EP1831570B9 - Pumpe, insbesondere dickstoffpumpe - Google Patents

Pumpe, insbesondere dickstoffpumpe Download PDF

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Publication number
EP1831570B9
EP1831570B9 EP05806528.5A EP05806528A EP1831570B9 EP 1831570 B9 EP1831570 B9 EP 1831570B9 EP 05806528 A EP05806528 A EP 05806528A EP 1831570 B9 EP1831570 B9 EP 1831570B9
Authority
EP
European Patent Office
Prior art keywords
rotor
pump according
longitudinal
pump
prismatic body
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.)
Not-in-force
Application number
EP05806528.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1831570A2 (de
EP1831570B1 (de
Inventor
Herbert Jung
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.)
Jung Herbert
Original Assignee
Jung Herbert
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 Jung Herbert filed Critical Jung Herbert
Publication of EP1831570A2 publication Critical patent/EP1831570A2/de
Application granted granted Critical
Publication of EP1831570B1 publication Critical patent/EP1831570B1/de
Publication of EP1831570B9 publication Critical patent/EP1831570B9/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0015—Radial sealings for working fluid of resilient material
    • 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
    • F04C2/22—Rotary-piston machines or pumps of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth-equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/02—Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to a pump, in particular sludge pump, with a rotating in a housing driven rotor.
  • Concrete is usually pumped on construction sites via so-called concrete distribution booms, which are stationary or mounted on roads suitable chassis, pumped to the point of application.
  • the pumping characteristic described causes a swinging of the boom, from which arise at the end, ie at the exit point of the concrete, movements whose extent, increasing with increasing mast length, endanger the working people in this area and the introduction of the concrete to the utmost make it difficult, even impossible.
  • accelerations results mainly from the mass of the conveyed Increasing length of the delivery line increasingly increased energy consumption for the drive.
  • peristaltic pump Another type of pump used to convey such thick materials as concrete is the so-called peristaltic pump. It is characterized by a simple, rotationally continuous drive. Due to the design results for the peristaltic pump a considerably lower discontinuity in the promotion than in the previously described piston pump. However, their use is limited to comparatively low discharge pressures (up to 30 bar), which severely restricts their use in the pumping of thick materials.
  • the EP 0 799 996 shows a pump in the manner of a Wankel engine with a rotary piston.
  • two suction openings and two discharge openings are provided on the circumference of a trochoidal housing having at the narrowest point stationary sealing or separating strips to separate the suction from the discharge openings.
  • the rotary piston in this case has a curved outer surface to ensure the required seal. As a result, however, the production is complicated, especially since the stationary sealing strips are required, which are also exposed to high wear.
  • the invention is based on the object, a new positive displacement pump, in particular for use as a slurry pump for pumping non-homogeneous, abrasive media such.
  • a new positive displacement pump in particular for use as a slurry pump for pumping non-homogeneous, abrasive media such.
  • the designed as a prism-like body rotor in which at least the connecting lines of the corners of the bases form an equilateral polygon, generated with its longitudinal edges during its rotation about its, simultaneously moved on a circular path center axis, the longitudinal inner wall surface of the housing.
  • the rotor whose center axis passes through a full circle, must be rotated about the central angle of the equilateral polygon formed by the connecting straight lines of the corners of the base areas of the prismatic body. It follows that the shape of the longitudinal inner wall surface of the housing is determined by the number of longitudinal edges of the prismatic body.
  • the circular motion of the center axis of the rotor is generated by its storage on the eccentric of the, mounted in the end walls of the housing, driven eccentric shaft.
  • the rotation of the rotor about its center axis according to the described regularity can be enforced with various gears.
  • the location of the feed and discharge ports, in conjunction with the length of the prismatic body, determines the geometric displacement of the pump. Therefore, in order to obtain the largest possible flow rate, it is necessary to set the position of the supply and discharge openings so that the value for the geometric displacement becomes maximum.
  • a feed container angeaut.sein wherein the sludge pump is arranged so that their feed opening (s) in the feed container are below the lowest level of the filled conveyed.
  • a preferably cylindrical intermediate wall Arranged in the rotor, preferably on the center axis thereof, is a preferably cylindrical intermediate wall which radially surrounds the gear described and which extends to the inner wall surfaces of the two end walls of the housing. It is advantageous to determine the radial position of the intermediate wall in connection with the determination of the rotor dimensions so that the swept from the end faces of the intermediate wall surfaces outside of the end faces of the, the longitudinal outer wall surfaces of the prismatic body forming outer walls of the rotor swept Areas lie.
