EP2153068B1 - Pompe à rouleaux à tuyau - Google Patents

Pompe à rouleaux à tuyau Download PDF

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Publication number
EP2153068B1
EP2153068B1 EP08749305.2A EP08749305A EP2153068B1 EP 2153068 B1 EP2153068 B1 EP 2153068B1 EP 08749305 A EP08749305 A EP 08749305A EP 2153068 B1 EP2153068 B1 EP 2153068B1
Authority
EP
European Patent Office
Prior art keywords
hose
rotor
accordance
roller pump
rollers
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.)
Active
Application number
EP08749305.2A
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German (de)
English (en)
Other versions
EP2153068A1 (fr
Inventor
Martin Lauer
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.)
Fresenius Medical Care Deutschland GmbH
Original Assignee
Fresenius Medical Care Deutschland GmbH
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Filing date
Publication date
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Publication of EP2153068A1 publication Critical patent/EP2153068A1/fr
Application granted granted Critical
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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
    • 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
    • F04B43/1276—Means for pushing the rollers against the tubular flexible member
    • 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
    • F04B43/0009—Special features
    • F04B43/0081—Special features systems, control, safety measures
    • 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
    • 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
    • F04B43/1292—Pumps specially adapted for several tubular flexible members
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/127—Braking parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/90—Braking
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the present invention relates to a hose reel pump with a stator, a rotor and a rotor drive, wherein the rotor comprises hose reels.
  • hose roller pumps In such hose roller pumps, a hose is inserted between the rotor and the hose roller track of the stator, which is pressed by the hose rollers against the hose roller track, so that liquid is pumped through the hose by the rotation of the rotor and thus the orbital movement of the hose rollers.
  • hose roller pumps find a variety of applications, especially in medical technology, and are used in dialysis, in particular hemodialysis or peritoneal dialysis, for pumping medical fluids such as dialysis fluid or blood.
  • the rotor consists of the rotationally driven hub body 4, are mounted on the usually two radially outwardly spring assisted rotating rockers 5, at the outer end of each a hose reel 9 is attached, which seeks to squeeze the hose 2 circumferentially against the hose roller track.
  • the hose roller track is part of the stationary part of the hose roller pump, which is often referred to as a pump bed or stator 1.
  • FIG. 1 explains the functional division of the tube roller track into three different segments.
  • the middle segment 17 (occlusion area) comprises about 180 degrees and represents a cylindrical surface. In this segment, the tube is completely occluded by the tube rolls.
  • the bilaterally mirror-inverted segments 18 (transition areas) extend over approximately 20 ... 30 degrees.
  • the radius of the roller track increases continuously, without the pump tube gets out of occlusion. Rather, the wings still follow the increase in radius until, towards the end of the transitional area, the point is reached at which the wings run up against stops which are arranged between the hub body and rocker and limit the further radial extension of the rockers and hose reels. Such stops are provided with each hose roller pump and not shown pictorially.
  • the radius of the roller track continues to increase while the rocker remains at the named stop until the pump hose has completely disengaged from the hose rollers before the start of the pump bed jaw area 20. In this mouth area, the pump tubing enters the pump bed and leaves it again.
  • the aforementioned swing stops have the additional task of preventing the hitting of the hose reels to the hose roller track with the pump hose removed.
  • the stops are set so that they allow a residual gap of about 1 mm between the hose roll and roller track, clearly less than twice the wall thickness of the occluded pump tube (occlusion condition).
  • the commercially available pumps have a plurality of hose guide wings 21, which point radially outward from the hub body like individual tines and terminate at a small frontal distance of approximately 1 to 3 mm in front of the hose roller track.
  • the hose guide wings are usually equipped with rotatable rollers to prevent friction and abrasion and play an important role in threading and unthreading the pump hose.
  • the hose guide vanes Since ordinary peristaltic pumps have the hose reels extended to the stops, the hose guide vanes must exert as much force on the hoses as is required to push it into the first approximately 1 mm gap between the hose reel and the roller track, with the rockers against the force to bring the springs to swing in until the pump tube is fully threaded and is overrun by both hose reels.
  • the elastomeric pump tube deforms by this application of force and tries to penetrate into the gap between the hose roller track and the end face of the hose guide vanes. In order to exclude this, the distance between the end face of the hose guide vanes and the hose roller track may only be about 2 ... 3 mm in the case of conventional peristaltic pumps.
  • the radius of curvature of the guide roller to the front side may not be much larger than 1 mm, because even so would create a sufficient condition for the pinching of the pump tubing during threading.
