US3463092A - Hose pump - Google Patents

Hose pump Download PDF

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Publication number
US3463092A
US3463092A US657381A US3463092DA US3463092A US 3463092 A US3463092 A US 3463092A US 657381 A US657381 A US 657381A US 3463092D A US3463092D A US 3463092DA US 3463092 A US3463092 A US 3463092A
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United States
Prior art keywords
rollers
hose
pump
rotatable member
disc
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Expired - Lifetime
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US657381A
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English (en)
Inventor
Sven Fredrik Erhard Meyer
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Biotec AB
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Biotec AB
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    • 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
    • F04B43/1215—Machines, pumps, or pumping installations having flexible working members having peristaltic action having no backing plate (deforming of the tube only by rollers)
    • 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 rollers form relatively sharp bends in the hose, thereby forming closed cells within the hose, which cells are moved along the hose by the rotation of the rotatable member.
  • the rollers are adjustable radially on the rotatable member to change the length of the cells and thereby the liquid output of the pump at an unchanged rotational speed of the rotatable member.
  • the invention further comprises mechanical means for the adjustment of the rollers on the rotatable member and for compensating for the variations of the length of the hose engaged by the rollers.
  • This invention refers to a hose pump, especially for medical use.
  • the invention has the purpose to eliminate this difficulty and to provide a device permitting a variation of the output of the pump without changing the number of revolutions of the rotatable member.
  • the invention thus concerns a hose pump with a flexible and elastic hose placed under tension around a number of rollers rotatably mounted on a rotatable member and is characterized in that the rollers are adjustable on the rotatable member for simultaneously changing their radial distance from the axis of rotation of the rotatable member.
  • the output will be adjustable from zero upwards.
  • the radial adjustment of the rollers on the rotatable member can be obtained in different ways, e.g.
  • FIG. 1 shows a longitudinal section through the rotatable member of a hose pump according to a first embodiment of the invention.
  • FIGS. 2 and 3 are axial projections of this embodiment at different adjustments of the rollers.
  • FIG. 4 shows an axial section through a second embodiment of the invention.
  • FIGS. 5 and 6 are axial views of the same embodiment in two different functional positions.
  • FIG. 7 shows a section through a third embodiment of the invention.
  • FIGS. 8 and 9 are axial views of the same embodiment in two different functional positions.
  • FIG. 10 is a side view of a fourth embodiment of a hose pump according to the invention.
  • FIG. 11 is an axial end view of the same embodiment.
  • FIG. 12 shows a longitudinal section and FIG. 13 a cross. section of this fourth embodiment in one functional position.
  • FIG. 14 shows a longitudinal section and FIG. 15 a cross section of this fourth embodiment in another functional position.
  • FIG. 16 is an axial view of a fifth embodiment shown in axial view in one functional position in FIG. 17 and in another functional position in FIG. 18.
  • FIG. 19 shows in a plan view and FIG. 20 in side elevation a sixth embodiment of the invention formed as a differential pump.
  • FIG. 21 shows a plan view and FIG. 22 a side view of a seventh embodiment of the invention, even this formed as a differential pump.
  • FIG. 23 shows a vertical axial section through a device for compensating for the pressure pulsations on the outlet side of the pump.
  • the pump consists of a circular disc 1, which is fixedly mounted on the output shaft 2 of a motor (not illustrated) with highly reduced speed.
  • a number of gear wheels 3 in circular arrangement.
  • These gear wheels mesh with a central gear wheel 4 rotatably mounted on the shaft 2 and connected by means of a hub 5 with a covering plate '6 of preferably transparent material permitting the surveyance of the function of the pump.
  • a roller 7 On each gear wheel 3, between this and the covering plate 6, is pivotally mounted a roller 7.
  • the cover plate 6 bears near its periphery an axially extending, screw-threaded pin 9, extending through an arched slot 10 in the outer plate 8. 0n the periphery of one of the plates 6 and 8, e.g. of the cover plate 6, there is an index mark cooperating with a scale 11 along the periphery of the other plate e.g. plate 8.