  • the space formed by the long-side inner wall surfaces of the outer walls of the prism-like body and the long-side outer wall surfaces of the intermediate wall in communication with the inner wall surfaces of the two end walls of the housing is provided as a washing chamber.
  • the supply and removal of the rinsing liquid can be done either via the frontal walls of the housing or over, through the eccentric shaft and the rotor leading lines.
  • the rubber-elastic elements are preferably vulcanized or glued.
  • the size of the connecting surfaces is increased by the fact that the rubber-elastic elements extend beyond the end faces on the longitudinal outer wall surfaces of the outer walls of the prismatic body.
  • this eliminates a high wear resistance of the longitudinal outer wall surfaces of the metallic outer walls.
  • sealing strips separate by their constant contact with the longitudinal inner wall surface of the housing, the pumping chambers from each other or seal against each other.
  • the sealing strips are preferably held interchangeably on the longitudinal edges of the prismatic body. They are made of highly wear-resistant and hard material, as they also run over the feed and discharge openings on the longitudinal inner wall surface of the housing with their end faces and thereby cut through the fluid.
  • the weather strips may be received and held in a groove machined in the longitudinal edges of the prismatic body.
  • the longitudinal edges of the prismatic body additionally mutually incorporated and filled with vulcanized or glued rubber elastic material recesses may be present, so that when they are acted upon by the pressure of the pumped medium held in the grooves incorporated sealing strips are pressure-dependent pressed against the longitudinal side inner wall surface of the housing ,
  • the sealed spaces facing sides of the sealing elements are expediently equipped with very good wiping action, so that on the inner wall surfaces of the frontal walls of the housing adhering fine-grained and abrasive particles are reliably stripped off.
  • the longitudinal outer walls of the prism-like body are formed by a plurality of, preferably identical, individual elements, which are releasably secured to a base body, which is composed of the other elements of the rotor.
  • the longitudinal outer walls of the prism-like body are formed by an undivided element, which is releasably secured to a base body composed of the remaining elements of the rotor.
  • the longitudinal outer walls of the prismatic body no separation points are present, which complicate the seal between the delivery chambers and the interior of the rotor. Furthermore, a simpler assembly of the rotor is given by the one-piece element.
  • the inner wall surface of the longitudinal housing wall is formed wear-resistant and / or equipped with a wear-resistant coating, so that the removal in the promotion of abrasive media such. B. concrete is kept as low as possible.
  • On the inner sides of the two end walls of the housing releasably secured plates are provided, at least in the area of swept by the front-side sealing elements and guide elements of the rotor surfaces.
  • the inside surfaces of the plates serve as a mating surface for the sealing elements and guide elements of the rotor and at the same time form the frontal boundaries of the constantly changing delivery chambers and the rinsing chamber. This requires a very smooth and wear-resistant surface, which is preferably produced by a coating, in particular by hard chrome plating.
  • the pump housing is formed from a longitudinal wall and two detachably connected end walls.
  • the shape of the inner surface of the longitudinal housing wall results from the path of the longitudinal edges of the prismatic body during its movement in accordance with the described regularity.
  • the supply and discharge openings for the conveyed material are arranged.
  • the front-side housing walls are preferably screwed via a flange with the longitudinal housing wall.
  • the bearings for the eccentric shaft are arranged in the center of the frontal housing walls.
  • the diameter of the eccentric is expediently made larger than the, increased by twice the amount of eccentricity, the largest shaft diameter.
  • the bearings and the gear teeth, as well as the front-side sealing elements and guide elements on the rotor are supplied to minimize the wear of at least one central lubrication system with lubricants. At all lubrication points on the rotor, the lubricants are supplied via lines guided by the eccentric shaft.
  • the rotor is designed as a prism-like body, in which at least the connecting straight lines of the corners of the base surfaces form an equilateral triangle.
  • the largest possible delivery volume with comparable rotor dimensions or with a given delivery volume results in the lowest comparable rotor dimensions.
  • the diameter of the circumference of, formed from the connecting lines of the corners of the base surfaces of the prismatic body apply.
  • the space for the gear arranged in the rotor can be greater than through the connecting straight line of the rotor Defined corners of the prism-like body, trained. Due to the described bulges and the ineffective for the delivery volume proportion of space is reduced in the delivery areas.
