AU2007203551A1 - Feed screw for eccentric screw pump - Google Patents

Feed screw for eccentric screw pump Download PDF

Info

Publication number
AU2007203551A1
AU2007203551A1 AU2007203551A AU2007203551A AU2007203551A1 AU 2007203551 A1 AU2007203551 A1 AU 2007203551A1 AU 2007203551 A AU2007203551 A AU 2007203551A AU 2007203551 A AU2007203551 A AU 2007203551A AU 2007203551 A1 AU2007203551 A1 AU 2007203551A1
Authority
AU
Australia
Prior art keywords
screw
perforations
pump according
screw pump
eccentric screw
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.)
Abandoned
Application number
AU2007203551A
Inventor
Ulrich Braun
Klaus Gerbl
Helmuth Goschy
Karl-Heinz Grebisz
Markus Rosam
Melanie Wetzel
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 AU2007203551A1 publication Critical patent/AU2007203551A1/en
Abandoned 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/08—Scoop devices
    • F04B19/12—Scoop devices of helical or screw-type
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Landscapes

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

Description

-1-
AUSTRALIA
PATENTS ACT 1990 COMPLETE SPECIFICATION FOR A STANDARD PATENT
ORIGINAL
Name of Applicant/s: Actual Inventor/s: Netzsch-Mohnopumpen Gmbh Markus Rosam and Karl-Heinz Grebisz and Melanie Wetzel and Helmuth Goschy and Ulrich Braun and Klaus Gerbl Address for Service is: SHELSTON IP Margaret Street SYDNEY NSW 2000 CCN: 3710000352 Attorney Code: SW Telephone No: Facsimile No.
(02) 9777 1111 (02) 9241 4666 Invention Title: FEED SCREW FOR ECCENTRIC SCREW PUMP The following statement is a full description of this invention, including the best method of performing it known to me/us:- File: 54872AUP00 501253724 1 DOC/5844 r'l Feed screw for eccentric screw pump The invention relates to an eccentric screw pump with a feed screw which supplies the suction region of the screw rotor mainly with medium to highly viscous media.
DE 101 60 335 Al shows an eccentric screw pump in this regard where a feed screw is n arranged in the pump housing before the pump rotor. The screw is connected with the screw core via its entire inner contour.
DE 101 18 071 Al shows an eccentric screw pump about the coupling rod of which a iN hollow screw is arranged. This hollow screw is connected with a disc on the drive side.
The other end in the suction-side region of the screw rotor has no connection to a joint or the coupling rod.
With a mixing device according to DE 1 277 819 dry substances are mixed with liquid and subsequently delivered by a pump. To this end, a mixing screw is seated in the region of a storage vessel, which mixing screw is connected on the one side with a motor and, on the other side with a screw pump. Liquid enters the screw region between the storage vessel and the pump. The feed screw consists of a helical band which is only fastened to the mixer shaft at one end by means of four braces.
A mixing and feed device is also shown in DE 43 18 177. The dry substances enter the region of a mixing screw via a hopper, while a liquid feed line also leads into the region of said mixing screw. Following the mixing operation, the mixture is transported onwards by a screw pump. The mixing screw itself consists of a region with a solid screw and a region with paddle and web-shaped mixing elements.
Each pump is designed for a determined delivery rate. To this end, adequate medium must always be available for the pump region on the suction side. The feed screws, which are arranged upstream of the actual screw or eccentric screw pump, can therefore deliver a multiple volume of the pump capacity. Because of this, a back-up effect develops in the so-called stuffing space in the suction region which is associated with danger of bridge formation in the hopper above the screw. Because of this stuffing effect, substantially higher drive power than necessary must be made available.
The object of the invention consists in adapting the stability of the feed screw to the required output while keeping the drive power constantly low even with different media.
This object is solved through the characteristics of claim 1. Further developments of the feed screw according to the invention are indicated from the characteristics of the subclaims.
The design of a corresponding feed screw between the pump rotor and the drive has shown that the devices known from the prior art solve only part problems of the object t according to the invention.
N The design according to the invention is obviously dependent on which products with which viscosities, and, if applicable, present solid materials have to be pumped.
According to the invention the normal embodiment concerns a feed screw having at least two perforations, wherein the webs formed between these perforations are connected with their screw root with the coupling shaft. Depending on which viscosity the product has it may be practical to increase the number of perforations to at least four in order to facilitate the return flow of the medium and ensure more homogenous mixing-through, through which bridge formation of the medium is already counteracted on the suctionside end of the pump.
Through the perforations according to the invention, low-loss drive power compared with delivery devices from the prior art, designed to the condition of the medium can be installed.
In order to obtain the advantage according to the invention also in the regions of the couplings (joints) the screw also extends beyond this region for the purpose of which the pipe employed as coupling rod has strip-shaped pipe segments which are connected with the screw. If the number of the pipe segments corresponds to the number of the perforations, a corresponding number of webs for their fastening is available.