  • the outer gear wheels which form planet wheels in the planet gear mechanism formed by the gears 3 and 4, in which gear 4 is the sun wheel are so mounted, that all the rollers 7 have the same angular position relative to the radius passing through the axis of the respective planet wheel 3 and the central axis 2.
  • the smaller rollers 13 shown besides the rollers 7 on each planet wheel 3 have an arrangement and a purpose to be described later on.
  • a hose which from a connection for the pump is placed under tension between the disc 1 and the plate 6 over the outsides of the rollers 7 and back to a second connection preferably near the first one, will normally be bent over the rollers 7 in such manner, that it is flattened at its bends over the rollers but between the rollers resumes its normal cross sectional shape, whereby separate pumping cells are formed within the hose according to the principles known for all kinds of hose pumps. If the nut 12 is so loosened and the plates 6 and 8 are rotated relative to each other, the sun wheel 4 is turned relative to the disc 1 in a corresponding manner, whereby the planet Wheels 3 are rotated and the positions of the rollers 7 relative to the disc 1 are changed. In this manner the rollers can be adjusted to different radial distances from the shaft 2, which changes the size of the cells enclosed in the hose between the rollers.
  • the small rollers 13 are mounted on the planet wheels 3 in such positions, that upon adjustment of the planet wheels 3 with the rollers 7 at a small radial distance from the shaft 2 they add themselves to the supporting surface for the hose to form a practically continuous, arcuate supporting surface (FIG. 2), which does not form distinct and separate bends of the hose and thereby not either distinct pumping cells in the hose.
  • FIG. 2 the liquid output of the pump is equal to zero.
  • the largest liquid output is obtained when the planet wheels 3 are turned with the rollers 7 past the position illustrated in FIG. 3 to a position radially outwards of the axis of the respective planet Wheel, where the space between consecutive rollers is the greatest possible.
  • the intermediate supporting rollers 13 are moved inwards and thus out of cooperation with the hose.
  • FIGS. 4-6 A device herefore is shown in FIGS. 4-6, which comprises a slide 16 displaceably guided towards and away from the shaft and supporting the connections 17 for the pump hose 15. This slide is under the action of a spring 18, which is tensioned between a pin 20 on the frame 19 of the pump and a pin 21 mounted on the slide 16 and keeps the hose under the desired tension.
  • a band a thin line can be passed over the rollers 7 besides the hose, preferably in separate guide grooves in said rollers. It is also possible, especially if the changes of liquid output of the pump occur at large time intervals,
  • a further modification for the adjustment of the tension of the hose 15 is to provide the slide with a tongue extending under the disc 1 and the gear wheels 3 and 4 to the vertical plane passing through the rollers 7, where the tongue has a projection, which is adjustable to such a distance from the shaft, that the projection is just out of the path of motion of the bends of the hose formed by the rollers 7. In FIG. 4 this alternative is shown in mixed lines.
  • FIGS. 4 to 6 differs from that illustrated in FIGS. 1 to 3 in a further respect.
  • a little gear wheel 24 operable e.g. by a screw driver which meshed with one of the planet wheels 3 and which can be secured by a stop screw 25.
  • the little gear wheel can instead be replaced by selfiocking worm screw meshing with one of the planet wheels.
  • This embodiment is illustrated with one of the planet wheels 3 provided with a scale cooperating with an index 26 on the disc 1.
  • the means for radially adjusting the space between the rollers 7 and the shaft 2 consists of two parallel discs 27 fixedly mounted on the shaft 2 and having a number of spiral grooves 28 corresponding to the number of rollers on their sides facing each other.
  • Shaft pins 29 for the rollers 7 have their ends guided in the spiral grooves 28.
  • rotatable guide discs 30 In contact with the inner sides of the discs 27 there are rotatable guide discs 30, which are fixedly connected with each other by means of a tubular hub 31.
  • the guide discs extend a little distance outside the periphery of the discs 27 and cover the edges thereof by a thickened border portion 32.
  • the guide discs have radial slots 33 in a number corresponding to the number of rollers 7.
