EP0025562A1 - Pompe à piston, notamment pompe de dosage - Google Patents

Pompe à piston, notamment pompe de dosage Download PDF

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Publication number
EP0025562A1
EP0025562A1 EP80105279A EP80105279A EP0025562A1 EP 0025562 A1 EP0025562 A1 EP 0025562A1 EP 80105279 A EP80105279 A EP 80105279A EP 80105279 A EP80105279 A EP 80105279A EP 0025562 A1 EP0025562 A1 EP 0025562A1
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
inner body
positive displacement
displacement pump
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Withdrawn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
EP80105279A
Other languages
German (de)
English (en)
Inventor
Joachim Dr. Teichmann
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.)
Franz Klaus Union Armaturen Pumpen GmbH and Co
Original Assignee
Franz Klaus Union Armaturen Pumpen GmbH and Co
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 Franz Klaus Union Armaturen Pumpen GmbH and Co filed Critical Franz Klaus Union Armaturen Pumpen GmbH and Co
Publication of EP0025562A1 publication Critical patent/EP0025562A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors

Definitions

  • the invention relates to a piston positive displacement pump (plunger pump), in particular a metering pump, for conveying fluids at high pressures and possibly high temperatures, with two piston-cylinder units, in which each of a linear drive via a clutch and a piston rod reciprocating displacement piston in a cylinder having an inlet valve (suction valve) and an outlet valve (pressure valve) can be pushed back and forth.
  • pluri pump in particular a metering pump
  • Oscillating displacement pumps i.e. pumps with pulsating delivery behavior
  • piston displacement pumps and metering pumps With metering pumps, the delivery volume per stroke can be set and reproduced within certain limits.
  • the dosing pumps can be subdivided into gland dosing pumps and glandless dosing pumps share.
  • stuffing box dosing pumps packings or sleeves provide the seal between the medium displacer and the pump chamber.
  • the pump chamber is separated from the primary displacer which transmits the reciprocating (oscillating) movement with the aid of a membrane, a hose membrane or a bellows, which is why such pumps are also called membrane pumps, hose membrane pumps or bellows pumps.
  • the primary displacer can be connected to the drive or the engine either by purely mechanical transmission or via a buffer liquid.
  • Stuffing box metering pumps are designed as plunger pumps or piston pumps. Plunger-free plunger pumps (plunger pumps) and piston pumps are not yet known.
  • gland dosing pumps mentioned here have certain advantages over the glandless pumps because of the need for diaphragms, hose diaphragms or bellows to separate the pump chamber from the primary displacer. These advantages include the fact that the service life until the need to replace wear parts, especially the Membranes, bellows or membrane hoses, is higher and that more precise dosing is often possible because of the larger strokes.
  • Diaphragm pumps have hitherto generally been used as metering pumps, particularly as a result of environmental protection requirements or because of the danger or toxicity of the medium to be pumped. These are not cheap. These pumps are very expensive, especially if they are used for medium quantities (approx. 1 m 3 / h) and higher back pressures ( > 100 bar). In order to achieve a long service life, the wearing parts are generally easily accessible and easy to replace. For the hydraulic side of diaphragm metering pumps, however, there is still no solution that is satisfactory from a maintenance point of view.
  • Oscillating positive displacement pumps have poor delivery characteristics and often lead to pressure pulsations, which are caused by the switching processes.
  • a large number of different possibilities have been shown to solve this problem.
  • the prerequisite is the use of at least two piston-cylinder units.
  • diaphragm pumps are out of the question. Rather, hydraulically driven gland piston pumps are considered inevitable.
  • Glandless metering pumps have a relatively low efficiency, which is 75 to 85% for diaphragm metering pumps and 85 to 95% for bellows metering pumps. But even with the usual stuffing box piston metering pumps, the efficiency is no higher than 85 to 95%.
  • diaphragm pumps become diaphragms breakage signaling double membranes applied, but this further reduces the efficiency.
  • Hydraulic pushrods are often not recommended for pumping mixtures, as this can result in component separation.
  • a double-acting oscillating positive displacement pump without leakage is achieved by using a magnetic coupling consisting of an inner and an outer body in the drive.
  • the pistons are each formed directly on the end faces of the inner body of the magnetic coupling, which is guided in a jacket tube made of non-magnetic material.
  • the cylinders or pumping spaces are also located within the casing tube, in each case at its end sections.
