EP0320963A2 - Pompe volumétrique pour fluides fonctionnant comme une pompe à pistons tournants - Google Patents

Pompe volumétrique pour fluides fonctionnant comme une pompe à pistons tournants Download PDF

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Publication number
EP0320963A2
EP0320963A2 EP88121098A EP88121098A EP0320963A2 EP 0320963 A2 EP0320963 A2 EP 0320963A2 EP 88121098 A EP88121098 A EP 88121098A EP 88121098 A EP88121098 A EP 88121098A EP 0320963 A2 EP0320963 A2 EP 0320963A2
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EP
European Patent Office
Prior art keywords
pump
masses
membrane
rotor
pump 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.)
Withdrawn
Application number
EP88121098A
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German (de)
English (en)
Other versions
EP0320963A3 (fr
Inventor
Renato Vicentini
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.)
Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0320963A2 publication Critical patent/EP0320963A2/fr
Publication of EP0320963A3 publication Critical patent/EP0320963A3/fr
Withdrawn legal-status Critical Current

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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
    • F04B43/1253—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
    • F04B43/12—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
    • F04B43/1269—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 the rotary axes of the rollers lying in a plane perpendicular to the rotary axis of the driving motor
    • 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
    • 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
    • F04B43/14—Machines, pumps, or pumping installations having flexible working members having peristaltic action having plate-like flexible members