  • the pump tubing still binds when threading, which usually leads to hose damage and requires the replacement pump tubing.
  • the diagonal pushing in of the pump tubing into the Target position may occasionally be associated with damage to the pump tube, which are mostly due to the local overload when crossing the front edges of the hose reels. Another accident can occur if the pump hose is not inserted sufficiently deep by the operator, so that the end face of the nearest hose guide wing can absorb and damage the hose when approaching the hose roller track.
  • the mechanism just described still has the disadvantage that the pump tube is exposed to strong mechanical stresses during threading and unthreading and that small errors in the coordination of the geometric and force-related relationships between the machine and the pump tube segment can lead to disturbances.
  • the mechanism is not applicable because it imperatively requires a tilting of the pump tube segment at the beginning of the Ausfädelungsphase, which is not feasible, for example, in cassette systems with multiple pump tube segments.
  • Another disadvantage of the mechanism just described is the increased space requirements and in the increased manufacturing costs, as added to the original rotor mechanism, an additional electrically or pneumatically driven linear unit for lifting the pump tube segment from the pump bed.
  • an adjusting device is provided with an adjusting element, by means of which the position of the hose rolls in the radial direction is adjustable. This can be pulled through the adjustment for safe insertion of the hose between the rotor and hose roller track the hose rollers.
  • the pump tube is geometrically completely free when installing and removing. Also eliminates the problem of a segmented pump roller conveyor.
  • the object of the invention is therefore to provide a hose reel pump with an adjustment for the hose reels available, in which a complete exposure of the pump tube segment for the situation of installation and removal of the pump tubing for significantly improved ergonomics and safety when pump tubing provides, but only a minimum additional cost compared to peristaltic pumps without adjustment is to be achieved, and also a consistent reliable pumping function should be guaranteed compared to the best available prior art.
  • only the least possible additional space and components of the mechanics, electronics and software is required by the adjustment.
  • a hose reel pump with a stator, a rotor and a rotor drive, wherein the rotor comprises hose rollers whose position is adjustable via an adjusting device with an adjustment in the radial direction
  • a braking device wherein the radial position of the hose rollers by the interaction of Braking device and rotor drive is changeable.
  • the braking device inhibits the movement of the adjusting element, so that the adjusting element can be moved relative to the rotor by braking the adjusting element and by rotating the rotor in order to change the position of the rollers.
  • the already existing rotor drive can be used as the drive of the roller pull-in mechanism, which guarantees a cost-saving implementation of the present invention. Also, there is no difference in functionality to conventional peristaltic pumps in pumping operation, so that the proven high reliability in pumping operation is guaranteed even in the present invention. Essentially, only the adjusting element and the braking device are needed as additional elements, so that a largely space-same mechanism with only a few additional components and thus low cost is possible.
  • hose reel pump Due to the principle chosen hose reel pump according to the invention is particularly suitable for use with cassettes, in which a rigid cassette body z. B. in a dialysis machine is inserted and the promotion of the liquid flowing through the cassette (such as blood) to be made by a roller pump.
  • the tube to be inserted into the roller pump is usually designed as a protruding from the cassette loop.
  • the tube roller pump according to the invention is also suitable for such cassettes, which are equipped with more than one pump tubing.
  • the braking effect of the braking device can be triggered by actuating a brake actuator.
  • the adjusting movement can be initiated by selective actuation of the braking device.
  • the adjustment of the hose rollers is thus carried out comfortably by operating the brake device and rotor drive.
  • the brake actuator of the braking device is controlled by the control of the pump.
  • this also makes an automatic process for coupling and uncoupling the hose reels to the pump hose segment possible, so that there is the possibility of the pump bed cover while avoiding injury to the operator.
  • the adjusting element is rotatably mounted coaxially with the rotor.
  • such a rotatable mounting of the adjusting element in terms of design and cleanability has significant advantages.
  • the adjusting element forms an adjusting disc, which is rotatably mounted coaxially with the rotor.
  • the adjusting element according to the invention is rotatably mounted on the rotor.
  • This rotor and adjusting advantageously form a single assembly, which in turn allows a simple and space-saving design. Again, results from the rotatable storage again better cleanability of the device and a better design. In this case, it is possible to resort essentially to an already known rotor on which only the adjusting element has to be rotatably mounted.
  • the adjusting element rotates with the rotor during normal operation.