  • the shaft pins 29 of the rollers 7 extend through the slots 33 into the guide grooves 28.
  • the shaft pins 29 and thereby also the rollers are moved along the spiral grooves 28 inwards or outwards to the desired position.
  • One of the thickened border portions 32 has preferably a stop screw 34, by which it can be secured in its position relative to the adjacent disc 27.
  • An index 35 on the outside of one of the discs 27 indicates the rotational position of the guide discs 30 on a scale 35a provided on the outside of the adjacent thickened border portion 32.
  • FIG. 8 shows the rollers 7 and their shaft pins 29 in their radially innermost position.
  • Axial pins 36 bridging over the space between the guide discs 30 are fixedly mounted on the guide discs along a circle at a radial distance from the shaft 2 corresponding to the radial distance of the outer periphery of the rollers 7 when these are in their innermost positions.
  • the rollers 7 and the pins 36 form together a practically continuous, annular support for the hose, which thereby is not subjected to the sharp bends necessary for the forming of pump cells within the hose.
  • the pins 36 thus permit a reduction of the liquid output of the pump to zero.
  • the rollers 7 are moved radially outwards by rotating the guide discs 30 relative to the discs 27, the hose looses its support on the pins 36 and forms closed pump cell between the rollers 7. Even in this embodiment it is possible to obtain a compensation for the tensioning of the hose e.g. by means of the device described in connection with FIGS. 4-6 for the same purpose.
  • rollers 7 are replaced by balls 37, which are radially movable between grooves 38 on the sides facing each other of discs 39 and 40, which by means of a tubular hub 41 are fixedly connected with the shaft 2 and form the rotatable member.
  • the hub sleeve 41 extends outside one of the discs 40 and has an outer helical groove on which is screwed a nut 42 having a conical tapered end projecting into the space between the discs 39 and 40.
  • a counter nut 43 is screwed onto the end of the hub sleeve 41.
  • the pump hose 44 extends from a point above the discs around the balls 37, which are situated in the lower part of the cage formed by the discs 39, 40 and the grooves 38, and keeps the balls pressed radially inwards against the tapered end of the nut 42.
  • the upper balls which are not maintained by the hose (see FIGS. 13 and 15) are kept in contact with the nut 42 by their own weight.
  • the discs 39, 40 are between the grooves 38 connected with each other by bridge portions 45, the outwards turned faces of which are in a common cylindric surface, which in the innermost position of the balls shown in FIG. 15 has its inside on a tangent to the balls.
  • the bridges 45 form thus together with the balls a sufficiently uniformly bent supporting surface for the hose to prevent the formation of pumping cells therein.
  • the outer ends of the grooves are narrowed by abutments formed by wires 46 placed into peripheral grooves in the outer edges of the discs.
  • An index member 47 mounted on the outside of the disc 40 indicates the screwing position 42 of the nut 42 and thereby the radial position of the balls on a scale 48 marked on the end face of the nut. Since the nut can be screwed in or out several revolutions, it is on the outside provided with a helical groove 49, which cooperates with an index member 47 longitudinally displaceable on a pin, thus giving a raw indication of the screwing position of the nut by reading the spire of groove 49 engaged by the index member 47.
  • the counter nut 43 is loosened and after the adjustment has been performed, it is retensioned.
  • the grooves, the nut and the hose the lower part of the device is preferably emerged in an oil bath 50.
  • FIGS. 16 to 18 An embodiment, which is based on the same principles but which permits larger radial movements of the balls 37 is shown in FIGS. 16 to 18.
  • two discs 51 are provided with a number of radial slots 52 of such width, that they form guides for the balls 53 placed between such slots.
  • a nut member 55 screwed onto a screw threaded portion of the shaft 2 has radial wings 56 capable of entering the slots 52 and of projecting through them more or less by screwing the nut 55 on the threaded portion 54.
  • the ends of the wings 56 extending through the slots 52 are inclined symmetrically towards the shaft 2, so that the balls are moved outwards by displacing the wings further in through the slots.
  • FIGS. 19 to 21 is based on the same principles as the embodiments according to the embodiments shown in FIGS. 1 to 6, i.e. on the principles of rollers mounted on planet wheels which can be rotated relative to a disc supporting said wheels for changing the liquid output of the pump.