Definitions

  • the invention relates to a volumetric pump acting in the manner of a rotary lobe pump for liquid or gaseous media, which in a housing with an inlet or outlet opening for the conveying medium has a motor-driven rotary lobe, which is rotatably mounted in the housing bore around its longitudinal axis and which, according to the older European patent application 8 611 3596.0 principle works.
  • the annular space 3 of FIGS. 1 and 2 of the drawing is divided with the aid of a plurality of partition walls or elements, the tightness for the fluid to be pumped being guaranteed, as is shown, for example, at 30 and 31 in FIG. 1.
  • These parts can, for example, be elementary duct arches which follow one another (cf. FIGS. 21 and 22).
  • Each bend is a pumping element because it is provided with an inlet and an outlet opening at the corresponding ends.
  • the various pumping elements which result from the subdivision of the intermediate space are actuated in succession by the same rotating masses which are moved by a single rotating part, for example a rotary piston or rotor.
  • the inlet and outlet openings of the respective pumping elements can be connected to one another in such a way that a parallel of elementary pumping elements is created in order to achieve a higher performance, or a parallel of some pump elements connected in series to one another to achieve one To achieve higher compression in several stages, these elements can be used independently of one another, all or in part also with different liquids and as desired, as suction or pressure devices or as a combination of such devices.
  • the pump according to the present invention retains all the positive features of the above-mentioned pump without, however, accepting the corresponding restrictions mentioned, because the pumping capacity is several times greater with the same dimensions and heat due to the compression is distributed in several zones of the pumps and in can be removed in a suitable manner by ribbing the pump body, ie providing it with ribs, or by switching on the heat exchanger between the compression stages.
  • the entire inner mechanical part can also be cooled in a suitable manner, the lubricant itself being brought into the outer exchanger using a sector of the pump. It follows from this that the construction of large machines, for example industrial compressors or vacuum pumps or mixed, simultaneously suction and pressure pumps, is possible.
  • Another feature of the present new pump is the possibility of working simultaneously and separately with different fluids, for example liquid and gaseous or only liquid or only gaseous media, but in this case of different types.
  • the pump according to the invention comprises practically all industrial applications which are not possible with the other devices today, e.g. With the current reciprocating compressors, it has advantages both in energy saving during dead times (this pump can in fact stop and start again every time the pressure in the storage tank has been reached, without having to disconnect the electrical supply network disturbing the engine's feeding, because it only requires torque after the working speed has been reached), as well as in the particular noiselessness, which can be attributed to the divided or fractional intake and the lack of vibrations with regard to the balanced, balanced configuration are.
  • the screw compressors are noiseless than the piston compressors, but they require separators at the outlet to separate the air from the oil, which the present pump does not require for the reasons described above.
  • the annular space is subdivided into several successive, for example arc-shaped chambers, that each of these chambers is provided at one end with a suction opening and at the other end with a discharge or outlet opening and an elementary pumping unit forms, and that the different pumping units resulting from the division of the chamber are actuated in succession by the same masses, provided in a suitable number, which are actuated by the same rotary piston.
  • the arrangement can be such that the pump body and the membrane are disc-shaped are and the annular chamber in the pump body, which may be subdivided to form several elementary pumping units, forms a ring concentric with it, that the axis of rotation of the rotary piston is formed at right angles to the plane of the pump body in which the diaphragm is fastened, and that the bearing axes for the masses are within the angle formed by the plane tangent to the pump body on the side to which the diaphragm is attached and the drive shaft.
  • rotary pistons or rotors can be mounted on an extension of the drive shaft, which is suitably guided at the two ends, which actuate a corresponding number of pumps with one or more pumping units, the rotary pistons or rotors and the annular chambers of the various pumps can be designed differently.
  • the membrane 4 must be made of a suitable elastomer that can stretch under the action of the masses 22.
  • the pressure of the fluid in the space 3, which communicates with the inlet opening, causes the membrane to swell, inflate, and beyond certain easily estimable pressure limits, the rotor will rub against it and damage it.
  • the axial expansion of the membrane stimulates its return to the rest position and thereby a considerable suction effect in the space 3, which communicates with the suction opening, which is why, by appropriately proportioning the depth of the space, the thickness and the characteristic features of the membrane or dimensioned, can easily realize vacuum pumps that are suitable for the lowest pressures that are close to absolute zero.
  • the annular space is obtained by appropriately shaping the membrane 4.
  • the pump body 1 does not contain the channel or space, its inner surface 5 is cylindrical.
  • the masses 6 are small cylinders or spheres, and their length or height 60 can be less than the distance between the inner surfaces of the rings 2, for example three times the thickness of the membrane 4.
  • the membrane 4 works up Pressure when the masses 6 act on them, which is why they can be realized with an elastomer that can be made of linen or textile material or simply of threads that are arranged axially and intersecting to prevent inflation due to the pressure of the fluid in the to prevent the cavity communicating with the suction opening or the corresponding intermediate space 3.
  • this solution is particularly suitable for compressors of any pressure value, although it is also suitable for vacuum pumps, but for pressures which are relatively less pronounced than in the solution according to FIGS. 1 and 2.
  • the channel has 5, for example, a trapezoidal cross-section and the shape corresponding to the masses 6, this arrangement being functionally equivalent or equivalent to the solution according to FIG. 2, over which it is advantageous if it is necessary to make the masses 6 lighter in order to accommodate the centrifugal force a suitable bore 600, which is coaxial to the cylinder, or if a rotor is used, which is shown in FIGS. 7 and 8.
