EP0518290A1 - Pome à tuyau - Google Patents

Pome à tuyau Download PDF

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Publication number
EP0518290A1
EP0518290A1 EP92109741A EP92109741A EP0518290A1 EP 0518290 A1 EP0518290 A1 EP 0518290A1 EP 92109741 A EP92109741 A EP 92109741A EP 92109741 A EP92109741 A EP 92109741A EP 0518290 A1 EP0518290 A1 EP 0518290A1
Authority
EP
European Patent Office
Prior art keywords
pressure rollers
peristaltic pump
hose
pump according
delivery hose
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.)
Withdrawn
Application number
EP92109741A
Other languages
German (de)
English (en)
Inventor
Karl Ebner
Stefan Ebner
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.)
Ebner and Co KG Anlagen und Apparate
Original Assignee
Ebner and Co KG Anlagen und Apparate
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 Ebner and Co KG Anlagen und Apparate filed Critical Ebner and Co KG Anlagen und Apparate
Publication of EP0518290A1 publication Critical patent/EP0518290A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/12—Machines, pumps, or pumping installations having flexible working members having peristaltic action
    • F04B43/1253—Machines, pumps, or pumping installations having flexible working members having peristaltic action by using two or more rollers as squeezing elements, the rollers moving on an arc of a circle during squeezing

