EP1332287B1 - Pompe - Google Patents

Pompe Download PDF

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Publication number
EP1332287B1
EP1332287B1 EP01979202A EP01979202A EP1332287B1 EP 1332287 B1 EP1332287 B1 EP 1332287B1 EP 01979202 A EP01979202 A EP 01979202A EP 01979202 A EP01979202 A EP 01979202A EP 1332287 B1 EP1332287 B1 EP 1332287B1
Authority
EP
European Patent Office
Prior art keywords
piston
pump
chamber
constant
speed
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.)
Expired - Lifetime
Application number
EP01979202A
Other languages
German (de)
English (en)
Other versions
EP1332287A1 (fr
Inventor
Andreas Wahlberg
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.)
OCTAPUMP AB
Original Assignee
Octapump AB
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Octapump AB filed Critical Octapump AB
Publication of EP1332287A1 publication Critical patent/EP1332287A1/fr
Application granted granted Critical
Publication of EP1332287B1 publication Critical patent/EP1332287B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C9/00—Oscillating-piston machines or pumps
    • F04C9/007—Oscillating-piston machines or pumps the points of the moving element describing approximately an alternating movement in axial direction with respect to the other element

Definitions

  • the present invention relates to a pump of the kind defined in the preamble of Claim 1.
  • SE-B-393441 discloses a rotationally driven circular-cylindrical piston, which is received in a corresponding piston chamber in a pump housing.
  • the two end surfaces of the pump housing are mutually symmetrical in relation to a plane normal to the housing axis.
  • the two end surfaces of the piston are generally parallel with one another.
  • the periphery of each end surface is shown to lie in one plane.
  • the end surfaces of the pump housing and the end surfaces of the piston extend obliquely to the piston axis and to the chamber axis.
  • the length of the piston is such that the peripheral edges of respective end surfaces of the piston run concomitantly in contact with the respective periphery of the two end surfaces of the chamber as the piston rotates, whereby the piston is guided to move alternately forwards and backwards as a result of the co-action between the end surfaces of the piston and the chamber.
  • the pump housing includes two diametrically opposed regions and has midway of its length pipe connectors for the supply and discharge of fluid.
  • the pump piston includes midway of its length two diametrically opposed sides that include recesses which communicate with the inlet and the outlet respectively.
  • a first channel extends between one recess in the piston to one end surface thereof.
  • a second channel extends from the other recess of the piston to its other end surface.
  • one object of the invention is to provide a pump of the kind indicated above that has a smoother flow rate and a smaller dead volume at the end positions of the piston than known pumps of this kind.
  • the inventive pump is defined in the accompanying independent Claim 1.
  • a mechanical transfer curve which functions to convert rotary movement of the piston to a constant axial piston speed, during at least its fluid delivery phases, and ensures that the output flow rate of the pump will be constant at a constant speed of piston rotation.
  • the inventive concept encompasses several different embodiments.
  • the end surfaces of the piston are obliquely cut, so that the end surfaces of the piston will co-act with the edge of respective end surfaces of the pump chambers.
  • the axial speed of the piston will be constant for a constant rotational speed of the piston. Both peripheral edges of the piston-ends lie continuously in contact with the end surfaces of the pump chambers as the pump is at work.
  • the piston in a second embodiment of the invention, includes a peripherally extending guide groove, and the wall of the pump chamber is provided with a guide pin which engages the guide groove.