  • 0 denotes the axis of rotation of the omitted rotor 01.
  • FIG. 3 and 4 0 denotes the axis of rotation of the omitted rotor 01.
  • 0 also denotes the axis of rotation of the partially shown rotor 01, which in turn passes through the masses 6 with the aid of the surface 011 Thrusts in rotation according to 0133. If one translates the shape of the space of Fig. 1 in Fig. 5, it can be seen that the rotor pushes the mass 6 in rotation with the aid of a thrust plane which is parallel to the centrifugal force 012 and perpendicular to the axis 014. With the shape of the rotor of FIG. 5, however, the thrust plane of the mass 6 becomes perpendicular to the axis 013.
  • the holes or bores 011 and 012 exactly envelop the circumferential profile of the masses 6, in order in this way to enable a very damped radial adjustment or sliding movement and to prevent possible hopping and impact movements of the masses even during the rotation.
  • FIG. 8 is a view taken along the line XX of Fig. 7. It partially shows a rotor 01 which pushes and pushes the mass 6 according to 0133 or pulls according to 0134 by means of an arm 013 which by means of a pin 0131 is articulated in a spoke 011 of the rotor itself.
  • the arm 013 can possibly be dampened in its movements with the help of the damper or the amortization device 0132. It carries the mass 6, which is formed, for example, from the pin 61, the bearings 62, the mounting rings, for example Seeger rings 63, and from the outer casing 64; this solution enables any kind of grazing friction to eliminate that is present in the configurations or configurations described above, in which the rotor 01 pushes and drives the masses 6 themselves. In Fig. 9, the direction of rotation 0133 or 0134 is unimportant, uninteresting.
  • the rotor 01, the masses 6 and possibly the membrane 4 are toothed, like the corresponding sun, satellite and inner wheels of an epicycloidal reduction gear.
  • a cage In order to hold the masses 6 in a predetermined position, a cage can be used, which consists of rings 0102 on both sides, which are connected to one another by means of 0104.
  • the advantage of such a system is less stress on the membrane 4 in the direction of rotation due to tearing, a type of sliding friction and the possibility of having a higher speed directly at the rotor 01 for driving the coaxial fan (FIG. 10).
  • the masses 6, instead of already pressing the membrane 4 against the pump body 1 in the rest position in such a way that the sealing of the fluid is achieved at the contact points, with a suitable choice of the tolerances of the pairing allow suitable leakage, which is then canceled by the centrifugal force, since the masses 6 can move radially in the guide grooves 0103 and slide there; 9 the subdivisions of the annular space 3 are not shown.
  • the cover 21 of the pump carries a bearing 22 in a suitable collar which is coaxial with the axis 0 and which serves to hold and support the shaft 81 of the fan.
  • the following parts are keyed onto the shaft 81: on the one hand, an element 82, which carries two or more pins, with corresponding bores cooperate in the rotor 01 to form the transmission connection, and on the other hand the impeller 8, which draws air through the opening 841 and presses it through the openings 842 onto the ribs 11 of the pump body 1, while cooling the latter.
  • the carrier 21 also acts as a cover for the pump and can form a single piece with the ring 2 or, which is more advantageous for maintenance, can be inserted into this ring in a detachable manner; ring 211, an O-ring, avoids loss of lubricant. 21 can finally be attached to the pump with the aid of screws or quick connections, which act on the pump body 1 or on the rings 2, which are not shown in the drawing.
  • 11 to 13 relate to the areas encircled in FIGS. 3 and 4, which represent suggestions for the fastening of the membrane 4, which are valid for each of the solutions shown in FIGS. 2 to 10.
  • 11 to 13 1 is the pump body in a partial sectional view, 2 the inner ring, against which the membrane is pressed. 11, the ring 2 has the shape 20 and possibly also the thread or a ribbing 201 in order to hold the membrane 4 even more firmly.
  • a complementary shape 10 is formed in the body 1, possibly a thread 101 can also be provided in the body 1.
  • the diaphragm 4 In the pumps in which the channel or space 5 is very deep, the diaphragm 4 is heavily stressed and, consequently, it must be blocked in a suitable manner without concentrating extraordinary loads along the circumference of the tension.
  • the blockage can be distributed, for example, in terms of its strength from the outside in and achieved by vigorously moving the membrane between 101 and 201 squeeze, then 90 ° or the like. bends according to the profile shown at 20 and 10, then compressed between the cylindrical walls 20 and 10 and lighter and weaker in the rest of the channel 5.
  • the membrane It is moreover expedient for the membrane to be reinforced by springs or fibers which are provided in the direction of the circumference in order to prevent it from being wrinkled or roughened, with corresponding wear on the side facing the channel.
  • the membrane 4 ends with the thickening 42, which engages compressed in the grooves or grooves 20 and 10 of the pump body 1 and the ring 2; this thickening can also have a polygonal or a circular cross section.
  • 11 and 12 are suitable for any channel shape, as suggested in FIGS. 2 to 4, which is why the possibly reinforcing linen or textile pieces 41 can be simple, circumferential springs or fibers that can be extend over the entire height of the membrane or only over a part of it, depending on the needs of the construction.
  • Fig. 13 represents a simpler alternative to blocking the membrane 4. If no special stresses are provided, the profile 20 can be formed or formed on the strip which forms the membrane when the pump is assembled.
  • Figure 14 illustrates a diaphragm of an elementary pump which has a very simple shape which can be made by thermoforming or thermoforming an elastomeric strip or by pressing.
  • 44 and 43 correspond to those in FIGS. 1 to 3 struck profiles.
  • 45 are bores which are provided on the fastening ends 46 for the passage of centering pins or connecting bolts which serve to connect the sectors which form the pump body 1.
  • the membrane according to FIG. 15 is intended for a machine with four pumping elements and, if a suitable production is provided, it is advantageous compared to that according to FIG. 14, the higher costs of the press mold being achieved by savings in the costs of the membrane in which Assembly of the pump and also during maintenance can be compensated.
  • the reference numerals are the same as those used in Fig. 14, the membrane is held at 42 and 47 according to that of Figs. 14 and 12.