Definitions

  • the present invention relates to a peristaltic pump for conveying conveyed goods, in particular for conveying conveyed goods containing solid particles.
  • Peristaltic pumps of the generic type or displacement pumps are used for the gentle conveying of material to be conveyed, which may contain particles, in particular solid particles, such as crystals. Such material is to be conveyed with the greatest possible protection of the existing particles. Such a conveyance, in which the particles to be conveyed are not subjected to any mechanical stress that would impair their shape, is possible using peristaltic pumps or positive displacement pumps.
  • peristaltic pumps or positive displacement pumps essentially consist of a pump housing through which a delivery hose passes. This delivery hose is continuously compressed by the action of pressure rollers or pinch rollers, which are arranged to be driven and rotatable within the pump housing. These pressure rollers or squeeze rollers move over the hose surface of the delivery hose, compressing it continuously, with the pump housing serving as an abutment, so that the material to be delivered on the delivery side is moved very gradually and gently through the delivery hose from the upstream to the downstream side.
  • the pressure rollers or pinch rollers are inside the pump housing on a drivable bracket, rotatably mounted.
  • This holder moves the pressure rollers or pinch rollers continuously along this conveyor tube with a decreasing radial distance between the center of the roller or holder and the delivery tube.
  • the pressure rollers roll on the conveyor hose, the frictional connection or the friction between the conveyor hose and the rotatable pressure rollers causes the pressure rollers to rotate about their own axis.
  • This pushing together or squeezing the delivery hose has a very negative effect, in particular on the life of the delivery hoses used.
  • the hose material used wears out much more quickly when it is pushed together than when the pinch rolls or pressure rollers roll or run on the conveyor hose.
  • peristaltic pumps or displacement pumps Another disadvantage of these peristaltic pumps or displacement pumps is the relatively poor overall efficiency, in contrast to centrifugal pumps or propeller pumps, which can be estimated with an overall efficiency of 60 to 70%.
  • the overall efficiency of peristaltic pumps or positive displacement pumps is 20 to 30%. This relatively poor overall efficiency depends, among other things, on the hose material used for the hose pump. When using rubber hoses, in contrast to the use of plastic hoses, you can achieve a somewhat better efficiency.
  • rubber hoses used in peristaltic pumps have the disadvantage that only funds with relatively low temperatures can be pumped. In contrast, plastic hoses used in peristaltic pumps are significantly more temperature-independent.
  • the hose pump according to the invention for conveying material to be conveyed with any particles present has a delivery hose which passes through a pump housing in which pressure rollers are rotatably arranged on a holder which is connected to a drive shaft. According to the invention, these pressure rollers are rotated about their longitudinal axis by at least one separate drive means which is independent of the conveyor hose, during their movement along the surface of the conveyor hose triggered by their drivable holder.
  • the pressure rollers on the conveying hose are securely rolled off, starting from the pressing point on the conveying hose up to the narrowest pinch point and beyond.
  • the independent separate drive means can have a wide variety of embodiments.
  • the pressure rollers can also be driven via a friction drive or pinion; it can be a separate drive means for each pressure roller or a drive means driving all the pressure rollers simultaneously.
  • the individual pressure rollers are preferably driven by positive or non-positive engagement, for example in the manner of a drag roller.
  • the pressure rollers can preferably be equipped with a slip-reducing, friction-increasing coating. When working in an oily atmosphere, this friction-increasing coating could also not be sufficient to reduce the slip that occurs and to ensure optimal power transmission and thus a continuous rotary movement. Therefore, a power transmission is preferably carried out by a positive drive, for example by a pinion.
  • a uniform movement of the material to be conveyed can be achieved by continuously rotating the individual pressure rollers about their own axes, thereby ensuring that the individual pressure rollers roll continuously on the conveying hose while gradually compressing the same.
  • This continuous rotary movement about its own axis and the consequent rolling of the printing rollers is brought about by an independent, separate drive means which forcibly rotates the printing rollers about their longitudinal axes.
  • the movement of the pressure rollers from the inflow side to the pressure side of the peristaltic pump which is preferably a circular movement, is realized by the holder connected to the drive shaft.
  • the advantage of this independent and separate drive means of the printing rollers according to the invention is that a continuous rolling of the printing rollers is ensured even with increasing counterforce or with the material pressure counteracting the direction of movement of the printing rollers.
  • the pressure rollers overcome this critical point of the narrowest pinch point of the conveying hose, which represents the point with the greatest counterforce, by rotation about its own axis and are not pushed along the conveying hose, thereby preventing the latter from being pushed together or squeezed in its longitudinal direction and wearing to a considerable extent.
  • each of the pressure rollers is provided with a gearwheel, with all gearwheels engaging in a common guide ring.
  • the gearwheels are preferably rigidly or non-rotatably connected to the pressure rollers and have a larger diameter than the pressure rollers, so that the gearwheels protrude beyond the periphery of the pressure rollers.
  • the rotationally fixed connection of the gearwheels to the pressure rollers can take place in such a way that they are positively guided over the conveying hose or between the conveying hose and the holding plate.
  • the gear wheels are arranged at the ends of the pressure rollers opposite the holder. An arrangement of the same on the drive side would also be conceivable.
  • the gearwheels are attached in particular to the side of the pressure rollers which is opposite the holding plate of the pressure rollers.
  • the guide ring can also be equipped with a friction lining.
  • a friction lining Preferably and adapted to the particularly positive force transmission, it is designed as a ring gear with internal teeth.
  • the movement of the gear wheels on a circular path is brought about by the arrangement of the pressure rollers on a driven holding device.
  • the inner periphery of the guide ring is dimensioned such that it is a perfect fit, complementary to the circle defined by the gears.
  • the guide ring is preferably firmly connected to the pump housing.
  • the guide ring is fixedly arranged on the inner housing cover opposite the holder.
  • the gears of the pressure rollers and the guide ring have complementary teeth.
  • the guide ring or ring gear can also be fixedly connected to the pump housing opposite the holder.
  • the ring gear is fixed on the housing cover, in particular on the inside of the pump housing opposite the holder.
  • the pump housing can be designed in a variety of forms in a known manner, but preferably has a semicircular area, in particular in the squeeze area of the delivery hose that has the drive.
  • the arrangement of the drive means in this area, in particular the drive shaft does not take place in the center, but in particular in the direction of the semicircle, offset to the center of the circle defined by the semicircular shape.
  • the radial distance between the drive shaft and the upstream or downstream pump housing is in particular greater than the radial distance between the drive shaft and the point of the pump housing opposite the narrowest pinch point of the delivery hose.
  • a kind of intermediate wall can be drawn in between the delivery hose and the side wall of the pump housing, which acts as an abutment upstream of the housing side wall, so that the compressive force on the pump housing is minimized.
  • the hose pump of the present invention has a pump housing 7 with an approximately semicircular wall area and is passed through by a delivery hose 6.
  • the pump housing 7 has a rear housing cover 10 and a front housing cover 8, which are approximately semicircular in their lower region. These housing covers 8.10 are connected to one another by a side wall 9. This side wall 9 is also semicircular in the lower region and serves as an abutment when compressing the delivery hose.
  • a drivable holder 2 is arranged on a drive shaft 1.
  • Rotatable pressure rollers 3 are attached to the periphery of this holder 2, all of which have the same radial distance from the drive shaft 1.
  • the pressure rollers 3 have gears 4 connected to them in a rotationally fixed manner. These gearwheels 4 engage in a guide ring 5 which is fixedly connected to the front housing cover 8.
  • the arrangement of the drive shaft 1 in the pump housing 7 takes place in relation to the center of the circle which is formed when the said semicircle is "completed", but in such a way that the radial distance of the drive shaft 1 from the mutually parallel sections of the side wall 9 is equal to.
  • the radial distance to the end-curved or semicircular area (ie the lower area in FIG. 1) of the pump housing 7, on the other hand, is dimensioned smaller than the distance of the drive shaft 1 to the parallel opposite sections of the side walls 9.
  • the radially smallest distance from the drive shaft 1 is at the narrowest pinch point 11 of the delivery hose 6, diametrically opposite the pump housing side.
  • This arrangement of the drive shaft 1 and the holding device 2 arranged on it, on which in turn rotatable pressure rollers 3 are arranged, causes a circular movement of the pressure rollers 3 in the pump housing during rotation or during a rotary movement of the holding device 2 in such a way that they move the delivery hose 6 very gradually Squeeze around.
  • the pressure of the pressure rollers 3 on the conveyor hose 6 is at each other Parts of the conveyor hose lying opposite each other are the least.
  • the guide ring 5 or toothed ring fixedly arranged on the front housing cover 8 has a toothing which is complementary to the toothing of the toothed wheels 4 arranged on the pressure rollers 3.
  • the guide ring 5 is attached to the front housing cover in such a way and dimensioned in its inner periphery that the gear wheels 4 fastened on the pressure rollers 3 engage in it and rotate in its inner periphery.
  • An advantage of the embodiment of this peristaltic pump according to the invention is in particular that, on the one hand, heavy delivery hose wear is caused by frequent pushing together and squeezing the conveying hose 6 in the longitudinal direction is avoided, and on the other hand, the forced rotation of the pressure rollers 3 completely prevents them from slipping and rubbing on the conveying hose 6.
  • continuous rolling of the pressure rollers 3 over the conveying hose 6 enables a continuous movement of the conveyed goods from the inflow side to the outflow side of the peristaltic pump. Conveyed goods jams that occur due to a squeezing of the conveyor hose 6 due to non-rotating pressure rollers are excluded. Furthermore, a continuous conveying of the material to be conveyed can be guaranteed regardless of the conveying hose diameter.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP92109741A 1991-06-10 1992-06-10 Pome à tuyau Withdrawn EP0518290A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4119083 1991-06-10
DE19914119083 DE4119083A1 (de) 1991-06-10 1991-06-10 Schlauchpumpe