  • the storage of the adjustment is advantageously carried out directly and without ball bearings, so that a deliberately constructive bearing friction between adjustment and storage on the rotor ensures a rattle-free pumping operation. Only for the radial adjustment of the hose rollers then the adjusting element is braked relative to the rotor and so moved relative to the rotor, in particular twisted.
  • the adjusting element according to the invention is designed symmetrically and / or latched to the rotor, in particular in a position in which the hose rollers are extended.
  • a symmetrical structure of the adjusting element can be prevented that vibrations z. B. between the stator and rotor to unwanted rotations between adjusting and rotor or lead to an unwanted rattling of the adjustment, since a symmetrically constructed adjustment can not learn depending on position different frictional force transmission to the pivot bearing. Also by a Verrastiana the adjusting element with the rotor z. B.
  • the braking device inhibits the relative movement between the stator and the adjusting element.
  • the adjusting element is inhibited by the braking device in its movement relative to the stator, while the rotor is further rotated via the drive shaft relative to the stator and thus a relative movement between the rotor and the adjusting element is generated.
  • the rotor of the hose reel pump according to the invention comprises movable bearing elements on which the hose reels are rotatably mounted.
  • the adjusting element and / or the rotor on a guide which with one or more counter-elements for radial movement of the hose rollers cooperates. Due to the relative movement of the adjusting element and the rotor, the counter-elements move along the guide and generate a radial movement of the hose rollers.
  • the special shape of the guide can be optimally adapted to the required Verstellgeometrie.
  • the guide is arranged on the adjusting element, while the counter-elements are arranged on the rotor.
  • the counter-elements and / or the guide are firmly connected to the bearing elements for the hose reels.
  • the bearing elements of the hose reels are moved directly through the interaction of counter-elements and guide when the adjustment moves relative to the rotor, is advantageously rotated.
  • the counter-elements are arranged directly on the bearing elements for the hose reels, wherein they are further advantageously arranged directly on the projecting axle portions of the hose reels.
  • the counter elements can continue to advantageously consist of guide rollers.
  • the guide according to the invention forms a cam groove.
  • the counter-elements can engage and are moved radially in a movement of adjusting with respect to the rotor through the cam groove.
  • the guide according to the invention forms a circumferential ring guide.
  • a crash is effectively prevented by abutting a counter element against the ends of the guide, wherein the slope of the guide is advantageously just chosen so large that the rotor mechanism can not be overloaded even with unwanted rotational movements.
  • a guide designed as a ring guide allows retraction and extension of the rollers, without the direction of rotation of the rotor would have to be changed. Rather, alternate in such a ring guide areas in which the hose rollers are extended, with areas in which the hose rollers are retracted from. By simply turning further adjusting element relative to the rotor, an alternating extension and retraction of the hose rolls can thus be made possible.
  • the guide according to the invention consists of two or more identical segments, in a ring guide in particular of two or more consecutive identical segments. Due to the symmetrical construction, the bearing shaft of the cam disk is not loaded with transverse forces during the retraction and extension of the rollers, thus minimizing friction and allowing the design to be carried out at low forces.
  • the two or more identical segments are connected to each other.
  • the number of identical segments corresponds to the number of hose reels.
  • the guide has spirally inwardly extending portions which are associated with the respective counter-elements for movement of the hose reels. These spirally inwardly extending portions so pull the counter-elements in a relative movement of the adjusting element and the rotor inwards and ensure a retraction of the hose rollers.
  • the pitch of the spirally inwardly extending portions is designed so that the torque required to move the hose reels in the radial direction is substantially constant over the spiral portion.
  • the existing torque capacity of the rotor drive can be used in an optimized manner for pulling the rollers and the rotor drive requires no higher torque rating than a conventional rotor drive.
  • the spirally extending inwardly regions are connected by areas with opposite and advantageously stronger slope.
  • the hose reels can be extended by further rotation of the rotor again, the extension is done here anyway in the direction of the bias of the hose rollers on the springs. Also, a striking of the counter-elements is prevented at the ends of the guide.
  • the guide has areas without slope or with a Rastbeule in which rest the counter elements with retracted hose rollers.
  • the reaction between the guide and counter-elements is repealed and the springs for biasing the hose reels remain taut without moving the adjustment. Therefore, it is possible in the position of the retracted roles to disengage the brake device and turn off the rotor drive with retracted roles.
  • the rotor in the position 'rollers retracted' the pump tube safely and conveniently removed or used, the rotor remains in this position remains rotatable.