  • the end surfaces of the piston and the end surfaces of the chamber are planar and perpendicular to the piston axis.
  • the piston will move axially at a constant speed for a constant rotational speed.
  • the end surfaces of the piston and the pump chambers may be designed solely with the aim of being complementary in the end positions of the piston.
  • the end surfaces of the piston and the pump chambers may then, e.g., be planar and perpendicular to the axis of the piston and of the pump chamber.
  • the pump may have in both of these variants an internal valve arrangement of the kind disclosed in SE-B-393441 , for example.
  • the pump chambers may have separate lines for the infeed and outfeed of the fluid concerned. These lines may include check valves for maintaining one-way flow of the fluid through respective lines.
  • the two outlet lines may take fluid from one source and the two outlet lines may be combined to form a common outlet channel which delivers fluid at an essentially uniform rate of flow when the piston is rotated at a constant speed relative to the pump chamber.
  • the groove may alternatively be arranged in the wall of the pump chamber in the second variant, and the guide pin fitted on the piston. However, it is preferred at present to provide the groove in the piston.
  • the piston may be divided into two axially separated parts which are movable relative to one another axially. These parts are rotated about their respective axes at a constant speed.
  • One of the piston parts may be driven from a motor.
  • the other piston part may be driven by the first part through the medium of a coupling, such as a splines coupling, which while providing a rotation-guided coupling between the piston parts enables said parts to move axially relative to one another.
  • a coupling such as a splines coupling
  • Extending through the cylinder wall is an outfeed port which, during axial displacement of the piston part, is in contact with a fluid delivery groove on the barrel surface of said piston part during the delivery phase of the pump.
  • the groove has an arcuate extension of slightly more than 180°.
  • This provides compensation for the size of the delivery port, so as to ensure that fluid will be delivered throughout a rotational angle of 180° with respect to said piston part, wherewith the piston part has a constant axial speed.
  • the speed of the piston part concerned is of less interest during the suction phase.
  • suction takes place throughout an angle that is smaller than 180°. A complete suction phase can be ensured whilst the pump rotates over an angle smaller than 180°, by modifying the guide groove.
  • the extension of the guide groove 67 will enable the piston part to move at a constant speed between its end positions over a rotational angle of precisely 180°, whereafter the piston is moved at a different speed through an angle smaller than 180° between the terminal positions of the piston part during a suction phase.
  • the two piston parts are mutually phase-shifted through 180°.
  • the pump according to Figs. 1-5 is based fundamentally on the construction according to SE-B-393441 .
  • the piston includes a piston chamber defined by a wall 10 which has a circular-cylindrical inner surface, and two end walls 11, 13.
  • the pump housing defines a chamber 14 for a piston 40 that has a circular-cylindrical outer wall, which borders closely on the barrel wall of the housing.
  • the piston 40 can be moved axially and rotated in the chamber 14.
  • the piston 40 has generally parallel end surfaces 41, 42, which define an angle with the plane normal to the axis of the piston 40.
  • the end surfaces 11, 13 are mutually mirror-symmetrical in relation to a plane normal to the axis of a housing.
  • the end wall 13 of the housing is formed by a cover member 20, which is detachably connected to the housing wall 10, for instance by a bayonet joint 21.
