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
  • 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
• • 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
• • 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
  • F04C2240/10—Stators
• • 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
  • F04C2240/80—Other components
  • F04C2240/802—Liners

Definitions

• the invention relates to an eccentric screw pump with a stator, which can be adjusted predominantly in the context of regular operation, according to the preamble of claim 1.
• Eccentric screw pumps are ideal for pumping fluids that contain abrasive components. You benefit from the fact that the pumping action of the eccentric screw pump is based on the principle of moving conveyor chambers that are formed between the central conveyor screw and the double-pitched screw thread formed by the stator lining.
• the support tubes 6 and 7 prevent the stator lining 5 from giving way radially outward when it is compressed in the area of its protrusion 19.
• the stationary support tube 7 is often equipped with an inner cone 10 into which the mobile support tube 6 slides deeper with increasing compression.
• the stationary support tube is usually stretched, which requires considerable forces that would be more beneficial if they were available to generate a transverse expansion of the stator lining over its entire length.
• the starting point is accordingly an eccentric screw pump with a rotor forming a screw conveyor and a stator forming a screw flight in which the rotor rotates in the conveying mode.
• the stator comprises a one-part or multi-part - in the latter case possibly not only transversely but also segmented in the direction of the longitudinal axis L of the stator or divided into several parts - stator housing.
• a stator lining made of an elastomeric, preferably vulcanized, material.
• the central cavity of the stator lining forms the worm gear.
• the stator lining forms a protrusion on at least one side along the longitudinal axis of the pump. This protrudes from the stator housing in such a way that a free force introduction surface is formed, via which a force can be applied which compresses the stator lining into the stator housing. The compression takes place in such a way that a transverse expansion of the stator lining occurs (especially) in the stator housing. The transverse expansion creates a narrowing of the worm thread.
• the protrusion is encompassed on its outer circumference by a mobile support tube.
• the mobile support tube can be displaced in the direction along the longitudinal axis of the stator housing relative to the stator housing.
• the mobile support tube or its circumferential jacket surface viewed in the radial direction, is arranged at least predominantly, preferably completely, in a recess of the stator lining. Ideally, only its radially protruding collar protrudes outwards.
• the outer circumferential surface of the mobile support tube closes off evenly or with a smooth surface. Then there is - at least essentially - no change in diameter with respect to the surrounding outer peripheral surface of the stator lining.
• an eccentric screw pump is thus obtained which can be set more precisely or more uniformly over its entire stator length.
• the eccentric screw pump according to the invention usually offers a particularly long distance by which the stator lining can be compressed, so that an enlarged adjustment range results.
• the mobile support tube is preferably designed so that it has an insertion length of at least! , better at least the outer radius of the stator lining.
• the cohesive connection can in particular be an “adhesive connection through vulcanization”, otherwise also a gluing in the actual sense or a welding, for example with a plastic layer of the support tube.
• the support tube can have connecting aids, such as holes / openings into which material penetrates that is later solidified by vulcanizing, ribs or a particularly rough, for example knurled, inner surface, which is intimately connected with the vulcanized material.
• stator lining This special way enables the stator lining to be compressed particularly well or evenly in the course of the adjustment, even when extremely strong compression is required.
• the eccentric screw pump it can make sense to design the eccentric screw pump so that the mobile support tube can be pushed into the stator housing itself for compression and that its outer diameter is smaller than the smallest inner diameter of the section of the stator housing available for insertion. In this way, the number of components of the eccentric screw pump is kept as small as possible, which reduces the manufacturing costs.
• the support tube is pushed into a stationary support tube attached in front of the end face of the stator housing for compression and its outside diameter is inherently smaller than the smallest inside diameter of the section of the stationary support tube available for insertion.
• stator housings can be used for the construction of the adjustable eccentric screw pumps that are also used for the construction of non-adjustable eccentric screw pumps. This also applies if this stator housing - different from the mobile Support tube - do not have a circular, but a polygonal clear cross-section on the inside.
• the stationary support tube preferably has a first radial flange on which one or more compression members act, mostly in the form of traction means. If traction devices are used, they are advantageously designed as threaded rods. With the aid of such a radial flange, forces for compressing the stator lining can be applied in a particularly simple manner, without the need to make structural changes to the substance of the stator housing.
• the mobile support tube then has a second radial flange on which one or more of the said compression members engage. In this way, the mobile support tube can be particularly easily involved in applying the forces required to compress the stator lining.
• Said threaded rods can, for. B. be equipped with nuts or rigid hexagonal heads, which are tightened manually using an open-end wrench if necessary.
• they can also carry actuators that are driven with a type of planetary gear through a sun-like gear in the manner of a planetary gear.
• the drive is motorized. This then turns nuts on the threaded rods or the threaded rods themselves.
• the mobile support tube or the second radial flange is preferably designed in such a way that, during compression, force is also introduced into the stator lining via the end ring surface on the free end face of the protrusion, prefers even the greater part of the force. In some cases it is beneficial to even introduce essentially all of the force in this way.
• the narrowing according to the method is carried out by compressing the stator lining, which is supported over its outer circumference in the radial direction by a stator housing, in the direction of the longitudinal axis of the stator.
• the compression force is applied to a protrusion, which the front of the actual stator housing forms outstanding stator lining.