  • the rotor can be safely removed and replaced in this position, for example for cleaning or replacement purposes.
  • the guide according to the invention has areas in which a radial movement of the extended tube rollers is possible without the adjusting element being moved relative to the rotor.
  • these areas correspond to a position with extended hose rollers. In this position, the hose reels can perform their typical inward and outward swinging motion without the guide restricting them.
  • the adjusting element be adjusted by a certain angular range around this position with extended hose rollers, without the guide would move the hose rollers. This results in a certain play around the position of the adjustment element assumed in the normal pumping operation.
  • the brake actuator according to the invention is arranged on the stator. This results in a structurally simple adjusting element, which only little additional space, e.g. needed on the rotor. Also, the braking device is much easier to control, since all moving parts can be arranged on the stator and the adjustment must have no moving parts.
  • the braking device according to the invention has a brake pin, which cooperates with a corresponding recess. This results in a particularly simple braking device by positive locking, wherein z. B. only the brake pin must be inserted into the corresponding recess and so can set the adjustment on the stator.
  • the brake pin is arranged on the stator and the recess on the adjusting element. This results in a particularly simple construction.
  • the braking device alternatively has a movable brake shoe, which cooperates with a rigid brake counter-element. Also, this results in a simple braking device, which is based on traction.
  • the brake shoe is arranged on the stator and the brake counter-element on the adjusting element.
  • the adjustment can get along without moving parts and the movement of the brake shoe via the brake actuator from the stator made.
  • hose guide vanes are arranged on the rotor whose radial distance to the hose roller track of the stator is greater than 2 times, advantageously greater than 3 times the wall thickness of the hose used. This corresponds, e.g. a distance of more than 4mm, advantageously more than 6mm.
  • the general structure of the embodiment of the present invention is based on the above-described proven basic type, so that reference is made to the description of the prior art with respect to the basic structure and the pumping function of the present invention.
  • the present invention differs from the prior art only by the shorter and more rounded hose guide wing 21. It is in the basic elements of the rotor and the stator but otherwise identical to a tube roller pump according to the prior art.
  • the embodiment of the present invention therefore has the same advantageous properties of long-time proven hose reel pumps in pumping operation, but now by the adjustment shown in the following drawings a considerably simplified insertion and removal of the hose is possible.
  • the rotor of the embodiment of the hose reel pump according to the invention builds on the conventional rotor, and is only by adding a running as a cam 10 adjustment element, two identical cam rollers 11 as counter-elements for the cam groove 12 executed as a guide and a thrust bearing for coaxial storage of the cam 10th added on the rotor to a roller intake rotor with adjusting device for the hose reels.
  • a braking device 15 must be arranged, in the embodiment, a light and effectively sealable brake device was selected via a brake pin.
  • FIGS. 1 to 8 show simplified representations of the mechanism in the positions “rollers extended” or “rollers retracted” and in different rotational angular positions of the rotor.
  • the rotor assembly includes the hub body 4, the wings 5, the swingarms 6, the springs 7, the roller axles 8, the hose rollers 9, the cam 10, the cam rollers 11, the rotating shaft of the rotor drive 3, not shown, and the rotor-side points of attack 16 of Braking device 15 for blocking the cam 10th
  • the stator assembly includes the pumping bed 1 with pump bed mouth 20, the hose roller conveyor 17 ... 19, the bearing of the rotor shaft and the actuator of the braking device 15th
  • the rotor assembly differs from ordinary rotors by the additionally independent of the hub 4 rotatably mounted cam 10 and the elongated roller axles 8, at whose ends 9 rotatable cam rollers 11 are mounted independently of the hose rollers, which engage in the cam grooves 12 of the cam.
  • the cam rollers 11 may be supported on separate axles attached to the rockers 5.
  • the braking mechanism 15 To retract the hose rollers 9, it is activated by the braking mechanism 15 in that the stator-side brake actuator produces a frictional or positive connection between the fixed stator and the rotatably mounted cam disk (see FIG Fig. 7 +8).
  • the rotor drive 3 rotates the hub body 4 by approximately 120 degrees (depending on the design of the cam groove) until the cam rollers 11 have moved into the position 13 "rollers retracted” (see Fig. 3 +7).
  • the rockers 5, where the hose rollers 9 are mounted and hereby also the hose rollers 9 and the cam rollers 11 are always pressed radially outward. Therefore, the cam rollers 11 ride only on the radially outwardly facing raceways of the cam grooves 12.
  • the cam grooves 12 extend in the angular range of the roller feeder spirally inward and transform the rotational movement of the rotor in a retraction movement of the tube rollers.
  • the existing torque capacity of the rotor drive 3 is utilized in an optimized manner for pulling the rollers 9.
  • the rotor drive 3 does not require a higher torque rating than a conventional rotor drive.