  • This pump according to FIGS. 19 to 21, however, is formed as a differential pump.
  • rollers are so arranged on the planet wheels, that when the rollers 57 all are positioned on their largest possible radial distance from the shaft 2, the other rollers 58 are at their shortest possible radial distance from the shaft 2, as shown in FIG. 19.
  • Both ends of the hose 60 are connected to a common inlet 61 and runs, counted from one of the end connections, first over the rollers 57 situated in one plane, thereafter over a return disc 62 and then over the three other rollers 58 situated in the other plane back to the inlet connection 19.
  • a hose connection to an outlet 63 In one of the parts of the hose 60 leading to the return disc 62 there is a hose connection to an outlet 63.
  • the three rollers 57 situated in one plane at a large radial distance from the axis of rotation of the disc 64 form a pump unit feeding a relatively large quantity of liquid from the inlet 61 in the direction of arrows 66 to the outlet 63.
  • the three other rollers situated in the other plane form a second pump unit which depending on the little radial distance from the axis of rotation feeds a relatively small quantity of liquid from the outlet 63 in the direction of arrows 67 towards the inlet 61.
  • the liquid output at the outlet 63 is then the difference between the quantities fed by each of the pump units in the direction of arrows 66, 67.
  • the liquid output is thus at a maximum when the rollers 57 are in their outmost radial positions and the rollers 58 consequently in the innermost radial positions.
  • the hose runs easily over the disc 62 without being squeezed and flattened against it.
  • the portion of the hose running over the disc 62 is surrounded by an enclosure which is flexible but radially stiffer than the hose, e.g. a sleeve 68 formed by a helical spring.
  • the change of the output quantities of the two pump units cannot be driven farther than to th same value where the differential quantity fed out at 63 is equal to zero because otherwise, since the rollers 57 and 58 are mounted on the same side of the disc 64, the shafts of the rollers 58 situated at a greater distance from the disc 64 would engage the hose part of the other pump unit.
  • FIGS. 21 and 22 show a differential pump in which the feeding quantities of the separate pump units can be adjusted past the point at which they are equal, so that the dilferential quantity fed out at the outlet can be either positive or negative, i.e. the pump can feed the liquid in both directions.
  • the planet wheels 70 are rotatably mounted on a disc 71 which is fixedly mounted on the rotatable driving shaft 2.
  • the planet wheels 70 are, as stated before, coupled to each other by a sun wheel 72.
  • the planet wheels are rotated by means of a gear wheel meshing with the planet wheel 70 and operable in any known manner, e.g. as previously described in connection with wheel 24 in FIGS. 4 and 6.
  • Each planet wheel 70 has two shaft pins placed at diametrically opposed points of the wheel, of which pins one 74 extends outwards away from the disc 71 and the other 75 projects through an arcuate slot 76 in the disc to the opposite side thereof.
  • Rollers 77 and 78 respectively are mounted onto the ends of the shaft pins 74 and 75.
  • the two hose loops 79 and 80 are passed over the rollers 77 and 78 and are now entirely independent of each other.
  • each of the hose loops 82 and 83 is connected to a common outlet 90, while the connections for the other ends of the loops are not shown. These other ends can, as in the embodiment shown in FIGS. 19 and be connected to a common inlet 61.
  • outlet and inlet are strictly correct only for the functional position of the apparatus elements shown in FIGS. 21 and 22. In other functional positions the direction of flow of liquid can be changed and outlets become inlets and vice versa.
  • FIG. 23 shows a simple device for compensating for these pressure pulsations.
  • the driving shaft 2 on which the pump elements are mounted, though not shown in this figure, is driven through a speed reducing gear 91, 92 with a speed ratio corresponding to the number of rollers cooperating with one hose loop.
  • a speed reducing gear 91, 92 On the shaft 93 or the smaller of the cooperating gear wheels, i.e. the driving gear 92, is fixedly mounted a disc 94 with a radial groove 95. This groove is engaged by a pin 96 excentrically mounted on another disc 97 itself mounted on the motor shaft 98 or on the output shaft of a gear mechanism driven by the motor 99.
  • the motor shaft 98 is adjustable sideways for adjusting the shafts 93 and 98 to a certain desired excentricity.