  • the cover member 20 includes a central axially extending bore 22 for accommodating a corresponding drive shaft 30. That part of the bore 22 which connects with the chamber 14 includes a co-axially extending and circular-cylindrical enlarged part 23 which receives a widened sealing-portion 31 of the shaft 30 and a blade-like shaft portion 32 extending outwardly therefrom and a pair of projections 48 from the piston, as shown more clearly in Fig. 3 .
  • the barrel surface of the piston 40 includes two diametrically opposed recesses 44, 45.
  • a pump chamber 51, 52 is formed in the pump housing, at respective ends of the piston.
  • a channel or passageway 46 extends from the recess 45 to the pump chamber 51.
  • a channel or passageway 47 extends from the recess 44 to the pump chamber 52. Extending from the end surface 42 of the piston is a central, blind recess 43 for receiving the shaft part 32.
  • the shaft part 32 and the projections 48 are formed so that they will together essentially fill the cross-sectional area of the bore 23. It will also be seen that the ends of the projections 48 are terminated in a plane normal to the piston 40, so that the bore 23 will be generally filled completely by the illustrated components.
  • the end wall 11 of the pump and the end 41 of the piston have essentially complementary surfaces. This also applies to the surfaces 13, 42.
  • the wall 10 has two diametrically opposed connection lines or ports 15, 16 for the infeed and outfeed of fluid respectively. It will also be seen from Fig. 2 that the disc-shaped part 49 of the piston bordering on the recesses 44, 45 have a valve function with respect to the ports or lines 15, 16.
  • the end surfaces 11, 41; 42, 13 are generally complementary. Moreover, the end surfaces have co-acting peripheries which guide axial movement of the piston and cause the piston to travel at a substantially constant speed at a constant rotational speed.
  • One advantage in this respect is that the pump delivers an even fluid rate of flow.
  • respective chambers 51,52 will function as a suction chamber and an expulsion chamber respectively, and will switch functions during the second half of a revolution.
  • Fig. 4 is an end view of the piston-end 41 whose surface S can be considered to be defined by points Pn.
  • Figs. 4 and 5 illustrate an orthogonal co-ordinate system where the Z-axis coincides with the housing axis and the piston axis.
  • the surface S is tangential to the X-Y plane.
  • Each point Pn is defined by its angular distance ⁇ from X in the XY-plane and its radial distance a from the Z-axis and its height Z above the XY-plane.
  • Fig. 4 shows the channel 46.
  • the surface S is symmetrical in relation to the X-Z plane.
  • Each of the housing surfaces 11, 13 and the piston surfaces 41, 42 have this form in the preferred embodiment.
  • the surface S is conveniently rounded in its plane of symmetry.
  • the small degree of rounding required in order for acceleration of the piston to be finite in the turning positions of the piston may be adapted between strength requirements on the one hand and the acceptance of fluctuations in respect of the resultant fluctuations in the rate of fluid flow on the other hand.
  • the pump can be used to pump liquid or gas and has universal use. It is also suitable for pumping sensitive fluids.
  • the pump components can be injection-moulded with tolerances that avoid the need for separate seals, such as O-rings and the like.
  • Fig. 6 illustrates an embodiment in which the barrel surface of the pump piston 40 includes a guide groove 67.
  • the chamber wall carries a pin 68 which engages the groove 67.
  • the groove 67 is designed to cause the piston 40 to travel axially at a constant speed between its end positions when the rotational speed of said piston 40 is constant.
  • Fig. 7 shows the angle ⁇ for an arbitrary point p on the curve 67.