  • the rotor With the position 13 "Rolled in”, the rotor reaches a position in which the pump tubing can be removed safely and conveniently, and in which the rotor can be safely removed and replaced (eg for cleaning or replacement purposes).
  • the brake actuators may optionally act axially (as shown in the figures) or radially (as in a shoe brake) on the cam.
  • the braking effect by pure positive engagement (as shown), by friction (as in a shoe brake) or by combined form and friction (as in a shaft-toothed torque limiter) come about.
  • the pin brake shown in pure positive engagement has the advantages of a very inexpensive implementation with high tolerances, a minimum energy requirement and an effective and hygienic sealing of the passage point of the brake pin through the stator bottom.
  • the cam-fitted rotor behaves like a conventional peristaltic pump rotor.
  • the cam 10 is disengaged from the brakes 15 and out of engagement with the cam rollers 11 and rotates with the rotor. So that it can not, for example by vibrations of the stator or rotor, to unwanted rotations between the cam 10 and hub body 4 may occur, which could lead to a rattling of the cam roller 11 to the flanks of the cam roller track, the cam is constructed strictly symmetrical, so they no Depending on the position may experience different Reibkraftübertragonne at its pivot point. The deliberately constructive bearing friction between the cam 10 and the rotor shaft supporting them ensures a rattle-free pumping operation.
  • a detent between the cam 10 and hub body 4 for example by a spring-loaded detent that conveys a detent position between the cam and hub body at 12 independently selected by the cam groove 12 a detent position Increased friction due to a wavy and resilient cam disk thrust washer.
  • the rotor transforms from the conventional rotor to the roller feed rotor by adding only three components: a cam 10, two identical cam rollers 11, and an axial bearing lock washer for the cam. This results in only additional costs for the adjustment mechanism in the amount of a few euros.
  • a complete geometric cropping of the pump tube segment after pulling the tube rollers 9 is possible, and thus a simple insertion and removing a simple pump tubing, a pre-fixed pump tubing (clip) or a pumped tubing cartridge.
  • the hose reel pump according to the invention is also suitable for use with cartridges which are equipped with more than one pump hose.
  • the tubular roller pump according to the invention has no different operation to conventional hose roller pumps in pumping operation, whereby a high proven reliability and a particularly low development risk is granted.
  • the pumptubes are largely straight after their extrusion and are brought by elastic bending in the mold, which allows them to insert into the pumping bed and put on the outside of the largely round tube roller track. Regardless of whether the pump tubing is bent during installation or whether it is already bent in the course of producing a prefixed pump tubing loop or when attached to cassettes, there is no round shape in the bending, but an approximately oval. If the pump tube length is designed so that the hose when pumping neither on the hub body 4 grinds nor is so long that it no longer fits into the pump bed, it creates an oval shape such that the largest diameter is slightly larger than the diameter of the hose roller conveyor.
  • the pump hose can be in a train and without the aid of a second hand in a circumferential annular gap, as realized by the roller feeder, insert on the side of the pump bed mouth without resistance to the required location in the pump bed, especially if it is supported by a clip or by a cassette. But on the side opposite the pump bed mouth side of the hose roller track but then the hose abuts against the insertion of the hose roller track because of the previously described larger oval diameter and does not always get into the depth position required for pumping due to friction. As a result, the complete installation must be done by hand assist or by the initially described automatic threading procedure with the roller-fitted hose guide blade 21.
  • a special feature is the fact that without removing the pump segment and with little control effort, the tube rollers 9 can be retracted and extended. Thus, especially in medical treatment devices new treatment methods are possible in which the switchable passage position can be used consciously for new procedural processes.
  • the tube rollers 9 can be pulled so far inward that the pump tube is completely geometrically released and can be removed with little resistance.
  • the installation is done by simply latching insertion of the pump tube segment with subsequent automatic threading in the full installation position.
  • the cam has two symmetrical cam groove areas, the beginning and end of which are connected in a preferred embodiment by a short piece of a groove with a greater pitch. Due to the symmetrical construction, the bearing shaft of the cam disk 10 is not loaded with transverse forces during the retraction and extension of the hose rollers 9, thus minimizing friction and allowing the design for low forces.
  • the connection of the two groove segments to a circumferential annular groove 12 creates an effective overload protection in case of disturbances in the control operations of the rotor rotation angle when the brake is applied. A crash by striking the cam roller 11 at the ends of a cam groove can not take place.
  • the slope of the two connecting grooves is just chosen so large that the rotor mechanism can not be overloaded even with unwanted rotational movements.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • External Artificial Organs (AREA)
  • Reciprocating Pumps (AREA)