  • the components are held together by the ring 12, they are placed on corresponding collars of the pump body 1 under the action of force, that is to say pressed on; however, the connection between the components of the pump can also either take place with screws which engage in the bores 45 (FIGS. 14 and 15) and with corresponding holes in the sectors of the pump body 1 or with a single drawn-on ring which is applied from the outside to the possible ribs 11 and the whole or part of the height of the pump body.
  • the upper part of the drawing shows a section through the projection 47 of FIG. 15 along a diametrical plane, while the lower part of the drawing relates to a middle plane between two projections 47.
  • the lubricant is designated by 9.
  • 91 and 92 are sectors or parts relating to the removal, re-introduction into the machine and the circuit of the lubricant 9 for the purpose of cooling this lubricant by means of a pumping element.
  • holes and corresponding connecting tubes are used, which are attached to the cover 21.
  • Fig. 17 shows a section along the axis X of Fig. 16 and shows the most suitable connection of the components at this point, which must be connected by the rings 12 without play and pressed together for the purpose of the correct circular shape of the pump and to restore concentricity and axiality with axis 0.
  • Fig. 18 shows a section along the line Y of Fig. 16 and shows in a partial representation on a larger scale the connections according to the axis Y. 13 and 14 are respectively the axes of the bores, which are the suction openings and discharge openings of two successive pumping elements form. These bores face the annular space 3 and can be aligned radially, as shown by arrows 131 and 141, or axially to connect the connections to the headers of the pump wear.
  • FIG. 19 shows a further exemplary embodiment of the pump according to the invention, in which the membrane 4 is arranged on a disk instead of on a cylindrical configuration.
  • the masses 6 have the shape of a truncated cone and are held by the pins 011, which e.g. are rigidly attached to the rotor 01, which in turn runs on a bearing 002, which is housed in the carrier 152 of the housing 15, which is provided with supports 151.
  • the gap 3 is already compressed by the masses 6 in the rest position, which make the pump work in motion.
  • the pins 011 can be articulated on the rotor by means of pins 0111, as shown in the drawing.
  • a suitable angle of inclination 600 and possibly additional masses which act on the pins 011 allow the resultant of the centrifugal force to be used in order to achieve the compression of the gap 3 in the direction of 0141.
  • 0141 also designates the exit (or the entry with the reverse course) of the fluid from the opening 14 shown as an example.
  • the insulation between the gaps of the various pumping elements can be achieved with the spokes 29 which connect the inner and outer rings 2 and which cause the pump body to abut the membrane.
  • the surface 251 of the spokes in FIG. 20 is coplanar with the corresponding surface of the membrane 4 when it is pressed by the masses 6.
  • FIG. 20 shows a further case in a longitudinal section game for the application of the invention to a double pump, which has and uses a space of the type shown in FIG. 3 and a space of the type shown in FIG. 4 with rotors 01 according to FIG. 5.
  • Two rotors according to FIG. 9 would be particularly suitable by using a shaft 011 which is simply toothed over the entire length.
  • the shaft 011 is guided and entrained by the shaft of the motor 00 on the one hand, and on the other hand it is supported and guided by bearings 22 which are attached to the cover 21, which in turn controls the fan as shown in FIG. 10 can support and hold.
  • the main object of this invention is characterized in any case by the division of the space 3 with the aid of a plurality of partitions 30, which guarantee a tightness for the fluid to be pumped, the division into several arcuate space or channel elements 31, 32 which follow one another like that 21 and 22 show schematic drawings in which each bend constitutes an elementary pumping unit because it is provided at the ends with the corresponding inlet (or suction) and outlet openings 38 and 39, respectively.
  • a schematic representation has been preferred in FIGS. 21 and 22, insofar as all structural details have already been described and illustrated in detail in the preceding explanations. 21 and 22: 1, the outer pump body, which is provided with corresponding inlet openings 38 and outlet openings 39, is present in such a number as subdivisions 30 are provided.
  • n is the number of elementary pumping units of a given machine, the total output is n times higher than that of a corresponding pump with a gap. In order for the angle 601 to be less than or equal to 389, it is generally sufficient if the number of masses is n + 1.
  • the two line sections 7 connect the outlet openings 39 to one another and introduce all of the liquid or all of the fluid into the recovery line 73, the check valve 72 preventing the fluid from returning when the machine is not running.
  • Fig. 22 shows an embodiment of the invention in a two-stage compressor using a machine with six elementary pumping units: the pumps 31, 32, 33 and 34 draw in the air from the environment with the corresponding four suction openings covering the whole Subdivide aspirated volumes, which results in a significant reduction in noise compared to a pump with a suction; the air accumulated in the collector 7 is cooled in the heat exchanger 70, which in turn is from that of a coaxial 10 promoted and cooled to the pumping unit 35 air is cooled.
  • the compression ratio of the first stage is 4 because on the one hand the volumes of the pumps 31-34 decrease due to the advance of the masses in the direction of 0133 and on the other hand the portion of the space corresponding to the suction of the pump 35 increases such that four volumes of the fluid be introduced into a volume of the pump 35.
  • the pump 36 can also be used to circulate the oil in a second heat exchanger 71, which is also on the one hand from the air of the coaxial fan is coated.
  • check valves 72 can be switched on, which above all improve the general function of the pump. These valves can be installed in each outlet or only in the latter, as shown in FIG. 22.
  • Fig. 23 is a diagram e.g. 21, assuming that the elementary pump unit 31 operates with air and the pump unit 32 with liquid. Although the two pumping units are identical, due to the different nature of the respective fluids, the pressure / performance characteristics are different, which is why, by using an insertion scheme 24, it is possible to achieve a mixture with a variable ratio between air and liquid, which acts on the opening pressure of the check valve 721 of the type with pressure control.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP88121098A 1987-12-18 1988-12-16 Pompe volumétrique pour fluides fonctionnant comme une pompe à pistons tournants Withdrawn EP0320963A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT8564687 1987-12-18
IT85646/87A IT1220167B (it) 1987-12-18 1987-12-18 Pompa volumetrica per fluidi liquidi o gassosi perfezionata