• the method according to the invention is characterized in that the compression force is applied, at least in part, more than only insignificantly, to the protrusion by means of a shear stress which acts on one of its circumferential surfaces.
• Figure 1 shows a previously considered concept.
• FIG. 2 shows an overview of an eccentric screw pump as a whole.
• FIG. 3 shows the stator of an eccentric screw pump according to the invention.
• FIG. 4 shows an enlarged detail from FIG.
• FIG. 2 shows the eccentric screw pump 1 forming the basis of the invention as a whole.
• the main components of such an eccentric screw pump 1 are the suction housing 11 and the pump section 12 which is in flow connection with it.
• the inlet 13 for the medium to be conveyed is formed on the suction housing 11.
• the pumped medium is output via the outlet 14 arranged at the end of the pump section 12.
• the block construction is preferred, even if this is not mandatory under patent law.
• the pump motor 15 is then flanged to the suction housing 11.
• the pump motor 15 drives the rotor, which will be described in more detail in a moment, via the mostly cardanic power train 16.
• the pump section is formed by the stator 3 with the rotor rotating therein.
• the rotor is formed by an eccentric screw 2, which can be classified as a round thread screw. Compared to a normal screw, the eccentric worm has a larger pitch, a larger thread depth and a smaller core diameter.
• the stator 3 is designed to be complementary to the rotor.
• the tightness of the contact line between rotor and stator influences the suction capacity and the achievable delivery pressure of the pump.
• FIG. 3 shows the pump section 12 already mentioned with reference to FIG. 2, but without showing the eccentric screw.
• the stator 3 can be clearly seen in FIG. 3. It consists of the stator housing 4, which can be optionally divided here and in which the stator lining 5 is located. On its outer circumferential surface, the stator lining 5 has no or at least essentially no frictional connection with the inner surface of the stator housing 4. The stator housing 4 therefore does not hinder the compression of the stator lining 5, which will be explained in more detail later
• stator lining 5 protrudes from the stator housing 4 on the left-hand side and forms a protrusion 19 there can also be clearly seen on the basis of the figure.
• This protrusion 19 lies at least essentially radially within the mobile support tube 6. Most of the time, the smaller part lies within the stationary support tube 7.
• a compression device 8 is connected to the support tubes 6 and 7. This comprises the first radial flange 20 of the stationary support tube 7 and the second radial flange 21 of the mobile support tube 6.
• the first radial flange 20 can be attached to the stationary support tube 7 or directly to the stator housing 4.
• the second radial flange 21 is generally connected to the mobile support tube 6, preferably welded.
• the distance between the two radial flanges 20 and 21 is adjustable.
• a traction means 22 is provided for this purpose, preferably in the form of a threaded rod.
• the first radial flange 20 has an internal thread for anchoring the threaded rod.
• the second radial flange 21 can have through holes through which the respective threaded rod passes in order to then be screwed to an actuating nut 23 on the other side.
• the particular positioning of the mobile support tube according to the invention can be seen very well in FIGS. 3 and 4.
• the stator lining 5 has on its outer circumferential surface a recess 25, which in many cases is purely annular-cylindrical.
• the recess 25 is preferably long and flat.
• the amount by which the said base extends along the longitudinal axis L is then preferably by at least a factor of 7.5, better by at least a factor of 10, greater than the amount by which each end wall of the recess 25 extends radially outward.
• the mobile support tube 6 is vulcanized into the stator lining 5 or fastened to it by gluing or "welding" in the broad sense that - preferably across the entire bottom of the recess 25 - a shear stress-resistant connection between the inner surface extending beyond a purely frictional connection the circumference of the mobile support tube and the elastomer of the stator lining 5 resting against it from the inside. It can be useful to make this connection resistant to shear stress over a particularly large length, for example over a length parallel to the longitudinal axis L of at least 1/2 or even better even at least 2/3 of the outer diameter of the stator lining.
• the stationary support tube 7 that can be seen in FIG. 4 is optionally available.
• the first radial flange 20 and the second radial flange 21 are moved towards one another. Since the mobile support tube 6 is non-positively connected to the second radial flange 21, it is pushed into the stationary support tube 7 in a direction parallel to the longitudinal axis L. It is also noteworthy that the stator lining is generally nowhere hollow, but is completely supported everywhere in the radially outward direction. This also differs from the previous solution shown in FIG. 1 in this respect.
• the mobile support tube 6 transmits a shear stress on its inner surface to the stator lining 5 located in its interior. This is propagated within the stator lining 5 into the area of the stator housing 4. However, the opposite end of the stator lining 5 is firmly clamped, so it cannot move in the direction of the longitudinal axis L. Because of this, transverse expansion occurs within the stator lining in the area of the stator housing 4. In the radially outward direction, this transverse expansion is prevented by the stator housing 4. As a result, there is a considerable transverse expansion in the radially inward direction. This narrows the worm thread.
• the above-described connection, which is resistant to shear stress, between the inner surface of the mobile support tube 6 and the part of the stator lining 5 located in it allows a very uniform introduction of force into the stator lining 5.
• force can also be introduced via the end ring surface S of the stator lining 5 in the region of the free end of the protrusion 19. Often this is even the major part of the force introduced for compression.
• traction means preferably in the form of a threaded rod

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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)
• Electromagnetic Pumps, Or The Like (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=76744563

Family Applications (1)

Country Status (8)

Families Citing this family (1)

Family Cites Families (13)

• 2020
  • 2020-06-05 DE DE102020114937.9A patent/DE102020114937A1/de active Pending
• 2021
  • 2021-06-01 WO PCT/DE2021/000103 patent/WO2021244688A1/de active Application Filing
  • 2021-06-01 US US18/000,760 patent/US20230265847A1/en active Pending
  • 2021-06-01 EP EP21736956.0A patent/EP4193065A1/de active Pending
  • 2021-06-01 CN CN202180040084.XA patent/CN115917151A/zh active Pending
  • 2021-06-01 AU AU2021284794A patent/AU2021284794A1/en active Pending
  • 2021-06-01 BR BR112022023605A patent/BR112022023605A2/pt unknown
• 2022
  • 2022-12-02 ZA ZA2022/13097A patent/ZA202213097B/en unknown

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