Claims (25)

  1. Pompe à rouleaux à tuyau comprenant un stator (1), un rotor et un entraînement de rotor, le rotor comprenant des rouleaux à tuyau (9), dont la position peut être réglée dans la direction radiale par le biais d'un dispositif de réglage doté d'un élément de réglage (10),
    caractérisée en ce qu'un dispositif de freinage (15) est prévu, qui entrave le déplacement de l'élément de réglage (10), de telle sorte que l'élément de réglage (10) peut être déplacé par rapport au rotor par un freinage de l'élément de réglage (10) et par une rotation du rotor pour modifier la position radiale des rouleaux à tuyau (9).
  2. Pompe à rouleaux à tuyau selon la revendication 1, caractérisée en ce que l'effet de freinage du dispositif de freinage (15) peut être déclenché par l'actionnement d'un actionneur de frein.
  3. Pompe à rouleaux à tuyau selon la revendication 2, caractérisée en ce que l'actionneur de frein du dispositif de freinage (15) est commandé par la commande de la pompe.
  4. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que l'élément de réglage (10) est monté rotatif de manière coaxiale au rotor.
  5. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que l'élément de réglage (10) est monté rotatif sur le rotor.
  6. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que, en fonctionnement normal, l'élément de réglage (10) tourne avec le rotor.
  7. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que l'élément de réglage (10) est réalisé symétrique et/ou peut être encliqueté avec le rotor, en particulier dans une position dans laquelle les rouleaux à tuyau (9) sont déployés.
  8. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que le dispositif de freinage (15) entrave le déplacement relatif entre le stator (1) et l'élément de réglage (10).
  9. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que le rotor comprend des éléments de support (5) mobiles, sur lesquels les rouleaux à tuyau (9) sont montés rotatifs.
  10. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que l'élément de réglage (10) et/ou le rotor comportent un élément de guidage (12), qui coopère avec un ou plusieurs éléments antagonistes (11) pour le déplacement radial des rouleaux à tuyau (9).
  11. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que les éléments antagonistes (11) et/ou l'élément de guidage (12) sont reliés solidement à des éléments de support (5) pour les rouleaux à tuyau (9).
  12. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que l'élément de guidage (12) forme une rainure de came.
  13. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que l'élément de guidage (12) forme un élément de guidage annulaire périphérique.
  14. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que l'élément de guidage (12) est composé de deux ou de plusieurs segments identiques, en particulier de deux ou de plusieurs segments identiques successifs dans le cas d'un élément de guidage annulaire.
  15. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que l'élément de guidage (12) comporte des zones s'étendant vers l'intérieur en forme de spirale, qui sont associées aux éléments antagonistes (11) respectifs pour le déplacement des rouleaux à tuyau (9), caractérisée en ce que la pente des zones s'étendant vers l'intérieur en forme de spirale est conçue de manière avantageuse de telle sorte que le couple nécessaire pour le déplacement des rouleaux à tuyau (9) dans la direction radiale est sensiblement constant sur la zone en forme de spirale.
  16. Pompe à rouleaux à tuyau selon la revendication 15, caractérisée en ce que les zones s'étendant vers l'intérieur en forme de spirale sont reliées par des zones avec une pente inverse et de manière avantageuse plus forte.
  17. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que l'élément de guidage (12) comporte des zones (13) sans pente ou avec une bosse d'arrêt, dans lesquelles les éléments antagonistes (11) restent lorsque les rouleaux à tuyau (9) sont rétractés.
  18. Pompe à rouleaux à tuyau selon la revendication 10, caractérisée en ce que l'élément de guidage (12) comporte des zones (14), dans lesquelles un déplacement radial des rouleaux à tuyau (9) déployés est possible sans que l'élément de réglage (10) soit déplacé par rapport au rotor.
  19. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que l'actionneur de frein est disposé sur le stator (1).
  20. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que le dispositif de freinage (15) comporte une tige de freinage, qui coopère avec un évidement (16) correspondant.
  21. Pompe à rouleaux à tuyau selon la revendication 20, caractérisée en ce que la tige de freinage est disposée sur le stator (1) et l'évidement (16) sur l'élément de réglage (10).
  22. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que le dispositif de freinage (15) comporte une mâchoire de freinage mobile, qui coopère avec un élément antagoniste de freinage fixe.
  23. Pompe à rouleaux à tuyau selon la revendication 22, caractérisée en ce que la mâchoire de freinage est disposée sur le stator (1) et l'élément antagoniste de freinage sur l'élément de réglage (10).
  24. Pompe à rouleaux à tuyau selon l'une des revendications précédentes,
    caractérisée en ce que des ailettes de guidage de tuyau (21) sont disposées sur le rotor, dont l'écart radial par rapport au chemin des rouleaux à tuyau du stator (1) est supérieur au double, de manière avantageuse supérieur au triple, de l'épaisseur de paroi du tuyau utilisé.
  25. Pompe à rouleaux à tuyau selon la revendication 24, caractérisée en ce que les ailettes de guidage de tuyau (21) comportent des rouleaux de guidage de tuyau, dont le rayon d'arrondi vers le côté frontal extérieur est supérieur à 20 %, de manière avantageuse supérieur à 40 %, du diamètre extérieur du tuyau de pompe.
EP08749305.2A 2007-05-02 2008-05-02 Pompe à rouleaux à tuyau Active EP2153068B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007020573.4A DE102007020573B4 (de) 2007-05-02 2007-05-02 Schlauchrollenpumpe
PCT/EP2008/003564 WO2008135245A1 (fr) 2007-05-02 2008-05-02 Pompe à rouleaux à tuyau