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Publication Number Publication Date
EP0320963A2 true EP0320963A2 (fr) 1989-06-21
EP0320963A3 EP0320963A3 (fr) 1989-11-23

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EP88121098A Withdrawn EP0320963A3 (fr) 1987-12-18 1988-12-16 Pompe volumétrique pour fluides fonctionnant comme une pompe à pistons tournants

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IT (1) IT1220167B (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0448937A2 (fr) * 1990-02-23 1991-10-02 Alcatel SEL Aktiengesellschaft Pompe à tuyau flexible
US8790096B2 (en) 2009-05-06 2014-07-29 Alcon Research, Ltd. Multiple segmented peristaltic pump and cassette
US20140356202A1 (en) * 2013-05-30 2014-12-04 Alcon Research, Ltd. Pump roller head with pivoting rollers and spring arms
US20140356203A1 (en) * 2013-05-30 2014-12-04 Alcon Research, Ltd. Pump roller assembly with independently sprung pivoting rollers
US20140356206A1 (en) * 2013-05-30 2014-12-04 Alcon Research, Ltd. Pump roller assembly with independently sprung rollers
US9693896B2 (en) 2013-03-15 2017-07-04 Novartis Ag Systems and methods for ocular surgery
US9750638B2 (en) 2013-03-15 2017-09-05 Novartis Ag Systems and methods for ocular surgery
US9797390B2 (en) 2013-05-30 2017-10-24 Novartis Ag Pump roller assembly with flexible arms
US9861522B2 (en) 2009-12-08 2018-01-09 Alcon Research, Ltd. Phacoemulsification hand piece with integrated aspiration pump
US9915274B2 (en) 2013-03-15 2018-03-13 Novartis Ag Acoustic pumps and systems
US9962288B2 (en) 2013-03-07 2018-05-08 Novartis Ag Active acoustic streaming in hand piece for occlusion surge mitigation
US10182940B2 (en) 2012-12-11 2019-01-22 Novartis Ag Phacoemulsification hand piece with integrated aspiration and irrigation pump
US20200256331A1 (en) * 2019-02-08 2020-08-13 Alcon Inc. Peristaltic pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9545337B2 (en) 2013-03-15 2017-01-17 Novartis Ag Acoustic streaming glaucoma drainage device
US9126219B2 (en) 2013-03-15 2015-09-08 Alcon Research, Ltd. Acoustic streaming fluid ejector