  • the length of stroke of the piston i.e. the distance with the Z-axis between the lowest and highest points of the groove 67 corresponds to the length of stroke h of the piston.
  • the ends of the piston are complementary with the end surfaces of the pump chamber.
  • the dead volume is substantially 0 at the end positions of the piston.
  • the end surfaces of the piston 40 are shown to be planar and perpendicular to the piston axis.
  • the end surfaces of the pump chamber are also shown to be planar and perpendicular to the axis of the pump housing.
  • the guide curve provides an axial cycle of piston movement with each revolution of the piston, which is beneficial with respect to a vertical arrangement of the kind shown in Fig. 1 , although it will be understood that the curve can be modified so as to provide two or more piston movement cycles with each revolution when so permitted by the chosen valve arrangement
  • valve function is formed by connection of the inlet and outlet ports or lines 15, 16 with axially extending piston recesses 44, 45 which widen circumferentially, where each widening is slightly smaller than one-half turn around the piston circumference, wherewith the fluid suction and fluid delivery phases are of equal length.
  • piston recesses 44, 45 which widen circumferentially, where each widening is slightly smaller than one-half turn around the piston circumference, wherewith the fluid suction and fluid delivery phases are of equal length.
  • the piston is divided axially into two parts 40, 40' which are coupled via a spline-coupling 81, 82, i.e. a rotationally rigid joint which couples together the piston parts 40, 40' while enabling said parts to move axially in relation to one another.
  • the piston part 40' is rotationally driven via a spline-connection 32, 33 from an axially driven shaft 30 which rotates at a constant speed.
  • Each piston part 40 has a circumferentially extending guide groove 67 in which a pin 68 engages.
  • the groove 67 has the form shown in Fig. 7 and extends through, or contains, an angle somewhat greater than 180°.
  • the pump also includes an outfeed port or line 16, 16' which co-acts with a peripheral groove 145, 145' which widens over a peripheral angle that is slightly greater than 180°.
  • fluid can be pumped out during rotation of respective piston parts 40, 40' through an angle of exactly 180°, wherewith said fluid is transported from respective chambers 51, 52 via a channel 146, 146' and via the groove 145, 145' to the port 16, 16' and through check valves 19 arranged therein.
  • the pin 68, 68' moves around the groove 67, 67' through an angle smaller than 180°, wherein the piston 40, 40' has corresponding suction grooves 144, 144' which are then held in alignment with the suction ports 15, 15'.
  • the suction grooves 144, 144' are in contact with respective pump chambers 51, 52 via channels 147, 147' in the piston 40, 40'.
  • the suction lines connecting with the ports 15, 15' may also include check valves 19, as shown in Fig. 8 .
  • the groove 67 has a steeper rise in the part that corresponds to the suction groove 144, it is ensured that the piston will be displaced between the end positions despite the groove 144 extending through an angle of less than 180°, wherewith the speeds of the piston parts 40, 40', however, will be different during the suction phase and the delivery phase respectively. These different speeds result in relative axial movements between the piston parts 40, 40', permitted by the coupling 81, 82.
  • the length of the pump housing is suitably chosen to ensure that the volumes of the chambers 51, 52 will be generally equal to 0 in the end positions of the piston.
  • the two piston parts are conveniently phase-shifted through 180° with respect to their fluid delivery phases, so that their common outflow will be constant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fluid-Driven Valves (AREA)
  • Eye Examination Apparatus (AREA)