Publications (1)

Publication Number Publication Date
EP0518290A1 true EP0518290A1 (fr) 1992-12-16

Family

ID=6433620

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92109741A Withdrawn EP0518290A1 (fr) 1991-06-10 1992-06-10 Pome à tuyau

Country Status (2)

Country Link
EP (1) EP0518290A1 (fr)
DE (1) DE4119083A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0638322A1 (fr) * 1993-08-12 1995-02-15 Stöckert Instrumente GmbH Pompe à galets
CN102720668A (zh) * 2012-07-10 2012-10-10 天津市协达伟业电子有限公司 蠕动泵弹性软管保护方法及其保护装置
WO2014207466A1 (fr) * 2013-06-26 2014-12-31 Intelligent Energy Limited Ensemble pompe
CN108194334A (zh) * 2017-12-11 2018-06-22 东莞市松研智达工业设计有限公司 一种基于转轮轮胎可自转的蠕动泵

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4241760C1 (de) * 1992-12-11 1994-04-07 Westfalia Separator Ag Verfahren und Vorrichtung zur Dampfsterilisation des Schlauches einer Schlauchpumpe
DE102006025009A1 (de) * 2006-05-30 2007-12-20 Klämpfl, Franz Xaver, Dipl.-Ing. Schlauchpumpe
DE102013104242A1 (de) * 2013-04-26 2014-10-30 Emitec Gesellschaft Für Emissionstechnologie Mbh Vorrichtung zur dosierten Bereitstellung einer Flüssigkeit

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1568940A (en) * 1977-02-10 1980-06-11 Jones A R Peristaltic pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1568940A (en) * 1977-02-10 1980-06-11 Jones A R Peristaltic pump

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0638322A1 (fr) * 1993-08-12 1995-02-15 Stöckert Instrumente GmbH Pompe à galets
US5470211A (en) * 1993-08-12 1995-11-28 Stockert Instrumente Gmbh Roller pump
CN102720668A (zh) * 2012-07-10 2012-10-10 天津市协达伟业电子有限公司 蠕动泵弹性软管保护方法及其保护装置
CN102720668B (zh) * 2012-07-10 2015-03-11 天津市协达伟业电子有限公司 蠕动泵弹性软管保护方法及其保护装置
WO2014207466A1 (fr) * 2013-06-26 2014-12-31 Intelligent Energy Limited Ensemble pompe
US10227966B2 (en) 2013-06-26 2019-03-12 Intelligent Energy Limited Epicyclical fluid pump assembly
CN108194334A (zh) * 2017-12-11 2018-06-22 东莞市松研智达工业设计有限公司 一种基于转轮轮胎可自转的蠕动泵
CN108194334B (zh) * 2017-12-11 2020-06-23 温州焕宏纺织品有限公司 一种基于转轮轮胎可自转的蠕动泵

Also Published As

Publication number Publication date
DE4119083A1 (de) 1992-12-17

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