  • this device it is possible to impart to the disc 94 and the shaft 93 and thereby to the gear wheel 92 a speed which is accelerated and decelerated once during each revolution.
  • the magnitude of these speed variations is adjustable by displacement of the shafts 93 and 98 relatively to each other.
  • the motor is adjustable sideways in guide slots 100 in the frame 101 and securable in the adjusted position by screws 102.
  • the driving shaft 2 is subjected to speed variations according to the rhythm of the passages of the rollers past a determined point. The device is so adjusted, that the shaft 2 receives a speed acceleration each time a roller leaves the hose loop, whereby the pressure decreasing impulse is compensated by an increased feeding speed of the pump.
  • the balancing of the speed increase in relation to the pressure decreasing pulse can be adjusted by displacement of the shaft 98 relative to the shaft 93.
  • a differential pump can also be provided with the ball system illustrated in FIGS. 10 to 15 or FIGS. 16 to 18.
  • the hose parts of the differential pump are then passed over two rotatable members mounted on the same shaft, wherein the balls are displaced in opposite direction by oppositely inclined oblique guide surfaces on a common nut member.
  • the rollers on one side can be rotatable about shafts fixedly mounted on the rotatable member, so that only the rollers cooperating with the hose loop are adjustable to different radial distance from the axis of the rotatable member.
  • a hose pump comprising a flexible elastic hose laid under tension around a number of rollers rotatably mounted on a rotatable member, means for simultaneously changing the radial distance of the rollers from the axis of the rotatable member and means to maintain the tension of the hose approximately unchanged in all possible radial positions of the rollers.
  • rollers are mounted each rotatably and eccentrically on one of a number of planet wheels mounted on the rotatable member and simultaneously rotatable thereon by means of a sun wheel meshing with all the planet wheels for changing the radial distance of the rollers from the axis of the rotatable member and means to maintain the tension of the hose approximately unchanged in all possible radial positions of the rollers.
  • a hose pump as claimed in claim 2 in which two operating discs are mounted for rotation relative to each other in front of the rollers and connected one to the rotatable member and the other to the sun wheel.
  • a hose pump as claimed in claim 2 in which an operating member rotatably mounted on the rotatable member meshes with one of the planet wheels and is securable in the adjusted position.
  • a hose pump as claimed in claim 2 in which the rollers are mounted outside the periphery of the planet wheels on arms fixedly mounted on said planet wheels.
  • a hose pump comprising a flexible elastic hose laid under tension around a number of rollers rotatably mounted on a rotatable member, means for simultaneously changing the radial distance of the rollers from the axis of the rotatable member in which the shafts of the rollers are displaceably guided in radial grooves in one portion of the rotatable member, and in spiral grooves in another portion of the rotatable member, both portions of said rotatable member being rotatable relative to each other for the radial adjustment of the rollers, and means to maintain the tension of the hose approximately unchanged in all possible radial positions of the rollers.
  • rollers are balls, radially guided in grooves in the face to face sides of two discs forming together the rotatable member and radially inwardly supported by inclined surfaces of a member axially adjustable relative to the rotatable member.
  • a hose pump as claimed in claim 7 in which the inclined surfaces are formed by the conically tapering end of a nut axially engaging an axial screw thread on a portion of the rotatable member.
  • a hose pump as claimed in claim 7 in which the inclined surfaces are formed by the chamfered end edges of radial wings on the axially adjustable member extending in radial slots in discs, in which the balls are radially guided.
  • a hose pump as claimed in claim 13 in which the slide is spring-actuated in the direction of tensioning the hose and is connected to a flexible band laid around the rollers together with the hose to limit the tensioning of the hose.
  • a hoes pump as claimed in claim 18 in which the rotatable member is driven through a gear mechanism with a gear ratio corresponding to the number of rollers cooperating with one hose part and in which the gear mechanism itself is driven by an excentric pin engaging a radial groove in a driving member adjustable relative to the axis of rotation of the excentric pin.