Publications (2)

Publication Number Publication Date
EP2153068A1 EP2153068A1 (fr) 2010-02-17
EP2153068B1 true EP2153068B1 (fr) 2017-10-25

Family

ID=39637640

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08749305.2A Active EP2153068B1 (fr) 2007-05-02 2008-05-02 Pompe à rouleaux à tuyau

Country Status (12)

Country Link
US (1) US8568115B2 (fr)
EP (1) EP2153068B1 (fr)
JP (1) JP5681484B2 (fr)
KR (1) KR101477829B1 (fr)
CN (1) CN101784795B (fr)
AU (1) AU2008248920B2 (fr)
BR (1) BRPI0810967B1 (fr)
CA (1) CA2680136C (fr)
DE (1) DE102007020573B4 (fr)
EA (1) EA016307B1 (fr)
ES (1) ES2656863T3 (fr)
WO (1) WO2008135245A1 (fr)

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DE202021101635U1 (de) 2021-03-26 2021-05-31 Jobst Technologies Gmbh Mikropumpe nach dem peristaltischen Wirkungsprinzip

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DE202021101635U1 (de) 2021-03-26 2021-05-31 Jobst Technologies Gmbh Mikropumpe nach dem peristaltischen Wirkungsprinzip

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AU2008248920A1 (en) 2008-11-13
JP2010525226A (ja) 2010-07-22
EP2153068A1 (fr) 2010-02-17
CN101784795A (zh) 2010-07-21
DE102007020573B4 (de) 2014-12-04
US8568115B2 (en) 2013-10-29
US20100129247A1 (en) 2010-05-27
EA200901477A1 (ru) 2010-04-30
BRPI0810967A2 (pt) 2015-01-27
EA016307B1 (ru) 2012-04-30
CA2680136C (fr) 2015-10-27
WO2008135245A1 (fr) 2008-11-13
CA2680136A1 (fr) 2008-11-13
BRPI0810967B1 (pt) 2019-07-16
KR101477829B1 (ko) 2014-12-30
ES2656863T3 (es) 2018-02-28
AU2008248920B2 (en) 2013-09-19
WO2008135245A8 (fr) 2010-04-01
JP5681484B2 (ja) 2015-03-11
DE102007020573A1 (de) 2008-11-06
KR20100014531A (ko) 2010-02-10
CN101784795B (zh) 2013-05-22

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