Claims (7)

  1. Pompe comprenant un logement de pompe (10, 11, 20), qui comprend une chambre de piston cylindrique-circulaire (14), un piston de pompe cylindrique-circulaire (40) qui peut tourner et peut être déplacé axialement dans la chambre, des moyens (30, 43) pour entraîner en rotation le piston dans la chambre et des moyens (67, 68) pour donner au piston un mouvement de va-et-vient axial guidé dans la chambre de piston, par le biais de la rotation du piston, dans laquelle la pompe comprend des lignes et des moyens de soupape permettant au fluide de la pompe d'être aspiré dans et pompé hors des chambres de pompe, dans une seule direction entre les extrémités de la chambre de piston et une extrémité étroitement adjacente respective du piston, les moyens pour donner un mouvement de va-et-vient axial au piston étant adaptés pour provoquer le déplacement du piston axialement, à une vitesse constante, à une vitesse de rotation constante du piston, au moins pendant la fourniture du fluide de pompe, et des surfaces d'extrémité réciproquement adjacentes (11, 41 ; 13, 42) du piston et de la chambre de piston, respectivement, ont une forme complémentaire, de façon à minimiser le volume mort des chambres de pompe (51, 52), lesdites surfaces d'extrémité adjacentes avec la paroi interne cylindrique (10) de la chambre de piston et un élément de couverture (20), définissant respectivement lesdites chambres de pompe (51, 52), caractérisée en ce que lesdits moyens (67, 68) pour donner au piston un mouvement de va-et-vient axial guidé comprennent une cannelure de guidage (67) et une broche de guidage (68), ladite cannelure de guidage (67) étant ménagée dans la paroi du cylindre de la chambre ou du piston (40) et se mettent en prise, dans la cannelure (67) ; et en ce que la cannelure (67) est conçue pour provoquer le déplacement du piston axialement, à une vitesse constante entre ses positions d'extrémité, à une vitesse de rotation constante du piston.
  2. Pompe selon la revendication 1, caractérisée en ce qu'un arbre de commande (30) coaxial par rapport au piston, s'étend le long d'un canal (22, 23) à travers une paroi de logement (20) et a une partie de châssis non arrondie (32) qui se met en prise lors d'une ouverture du châssis (43) dans l'extrémité adjacente du piston (40) ; en ce que le canal (22, 23) a, près du piston, une partie élargie qui reçoit une section longitudinale de la partie de châssis non arrondie d'une part, et des corps de remplissage (48) disposés sur le piston d'autre part, dans laquelle la partie de châssis (32) et les corps de remplissage (48) remplissent la zone transversale de la partie élargie (23).
  3. Pompe selon la revendication 1 ou 2, caractérisée en ce que l'arbre (30) a une partie élargie (31), qui remplit une partie extérieure axialement de la portion élargie (23) du canal ; en ce que les corps de remplissage (48) se terminent dans un plan perpendiculaire à l'axe du piston (40) et remplissent la partie restante de la portion élargie du canal, avec la partie de châssis (32), quand la chambre de pompe adjacente (52) a un volume minimisé.
  4. Pompe selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le piston (40) a des extrémités symétriques en rotation.
  5. Pompe selon l'une quelconque des revendications 1 à 4, caractérisée en ce que les extrémités du piston et des chambres de pompe sont généralement planes et perpendiculaires à l'axe du piston.
  6. Pompe selon l'une quelconque des revendications 1 à 5, caractérisée par un orifice ou un tuyau d'entrée (15) et un orifice ou tuyau de sortie (16) qui relient, à travers la paroi de la chambre de pompe (10), dans deux zones diamétralement opposées de la chambre de piston (14), dans une zone centrale longitudinale de celle-ci, deux cavités ou creux diamétralement opposés (44, 45), dans la zone centrale longitudinale du piston, un premier canal (46) dans le piston entre sa dernière cavité (45) et une surface d'extrémité (41), un second canal (47) dans le piston entre sa seconde cavité (44) et sa seconde surface d'extrémité (42).
  7. Pompe selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le piston est divisé en deux parties axialement séparées (40, 40') ; en ce que chacune desdites pièces de piston a son propre dispositif (67, 68, 67', 68') pour permettre la translation de la vitesse rotationnelle en une vitesse de mouvement axial ; en ce que chaque pièce de piston a une première cannelure (144, 144'), qui est en contact avec un orifice d'entrée de fluide (15, 15') et a un élargissement périphérique de moins de 180° ; en ce que chaque pièce de piston a une seconde cannelure (145) qui est en contact avec un orifice de sortie (16, 16') et qui a un élargissement périphérique de plus de 180°, de sorte que le fluide sera distribué selon un angle de rotation de 180° ; en ce que la cannelure de guidage (67) est adaptée pour provoquer le déplacement du piston à une vitesse axiale constante pendant la phase de distribution de la pompe à une vitesse constante de rotation du piston ; et en ce que les pièces de piston (40, 40') sont adaptées pour être entraînées en rotation à une vitesse constante et similaire de rotation et sont adaptées pour un mouvement axial l'une par rapport à l'autre.
EP01979202A 2000-11-08 2001-11-01 Pompe Expired - Lifetime EP1332287B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE0004085A SE522138C2 (sv) 2000-11-08 2000-11-08 Pump
SE0004085 2000-11-08
PCT/SE2001/002400 WO2002038957A1 (fr) 2000-11-08 2001-11-01 Pompe