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US657381A 1966-08-01 1967-07-31 Hose pump Expired - Lifetime US3463092A (en)

Applications Claiming Priority (1)

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SE10439/66A SE317466B (enrdf_load_stackoverflow) 1966-08-01 1966-08-01

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US3463092A true US3463092A (en) 1969-08-26

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US657381A Expired - Lifetime US3463092A (en) 1966-08-01 1967-07-31 Hose pump

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Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3737251A (en) * 1971-02-08 1973-06-05 Alphamedics Mfg Cop Peristaltic pump
US3816035A (en) * 1972-10-24 1974-06-11 E Malbec Peristaltic pump
US4132509A (en) * 1976-04-30 1979-01-02 Motan Gesellschaft Mit Beschrankter Haftung Peristaltic pump with means to vary relative pumping volume between tubes
US4205948A (en) * 1977-02-10 1980-06-03 Jones Allan R Peristaltic pump
US4548553A (en) * 1984-09-24 1985-10-22 Ferster Reuben I Peristaltic pump structure
DE3943430A1 (de) * 1989-05-17 1991-04-04 Ismatec S A Rotations-schlauchpumpe
US5193750A (en) * 1991-03-22 1993-03-16 Ransburg Corporation Peristaltic voltage block roller actuator
US5256041A (en) * 1993-02-05 1993-10-26 Auto-Chlor System, Incorporated Peristaltic pump arrangement
US5586873A (en) * 1992-06-18 1996-12-24 Novak; Pavel Tube pump with retractable rollers
US5657000A (en) * 1995-06-02 1997-08-12 Cobe Laboratories, Inc. Peristaltic pump occlusion detector and adjuster
EP1319129A4 (en) * 2000-09-22 2004-08-04 Sorenson Technology Inc HOSE PUMP
US20050254879A1 (en) * 2002-06-13 2005-11-17 Gundersen Robert J Adjustable flow texture sprayer with peristaltic pump
EP1847711A1 (en) * 2006-03-20 2007-10-24 Bredel Hose Pumps B.V. Peristaltic pump, method for manufacturing a hose therefor, and hose for such a pump
US20080095645A1 (en) * 2006-10-20 2008-04-24 Johnson Electric S.A. Pump
EP2036585A1 (en) * 2007-09-13 2009-03-18 Ulrich GmbH & Co. KG Roller pump
CN102782325A (zh) * 2010-03-01 2012-11-14 乌尔里希有限及两合公司 蠕动泵
EP2708251A1 (en) * 2012-09-17 2014-03-19 Micrel Medical Devices S.A. Infusion rotary peristaltic pump
US20160327034A1 (en) * 2012-11-05 2016-11-10 Medtronic, Inc. Roller Pump with Dynamic Occlusion Adjustment
US20230279849A1 (en) * 2022-03-07 2023-09-07 Robert Hordis Peristaltic pump

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4417856A (en) * 1981-08-25 1983-11-29 Minissian Kevin G Peristaltic pump
FR2519381B1 (fr) * 1981-12-31 1986-09-26 Delasco Sa Pompe peristaltique
CN115182873A (zh) * 2022-07-27 2022-10-14 保定雷弗流体科技有限公司 一种挤压驱动结构和挤压式蠕动泵

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US1703361A (en) * 1924-12-24 1929-02-26 Pohl Ernst Pump
US2794400A (en) * 1956-05-28 1957-06-04 Jr Albert G Bodine Pump for fluid and semi-fluid materials
US2885967A (en) * 1956-12-18 1959-05-12 Santa Anita Mfg Corp Spiral type pump means
US3140666A (en) * 1962-06-11 1964-07-14 American Instr Co Inc Peristaltic pump
US3172367A (en) * 1963-01-08 1965-03-09 Technicon Instr Roller type pump