  • Fig. 1 shows a slurry pump 1 with a designed as a triangular prism rotor 4 and the longitudinal side wall of the housing 2 in cross-section shown schematically.
  • a transmission 5 is arranged in the center of the rotor 4.
  • the longitudinal wall of the housing 2 is interrupted once each by an opening for the supply (Z) and an opening for the delivery (A) of the conveyed. Furthermore, it is shown how the thick matter pump 1 immersed in its installed position with the feed opening in the pumping medium (possibly in a feed container).
  • Upon rotation of the rotor 4 in a clockwise direction results here a promotion of the feed opening to the discharge opening; with opposite rotation, the promotion results from the discharge opening to the feed opening.
  • Fig. 2 is a slurry pump according to Fig. 1 shown in longitudinal section.
  • an eccentric shaft 3 is mounted with its eccentric 3a in the front-side housing walls 2b. It is powered by a motor.
  • the rotor 4 is mounted on the eccentric 3a of the eccentric shaft 3, the rotor 4 is mounted. It is made up of, arranged in the center hub for receiving the bearing 4a, a web 4a with a centrally arranged intermediate wall 6 and the also centrally arranged, at the web via screw fastened element 4b, with the longitudinal outer walls of the rotor Prismas are formed, together.
  • the flushing chamber (S) is formed in connection with the inner wall surfaces of the two end walls of the housing.
  • rubber-elastic elements 7a are vulcanized.
  • sealing strips 4c are arranged on the longitudinal edges of the rotor prism 4 '. In the end faces of the partition sealing elements and guide elements 7b are inserted into correspondingly incorporated grooves.
  • the intermediate wall 6 also serves to receive and fix the likewise centrally arranged in the rotor 4 ring gear 5b, which engages in the, arranged on the axis of rotation of the eccentric shaft 3, attached to the frontal housing wall 2b pinion 5a.
  • a bearing for the eccentric shaft 3 is arranged in the hub of the housing-fixed pinion 5a.
  • the housing 2 is composed of a longitudinal side wall 2a and two end walls 2b.
  • the end walls 2b are bolted to the longitudinal side wall 2a via a flange connection.
  • the inside wall surface of the longitudinal housing wall 2a is here equipped with a particularly hard and wear-resistant lining, on the surface of the front surfaces of the, arranged on the longitudinal edges of the rotor prism sealing strips 4c slide.
  • the lining is replaceable fastened.
  • wear plates 8 are mounted interchangeable with a hard surface and high surface quality, they serve as mating surfaces for the end-side sealing elements and guide elements 7a, 7b on the rotor 4th
  • Fig. 3 the contour of the longitudinal outer walls of a triangular rotor prism for a preferred embodiment of the rotor 4 is shown.
  • the advantage of formed with such bulges, longitudinal outer walls in a triangular rotor prism is in the enlargement of the space for the enclosed therein gear 5 while reducing the ineffective for the volume volume space in the delivery chambers.
  • Fig. 4 shows in a detailed representation of a possible embodiment for the corner region in a triangular rotor prism.
  • the sealing strip 4c is held here in a, in the longitudinal edge of the rotor prism 4 'incorporated groove.
  • On one side is shown in cross-section one of the mutually incorporated, filled with elastomeric material recesses 4 '"and one of the vulcanized on the longitudinal outer walls of the rotor prism 4' rubber-elastic elements 7a.
  • Fig. 5 is a pump according to Fig. 1 with a transmission 5 according to claim 3 shown schematically in longitudinal section.
  • the diagram shows all the main parts of the pump such as the housing 2, the eccentric shaft 3, the rotor 4 and in particular the elements of the transmission 5 according to claim 3. It can be seen that on the axis of the Eccentric shaft 3 arranged in the center of the housing 2 fixed housing pinion 5a with the arranged on the center axis of the eccentric 3a and the mounted on the eccentric 3a rotor 4, rotor-fixed ring gear 5b meshes (as in Fig. 2 shown).
  • Fig. 6 is a pump according to Fig. 1 with a transmission according to claim 4 in longitudinal section and partially in plan view shown schematically.
  • the schematic diagram contains as in Fig. 5 all main parts of the pump 1 and in particular here the elements of the transmission 5 according to claim 4.
  • the planetary gear arranged on the center axis of the eccentric 3a and of the eccentric 3a mounted rotor 4 can be seen.
  • the sun gear 5c is rotationally fixed on the eccentric 3a of the eccentric shaft 3; the planet gears 5d are rotatably mounted on the rotor-fixed planetary carrier 5e.
  • the ring gear 5f is rotatably mounted on the eccentric 3a of the eccentric shaft 3 and connected via its hub with the guide rod of a cross coupling 5g. It can not perform rotation about the center axis of the eccentric 3a by this connection and is supported by the cross coupling 5g on the housing 2.
  • the cross coupling (5g) is separate in the right half of Fig. 6 also shown schematically in a plan view.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP05806528.5A 2004-10-29 2005-10-29 Pumpe, insbesondere dickstoffpumpe Not-in-force EP1831570B9 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004052928A DE102004052928B4 (de) 2004-10-29 2004-10-29 Pumpe, insbesondere Dickstoffpumpe
PCT/EP2005/011611 WO2006048212A2 (de) 2004-10-29 2005-10-29 Pumpe, insbesondere dickstoffpumpe