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH266467A (de) * 1948-06-10 1950-01-31 Schottler Hinrich Verdrängermaschine mit elastisch verformbaren Arbeitsraumwänden.
GB1152912A (en) * 1966-05-06 1969-05-21 Vni K I T I Gidromashinostroen Improvements in or relating to Rotary Pumps
DE2433145A1 (de) * 1974-07-08 1976-01-29 Rudolf V Davier Axiale druckmittelrotationsmaschine mit einer ringfoermigen membran
EP0223025A2 (fr) * 1985-11-18 1987-05-27 Renato Vicentini Pompe volumétrique pour fluides fonctionnant comme une pompe à pistons tournants
WO1988005868A2 (fr) * 1987-02-03 1988-08-11 Manfred Streicher Pompe peristaltique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH266467A (de) * 1948-06-10 1950-01-31 Schottler Hinrich Verdrängermaschine mit elastisch verformbaren Arbeitsraumwänden.
GB1152912A (en) * 1966-05-06 1969-05-21 Vni K I T I Gidromashinostroen Improvements in or relating to Rotary Pumps
DE2433145A1 (de) * 1974-07-08 1976-01-29 Rudolf V Davier Axiale druckmittelrotationsmaschine mit einer ringfoermigen membran
EP0223025A2 (fr) * 1985-11-18 1987-05-27 Renato Vicentini Pompe volumétrique pour fluides fonctionnant comme une pompe à pistons tournants
WO1988005868A2 (fr) * 1987-02-03 1988-08-11 Manfred Streicher Pompe peristaltique

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0448937A2 (fr) * 1990-02-23 1991-10-02 Alcatel SEL Aktiengesellschaft Pompe à tuyau flexible
EP0448937A3 (en) * 1990-02-23 1992-01-02 Standard Elektrik Lorenz Aktiengesellschaft Hose pump
US5173038A (en) * 1990-02-23 1992-12-22 Standard Elektrik Lorenz Aktiengesellschaft Peristaltic pump
US8790096B2 (en) 2009-05-06 2014-07-29 Alcon Research, Ltd. Multiple segmented peristaltic pump and cassette
US9861522B2 (en) 2009-12-08 2018-01-09 Alcon Research, Ltd. Phacoemulsification hand piece with integrated aspiration pump
US10182940B2 (en) 2012-12-11 2019-01-22 Novartis Ag Phacoemulsification hand piece with integrated aspiration and irrigation pump
US9962288B2 (en) 2013-03-07 2018-05-08 Novartis Ag Active acoustic streaming in hand piece for occlusion surge mitigation
US9693896B2 (en) 2013-03-15 2017-07-04 Novartis Ag Systems and methods for ocular surgery
US9750638B2 (en) 2013-03-15 2017-09-05 Novartis Ag Systems and methods for ocular surgery
US9915274B2 (en) 2013-03-15 2018-03-13 Novartis Ag Acoustic pumps and systems
US9624921B2 (en) * 2013-05-30 2017-04-18 Novartis Ag Pump roller head with pivoting rollers and spring arms
US9797390B2 (en) 2013-05-30 2017-10-24 Novartis Ag Pump roller assembly with flexible arms
US9797391B2 (en) * 2013-05-30 2017-10-24 Novartis Ag Pump roller assembly with independently sprung pivoting rollers
US20140356206A1 (en) * 2013-05-30 2014-12-04 Alcon Research, Ltd. Pump roller assembly with independently sprung rollers
US20140356203A1 (en) * 2013-05-30 2014-12-04 Alcon Research, Ltd. Pump roller assembly with independently sprung pivoting rollers
US10041488B2 (en) * 2013-05-30 2018-08-07 Novartis Ag Pump roller assembly with independently sprung rollers
US20140356202A1 (en) * 2013-05-30 2014-12-04 Alcon Research, Ltd. Pump roller head with pivoting rollers and spring arms
US20200256331A1 (en) * 2019-02-08 2020-08-13 Alcon Inc. Peristaltic pump

Also Published As

Publication number Publication date
IT8785646A0 (it) 1987-12-18
IT1220167B (it) 1990-06-06
EP0320963A3 (fr) 1989-11-23

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