Since for the return flow of the medium not only the number of perforations but also their area place a substantial role, it can be provided according to a version according to the invention to dimension the perforations between 30% and 70% of the height of the screw start. With low-viscosity substances the height of the perforations can be selected in the range from 20 to 60 of the height of a screw pitch.
As is shown in an exemplary embodiment the width of the perforations will correspond to the width of the webs because of the homogenous return feed and even loading of the screw. With high-viscosity media the return flow possibility must certainly be improved rwherein the width of the perforations is greater than the width of the webs. With low Zviscosity substances the danger of bridge formation is relatively low so that here the width of the webs can be greater than that of the perforations.
To improve the return flow and thus reduce the stagnation effect the flow along the Icoupling shaft can be improved in that the webs have an inclination and thus produce a Vt flow direction which is opposite to the course of the screw.
Depending on which design of the screw is required, the webs can be offset to one another by 300 to 120 0 per screw start. In order for the feed screw to be stabilised about Sits entire length through the coupling shaft the length of the pipe segments is adapted to the course of the feed screw.
Easier affixing of the feed screw to the coupling shaft is obtained in that the feed screw consists of several parts which enable better handling during the mostly employed welding operation.
The invention is exemplarily described in the following by means of exemplary embodiments.
It shows: Fig. 1 Lateral view of the feed screw Fig. 2 A three-dimensional representation of the feed screw Fig. 3 A cross section of the feed screw Fig. 4 Feed screw with joint part on both sides Fig. 5 Lateral view of the feed screw according to Fig. 4 Fig. 6 Cross section of a feed screw Fig. 7 Screw cross section with 6 perforations Fig. 8 Screw cross section with 4 perforations rFig. 9 Screw cross section with various perforation distances from the coupling rod Fig. 1 shows a design possibility of a feed screw 10 with a screw pipe 12. A screw 14 is welded on to the circumferential surface of the screw pipe 12. On both ends 16, 18 of the screw pipe 12, pipe segments 20 for fastening the screw 14 are provided. Each of the pipe segments 20 ends at the point at which the screw 14 ends in axial direction. In the t region of the pipe elements 20, couplings 22 for the joints not shown are provided at both ends. The screw 14 is manufactured from flat band-shaped material.
The design of the screw 14 can be more clearly seen in Fig. 2. From the perspective N representation it becomes evident that the screw 14 is provided with perforations 24 and webs 26. Each screw root 34 of the webs 26 is connected with the pipe segment 20 or the coupling shaft 32 for example through a welding operation. While the medium in axial direction flows from the rotor region back to the pump inlet through the perforations of the feed screw closely along the screw pipe, the screw 14 with its end faces 28 transports the medium in the direction towards the pump rotor. The pump rotor, through a joint which is not completely shown, and which joint is fastened to the coupling 22, is in positive contact with the feed screw.
Fig. 3 shows the embodiment and arrangement of the perforations 24 and webs 26 for a feed screw for highly viscous media. Here, the large free areas of the perforations 24 enable very good return flow possibilities for the medium in order to adapt the stagnation pressure in the stuffing space to the pump output. Here, dehydration of the medium and increased tendency toward bridge formation is prevented and undesirably high drive power avoided.
The perforations 24 according to this exemplary embodiment are wider than the webs 26. The middle of the perforations in each case is located on the midperpendicular and is thus offset by 900 relative to one another which produces 4 perforations 24 and 4 webs 26 per screw pitch. The height of the perforations corresponds to approximately 50% of the screw height.
A feed screw 10 is also shown in Fig. 4 and Fig. 5. Here, a coupling shaft 32 is provided as drive component. A screw 14 is welded on to the coupling shaft 32 in the region between the joint components 30 which, as with all other exemplary embodiments, consists of individual screw segments. This embodiment of the screw 14 is employed for instance with low-viscosity media. By way of the large face areas 28 compared with the Sareas of the perforations 24, more medium enters the rotor region while the smaller dimensioned perforations nevertheless prevent an increased need for drive power.
CC The arrangement of the perforations 24 and their size of the feed screw 10 shown in Fig.
4 and 5 is shown in Fig. 6. Per screw pitch, three perforations each offset by 120 0 are provided in the screw 14.
Additional exemplary embodiments for the screw design for one winding each are Nshown in Fig. 7, 8, 9.
(1Fig. 7 represents an even distribution of 6 perforations 24 and webs 26. The height HD of the perforations is 50 compared with the height HS of the screw 14. The width BD of the perforations corresponds to the width BS of the webs.
In Fig. 8 the screw 14 has four perforations 24 and four webs 26 while the width BD of the perforations is greater than the width BS of the webs. The height HD of the perforations 24 is 50 of the height HS of the screw 14.
The interrupted lines of Fig. 9 shows different size relationships with regard to the height HD of the perforations to the height HD of the screw 14, while three perforations 24 are shown with a division by 120 List of reference numbers 10 Feed screws 12 Screw pipe 14 Screw 16, 18 Coupling shaft ends Pipe segments 22 Couplings Perforations -7-
O
O
S26 Webs 28 End face 30 Joint components 32 Coupling shaft 34 Screw root

