503034A1 (fr) * 2002-04-24 2005-02-02 Vladimir Vsevolodovich Davydov Machine a rotor dente
EP1522729B2 (fr) 2003-10-07 2013-03-27 Johann Heinrich Bornemann GmbH - Kunststofftechnik Obernkirchen - Pompe à cavité progressive et stator pour une telle pompe
DE102012001617A1 (de) * 2012-01-30 2013-08-01 Netzsch Pumpen & Systeme Gmbh Vorrichtung zum Fördern von Medien

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2703148Y (zh) * 2004-04-22 2005-06-01 潘立明 锥形单螺杆泵
JP5821058B2 (ja) * 2010-12-27 2015-11-24 兵神装備株式会社 一軸偏心ねじポンプ
CN106907318A (zh) * 2017-04-20 2017-06-30 天津汉诺工业泵制造有限公司 一种单螺杆泵
CN209041106U (zh) * 2018-11-26 2019-06-28 保定毓嘉泵业制造有限公司 带有可调节式定子的螺杆泵

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0358789A1 (fr) * 1988-09-14 1990-03-21 FOREG Aktiengesellschaft Stator pour pompe à vis excentrique
DE4111166C2 (de) 1991-04-06 1999-03-18 Gummi Jaeger Kg Gmbh & Cie Exzenterschneckenpumpe
DE19531318A1 (de) 1995-08-25 1997-02-27 Artemis Kautschuk Kunststoff Stator für Exzenterschneckenpumpen
EP1503034A1 (fr) * 2002-04-24 2005-02-02 Vladimir Vsevolodovich Davydov Machine a rotor dente
EP1522729B2 (fr) 2003-10-07 2013-03-27 Johann Heinrich Bornemann GmbH - Kunststofftechnik Obernkirchen - Pompe à cavité progressive et stator pour une telle pompe
DE102012001617A1 (de) * 2012-01-30 2013-08-01 Netzsch Pumpen & Systeme Gmbh Vorrichtung zum Fördern von Medien

Also Published As

Publication number Publication date
CN114341496B (zh) 2023-10-13
WO2021009275A1 (fr) 2021-01-21
UA130058C2 (uk) 2025-10-29
EP3767105B1 (fr) 2021-12-29
PL3767105T3 (pl) 2022-05-02
ES2909699T3 (es) 2022-05-10
CN114341496A (zh) 2022-04-12

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