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Publication number Priority date Publication date Assignee Title
US419461A (en) * 1890-01-14 Surgical pump
US1703361A (en) * 1924-12-24 1929-02-26 Pohl Ernst Pump
US2794400A (en) * 1956-05-28 1957-06-04 Jr Albert G Bodine Pump for fluid and semi-fluid materials
US2885967A (en) * 1956-12-18 1959-05-12 Santa Anita Mfg Corp Spiral type pump means
US3140666A (en) * 1962-06-11 1964-07-14 American Instr Co Inc Peristaltic pump
US3172367A (en) * 1963-01-08 1965-03-09 Technicon Instr Roller type pump

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3737251A (en) * 1971-02-08 1973-06-05 Alphamedics Mfg Cop Peristaltic pump
US3816035A (en) * 1972-10-24 1974-06-11 E Malbec Peristaltic pump
US4132509A (en) * 1976-04-30 1979-01-02 Motan Gesellschaft Mit Beschrankter Haftung Peristaltic pump with means to vary relative pumping volume between tubes
US4205948A (en) * 1977-02-10 1980-06-03 Jones Allan R Peristaltic pump
US4548553A (en) * 1984-09-24 1985-10-22 Ferster Reuben I Peristaltic pump structure
DE3943430A1 (de) * 1989-05-17 1991-04-04 Ismatec S A Rotations-schlauchpumpe
US5193750A (en) * 1991-03-22 1993-03-16 Ransburg Corporation Peristaltic voltage block roller actuator
US5586873A (en) * 1992-06-18 1996-12-24 Novak; Pavel Tube pump with retractable rollers
US5256041A (en) * 1993-02-05 1993-10-26 Auto-Chlor System, Incorporated Peristaltic pump arrangement
US5657000A (en) * 1995-06-02 1997-08-12 Cobe Laboratories, Inc. Peristaltic pump occlusion detector and adjuster
EP1319129A4 (en) * 2000-09-22 2004-08-04 Sorenson Technology Inc HOSE PUMP
US20050254879A1 (en) * 2002-06-13 2005-11-17 Gundersen Robert J Adjustable flow texture sprayer with peristaltic pump
EP1847711A1 (en) * 2006-03-20 2007-10-24 Bredel Hose Pumps B.V. Peristaltic pump, method for manufacturing a hose therefor, and hose for such a pump
US20080095645A1 (en) * 2006-10-20 2008-04-24 Johnson Electric S.A. Pump
EP2036585A1 (en) * 2007-09-13 2009-03-18 Ulrich GmbH & Co. KG Roller pump
US20090074597A1 (en) * 2007-09-13 2009-03-19 Baecke Martin Roller pump
WO2009034192A3 (en) * 2007-09-13 2009-05-22 Ulrich Gmbh & Co Kg Roller pump
CN102782325A (zh) * 2010-03-01 2012-11-14 乌尔里希有限及两合公司 蠕动泵
US20130045121A1 (en) * 2010-03-01 2013-02-21 Ulrich Gmbh & Co. Kg Peristaltic Pump
EP2708251A1 (en) * 2012-09-17 2014-03-19 Micrel Medical Devices S.A. Infusion rotary peristaltic pump
US20160327034A1 (en) * 2012-11-05 2016-11-10 Medtronic, Inc. Roller Pump with Dynamic Occlusion Adjustment
US10012226B2 (en) * 2012-11-05 2018-07-03 Medtronic, Inc. Roller pump with dynamic occlusion adjustment
US20230279849A1 (en) * 2022-03-07 2023-09-07 Robert Hordis Peristaltic pump

Also Published As

Publication number Publication date
SE317466B (enrdf_load_stackoverflow) 1969-11-17
GB1167570A (en) 1969-10-15

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