Claims (11)

  1. 2. The eccentric screw pump according to claim I, characterized in that at least four perforations are present per screw pitch.
  2. 3. The eccentric screw pump according to claim 1 or 2, characterized in that the coupling shaft has a screw pipe on which strip-shaped pipe segments (20) are located at one end parallel to the longitudinal axis of the feed screw (10) which are connected with the screw (14).
  3. 4. The eccentric screw pump according to claim 3, characterized in that the number of pipe segments (20) corresponds to the number of perforations (24). The eccentric screw pump according to any one of the claims 1, 2 or 4, characterized in that the height (HD) of the perforations (24) corresponds to between 30 and 70 of the height (HS) of the screw (14).
  4. 6. The eccentric screw pump according to claim 5, characterized in that the height (HD) of the perforations (24) corresponds to between 20 to 60 of the height (HS) of the screw (14).
  5. 7. The eccentric screw pump according to claim 3 or 4, characterized in that the pipe segments (20) in the operational state cover the joint element/s
  6. 8. The eccentric screw pump according to any one of the claims 1 to 7, characterized in that the width (BD) of the perforations (24) corresponds to the width (BS) of the webs (26) which are connected with the coupling rod.
  7. 9. The eccentric screw pump according to any one of the claims 1 to 7, characterized in that the width (BD) of the perforations (24) is greater than the width (BS) of the webs (26). The eccentric screw pump according to any one of the claims 1 to 8, characterized in thatthe width (BS) of the webs (24) is greater than the width Cc (BD) of the perforations (26).
  8. 11. The eccentric screw pump according to any one of the claims 1 to t characterized in that the webs (26) have an inclination opposite to the course of the screw.
  9. 12. The eccentric screw pump according to any one of the claims 1 to 11, Scharacterized in that the webs (26) are offset to one another by 30 O to 120 O
  10. 13. The eccentric screw pump according to claims 7, characterized in that the length of the pipe segments (20) is adapted to the course of the screw (14).
  11. 14. The eccentric screw pump according to any one of the claims 1 to 13, characterized in that the screw (14) consists of several parts. An eccentric screw pump substantially as herein described with reference to any one of the embodiments of the invention illustrated in the accompanying drawings and/or examples.
AU2007203551A 2006-08-03 2007-07-30 Feed screw for eccentric screw pump Abandoned AU2007203551A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006036243 2006-08-03
DE102006036243A DE102006036243A1 (en) 2006-08-03 2006-08-03 Feed screw for eccentric screw pump

Publications (1)

Publication Number Publication Date
AU2007203551A1 true AU2007203551A1 (en) 2008-02-21

Family

ID=38535631

Family Applications (1)

Application Number Title Priority Date Filing Date
AU2007203551A Abandoned AU2007203551A1 (en) 2006-08-03 2007-07-30 Feed screw for eccentric screw pump

Country Status (9)

Country Link
US (1) US20080031758A1 (en)
EP (1) EP1884660A1 (en)
JP (1) JP2008038907A (en)
KR (1) KR20080012769A (en)
CN (1) CN101122287A (en)
AU (1) AU2007203551A1 (en)
BR (1) BRPI0703164A (en)
CA (1) CA2595015A1 (en)
DE (1) DE102006036243A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009024088A1 (en) 2009-06-06 2010-12-09 Zeus Gmbh Tire filler, method for producing a tire filling and apparatus for carrying out the method
KR101035078B1 (en) * 2011-01-14 2011-05-19 주식회사 유성엔지니어링 Screw pump
US10087758B2 (en) 2013-06-05 2018-10-02 Rotoliptic Technologies Incorporated Rotary machine
US10436068B2 (en) * 2016-02-12 2019-10-08 General Electric Company Flowpath contouring
CN108373929A (en) * 2018-05-07 2018-08-07 青岛科技大学 The continuous output device of cracked residue and method of a kind of scrap rubber or waste plastics
WO2020051690A1 (en) 2018-09-11 2020-03-19 Rotoliptic Technologies Incorporated Helical trochoidal rotary machines
USD927968S1 (en) * 2019-03-28 2021-08-17 Ojjo, Inc. Screw anchor
US11815094B2 (en) 2020-03-10 2023-11-14 Rotoliptic Technologies Incorporated Fixed-eccentricity helical trochoidal rotary machines
US11802558B2 (en) 2020-12-30 2023-10-31 Rotoliptic Technologies Incorporated Axial load in helical trochoidal rotary machines