Publications (2)

Publication Number Publication Date
EP1332287A1 EP1332287A1 (fr) 2003-08-06
EP1332287B1 true EP1332287B1 (fr) 2009-05-27

Family

ID=20281742

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01979202A Expired - Lifetime EP1332287B1 (fr) 2000-11-08 2001-11-01 Pompe

Country Status (8)

Country Link
US (1) US20040101426A1 (fr)
EP (1) EP1332287B1 (fr)
JP (1) JP2004513299A (fr)
AT (1) ATE432417T1 (fr)
AU (1) AU2002211187A1 (fr)
DE (1) DE60138826D1 (fr)
SE (1) SE522138C2 (fr)
WO (1) WO2002038957A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1817499B1 (fr) 2004-11-29 2008-10-15 Thierry Navarro Pompe volumetrique a piston alternatif et rotatif
US7384249B2 (en) * 2005-02-28 2008-06-10 Nordson Corporation Fluid metering system
DE602005009966D1 (de) * 2005-12-28 2008-11-06 Sensile Pat Ag Mikropumpe
AU2011232741B2 (en) * 2005-12-28 2012-12-20 Sensile Medical Ag Micropump
US8172799B2 (en) * 2007-01-10 2012-05-08 Acist Medical Systems, Inc. Volumetric pump
US7951112B2 (en) * 2007-05-16 2011-05-31 Smiths Medical Asd, Inc. Pump module for use in a medical fluid dispensing system
EP2022982B1 (fr) 2007-07-23 2016-12-21 ACIST Medical Systems, Inc. Pompe volumétrique
EP2258333B1 (fr) 2009-06-02 2012-08-29 F.Hoffmann-La Roche Ag Dispositif de remplissage de réservoir flexible
EP2547908B1 (fr) * 2010-03-17 2019-10-16 Sensile Medical AG Micropompe
EP2628494A1 (fr) * 2012-02-17 2013-08-21 Sensile Pat AG Système de distribution et de stockage de liquide
US9511186B1 (en) 2012-10-23 2016-12-06 Acist Medical Systems, Inc. Medical injection systems and pumps
CN107747531B (zh) * 2017-04-25 2020-05-19 北京空天技术研究所 一种二维活塞输油泵

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Publication number Priority date Publication date Assignee Title
US1114132A (en) * 1912-07-24 1914-10-20 Gustav Gehrandt Gas-engine.
US2291601A (en) * 1940-07-31 1942-08-04 Howard L Bancroft Pump
US2316107A (en) * 1941-09-02 1943-04-06 Ruben Zorro David Engine
US2508253A (en) * 1946-09-26 1950-05-16 Dean C Haggardt Compressor unit
US3168872A (en) * 1963-01-23 1965-02-09 Harry E Pinkerton Positive displacement piston pump
JPS5524374Y2 (fr) * 1974-08-02 1980-06-11
SE393441B (sv) * 1975-07-31 1977-05-09 E A Nimell Vetskekolvpump med roterande och fram- och atergaende kolv
US4231716A (en) * 1978-02-27 1980-11-04 Tohoku Mikuni Kogyo Co., 1Td. Mechanical lubricating pump
US4797073A (en) * 1986-10-20 1989-01-10 Tohoku Mikuni Kogyo Kabushiki Kaisha Pump with rotating and reciprocating piston
US4854837A (en) * 1987-09-15 1989-08-08 Cordray International Corporation Rotary actuated pump or motor
US5032067A (en) * 1988-05-31 1991-07-16 Textron Inc. Lubricating - oil pump control
JP3290224B2 (ja) * 1993-01-12 2002-06-10 東芝キヤリア株式会社 流体圧縮機
US5494420A (en) * 1994-05-31 1996-02-27 Diba Industries, Inc. Rotary and reciprocating pump with self-aligning connection

Also Published As

Publication number Publication date
SE0004085L (sv) 2002-05-09
EP1332287A1 (fr) 2003-08-06
DE60138826D1 (de) 2009-07-09
WO2002038957A1 (fr) 2002-05-16
US20040101426A1 (en) 2004-05-27
SE522138C2 (sv) 2004-01-13
SE0004085D0 (sv) 2000-11-08
ATE432417T1 (de) 2009-06-15
AU2002211187A1 (en) 2002-05-21
JP2004513299A (ja) 2004-04-30

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