Publications (3)

Publication Number Publication Date
EP1831570A2 EP1831570A2 (de) 2007-09-12
EP1831570B1 EP1831570B1 (de) 2013-08-21
EP1831570B9 true EP1831570B9 (de) 2014-02-12

Family

ID=35636745

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05806528.5A Not-in-force EP1831570B9 (de) 2004-10-29 2005-10-29 Pumpe, insbesondere dickstoffpumpe

Country Status (9)

Country Link
US (1) US8192183B2 (ko)
EP (1) EP1831570B9 (ko)
JP (1) JP5076218B2 (ko)
KR (1) KR101190336B1 (ko)
CN (1) CN101107447B (ko)
CA (1) CA2593673C (ko)
DE (1) DE102004052928B4 (ko)
EA (1) EA010914B1 (ko)
WO (1) WO2006048212A2 (ko)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012020326A1 (de) 2012-10-17 2014-04-17 Herbert Jung Rotationskolben-Verdrängermaschine
CN106014971B (zh) * 2015-12-23 2018-04-20 山东大学 一种大流量偏心回转注浆泵及其使用方法
CN106014974B (zh) * 2015-12-23 2018-05-15 山东大学 一种双缸偏心回转泵

Family Cites Families (27)

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DE1173746B (de) * 1960-06-30 1964-07-09 Goetzewerke Radialdichtung fuer Rotationskolbenmaschinen
DE1144051B (de) * 1960-12-09 1963-02-21 Daimler Benz Ag Rotationskolben-Brennkraftmaschine in Trochoidenbauart
DE1194636B (de) * 1962-03-24 1965-06-10 Beteiligungs & Patentverw Gmbh Kreiskolbenmaschine
US3112868A (en) * 1962-06-11 1963-12-03 Marcus W Hagen Fluid seal for rotor
DE1187080B (de) * 1962-09-10 1965-02-11 Goetzewerke Radialdichtung fuer Rotationskolbenmaschinen
DE1175505B (de) * 1962-09-29 1964-08-06 Nsu Motorenwerke Ag Axialdichtung fuer eine Rotationskolbenmaschine
DE1187854B (de) * 1962-10-13 1965-02-25 Nsu Motorenwerke Ag Kreiskolbenmaschine, insbesondere -Brennkraftmaschine in Trochoidenbauart
BE790672A (fr) * 1971-10-29 1973-04-27 Copeland Corp Compresseur a chambres rotatives
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JPS5468208U (ko) * 1977-10-25 1979-05-15
JPS5866194U (ja) * 1981-10-30 1983-05-06 小倉クラツチ株式会社 バンケル形ロ−タリコンプレツサのアペツクスシ−ル
US4551073A (en) * 1982-05-12 1985-11-05 Walter Schwab Pump for liquid and gaseous fluids, especially blood
DE3426029A1 (de) * 1984-07-14 1986-01-23 Hugo Vogelsang Faß- und Maschinenbau GmbH, 4572 Essen Foerdervorrichtung fuer inhomogene fluessigkeiten, insbesondere guelle
JPS6128783A (ja) * 1984-07-17 1986-02-08 Asahi Malleable Iron Co Ltd 回転ピストン形圧縮機
DE4337427A1 (de) * 1993-11-03 1994-08-11 Konstantin Dipl Ing Trifonov Statorgeometrie einer Rotations-Kolbenmaschine
JPH0842462A (ja) * 1994-07-27 1996-02-13 Sato Shinku Kikai Kogyo Kk 回転ポンプ
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JP2003328970A (ja) * 2002-05-09 2003-11-19 Advics:Kk 真空ポンプ

Also Published As

Publication number Publication date
CN101107447A (zh) 2008-01-16
DE102004052928B4 (de) 2009-06-04
DE102004052928A1 (de) 2006-05-04
WO2006048212A2 (de) 2006-05-11
US20080274000A1 (en) 2008-11-06
EA200700962A1 (ru) 2007-10-26
CA2593673C (en) 2013-10-29
EA010914B1 (ru) 2008-12-30
CA2593673A1 (en) 2006-05-11
US8192183B2 (en) 2012-06-05
KR101190336B1 (ko) 2012-10-11
EP1831570A2 (de) 2007-09-12
JP2008518148A (ja) 2008-05-29
WO2006048212A3 (de) 2006-06-29
JP5076218B2 (ja) 2012-11-21
KR20070097424A (ko) 2007-10-04
CN101107447B (zh) 2010-06-02
EP1831570B1 (de) 2013-08-21

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