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3271081A (en) * 1964-09-28 1966-09-06 Phillips Petroleum Co Apparatus and process for pumping slurry
DE1244723B (en) * 1965-05-12 1967-07-20 Karl Schlecht Dipl Ing Device for the continuous mixing of dry material with a liquid
DE1277819B (en) * 1965-05-12 1968-09-19 Karl Schlecht Dipl Ing Device for continuous mixing of powdery to fine-grained bulk material
US4134736A (en) * 1978-02-22 1979-01-16 E. I. Du Pont De Nemours And Company Steam-polymer separation apparatus
JPS58192814U (en) * 1982-06-15 1983-12-22 株式会社神戸製鋼所 Screw blade structure
SE435951B (en) * 1983-03-14 1984-10-29 Sunds Defibrator CENTRIFUGAL PUMP WITH SCREW FEED FOR PUMPING PUMP WITH HIGH CONCENTRATION
JPH0748587Y2 (en) * 1988-07-12 1995-11-08 兵神装備株式会社 Powder transfer device
DE4121717C2 (en) * 1991-06-07 1995-01-26 Allweiler Ag Screw pump, in particular eccentric screw pump
DE9211567U1 (en) * 1992-08-27 1992-10-29 BuG Betriebsanlagen- und Grundbesitz GmbH, 8046 Garching Device for the on-site production of pumpable mortar masses
DE4442060C1 (en) * 1994-11-25 1996-03-14 Netzsch Mohnopumpen Gmbh Eccentric screw pump for highly viscous media
DE10118071C2 (en) * 2001-04-11 2003-05-28 Seepex Seeberger Gmbh & Co Eccentric screw pump
DE10160335B4 (en) * 2001-12-07 2006-02-02 Ksb Aktiengesellschaft Feeding device for an eccentric screw pump

Also Published As

Publication number Publication date
CN101122287A (en) 2008-02-13
JP2008038907A (en) 2008-02-21
CA2595015A1 (en) 2008-02-03
US20080031758A1 (en) 2008-02-07
DE102006036243A1 (en) 2008-02-14
BRPI0703164A (en) 2008-03-25
EP1884660A1 (en) 2008-02-06
KR20080012769A (en) 2008-02-12

Similar Documents

Publication Publication Date Title
AU2007203551A1 (en) Feed screw for eccentric screw pump
KR101717276B1 (en) Device for mixing
US20090123319A1 (en) "rotary piston pump comprising a pump housing and two double bladed rotary pistons"
US10233921B2 (en) Axis eccentric screw pump with decreasing sectional area of stator with a constant diameter rotor
US11085710B2 (en) Heat exchanger
KR102356133B1 (en) Control of Gap Geometry in Eccentric Screw Pumps
JPH0617771A (en) Pump for high viscous material
JP6975714B2 (en) Flexographic printing equipment and inlet module
US6213745B1 (en) High-pressure, self-lubricating journal bearings
JP2006142616A (en) Hermetically closed kneader and kneading rotor used therein
AU755036B2 (en) High output device for liquifying or reducing the viscosity of materials
US20110128813A1 (en) Fluid mixer with rotary shafts and relative seal unit
KR20140023865A (en) Rotary displacement pump for pumping solids emulsions, especially liquid explosives
KR101728260B1 (en) Multiple pump arrangement
US10610896B1 (en) Hydraulic vibration generating device
CN112814896A (en) Sealing drive for connecting a progressive cavity pump rotor to a universal joint
CN114341496A (en) Stator for eccentric screw pump
US20200061555A1 (en) Dynamic mixer and dosing device
US9488170B2 (en) Gear pump driven gear pressure loaded bearing
JP4971600B2 (en) Pipe transport method and transport device for dehydrated cake
KR100274572B1 (en) A stator of a mono pump
DE10160335A1 (en) Input device for eccentric spiral pump has rise of spiral equal to at least half the filing funnel width measured in axial direction of spiral
JP6574539B2 (en) Fluid supply system
CN219816268U (en) Slurry mixing device
US10858940B1 (en) Bearing with an asymmetric pressure balance groove

Legal Events

Date Code Title Description
MK5 Application lapsed section 142(2)(e) - patent request and compl. specification not accepted