  • the invention is accordingly based on the task of creating a piston displacement pump which allows adaptation to different pressures or delivery volumes, which have a higher efficiency and a lower power-to-weight ratio than all Known metering pumps, which has a longer service life than all glandless metering pumps, which in particular achieves a volume flow of approx. 1 m 3 / h at high pressures (up to approx. 150 bar) and high temperatures (250 to 450 ° C without rod) and which is designed in such a way that the environmental protection requirements are met, according to which leaked liquid must not escape.
  • a pump solving this problem is specified in claim 1.
  • Advantageous refinements result from the subclaims. For example, for handling several different volume flows, in particular for their metered mixing, more than one piston-cylinder unit can also be provided on each side, possibly with different piston or cylinder dimensions, driven by a single drive unit.
  • the invention provides that at the point of introduction of the driving force, i.e. where the piston rod or the like is usually guided through the cylinder cover and the stuffing boxes, packings or sleeves are provided, such a seal is omitted, but the drive in Form of a magnetic coupling is formed, which, in contrast to what is known to date, has its inner body in a split tube connected to the cylinder or its cover flange in a liquid-tight manner, which in turn is fixedly connected to the piston rod, while the outer body of the magnetic clutch on the outside of the split tube, for example, from a linear drive is provided longitudinally displaceable.
  • the can in the preferred embodiment of the pump according to the invention is not only connected to the cylinder head of one pump, but simultaneously to two pumps, otherwise the free end of the gap Pipe is hermetically sealed with a lid, leakage liquid, which emerges from the pump chamber at the seals of the pump piston, cannot escape to the outside into the environment. So that the leakage liquid does not accumulate in the space above the rear of the pump piston such that a piston movement is finally no longer possible, a flow compensation is provided, which can be in the form of a line connecting both sides of the inner body of the magnetic coupling.
  • This relief line can be designed according to claim 2.
  • training according to claim 7 is expedient.
  • the essential importance of the invention lies in the possibilities that result from the structural separation of the magnetic drive from the piston-cylinder units. Because this separation allows an optimal dimensioning, design and adaptation of these units to the respective need and its requirements regardless of the design of the possible or required magnetic drive.
  • the pump pistons and cylinders also from the material selection, can be designed and manufactured in such a way that the leakage flow is kept as low as possible and the pistons are well guided and that sufficient lubrication is ensured by the pump medium.
  • the magnetic drive can be designed in terms of stroke and power in such a way that it can be adapted to the desired delivery characteristics and also to the energy requirement.
  • the diameter of the drive magnet can be made considerably larger than that of the piston, which means that Installation of correspondingly strong magnets, which thus interact with the outer body of the magnetic coupling with little slip, is made possible.
  • piston-cylinder units with different permanent magnet drives can be connected as a kit in order to achieve the desired delivery characteristics. Therefore, the invention enables the use of these pumps in a wide range of applications in an economical manner.
  • the pump according to the invention can be operated at very high pressures, e.g. System pressures of 800 bar, and at the same time high temperatures, i.e. Use temperatures above 300 ° C. It has a very high efficiency of over 95%. Due to the simple design principle, the power-to-weight ratio of the pump is also significantly lower than that of all other known glandless pumps, and the new pump mainly works with large strokes. This results in a small clearance ratio and, especially with two piston-cylinder units, low pulsations and small mass forces. The latter result from the fact that, as is well known, the inertial forces in piston pumps depend quadratically on the frequency, but only linearly on the stroke. The conventional glandless metering pumps had to be operated at relatively higher speeds, however, because their diaphragm does not allow large excursions. Long stroke piston pumps work more "valve independent" and therefore have a better volumetric efficiency. This also improves with decreasing frequency.
  • very high pressures e.g. System pressures of 800 bar
  • high temperatures i.e
  • the production cost of the pump according to the invention is also lower than in the case of known glandless metering pumps.
  • the two cylinder-piston units are designed as piston displacement pumps 1, the cylinders 5 of which have an inlet valve (suction valve) 2 and an outlet valve (pressure valve) 3 designed as a ball valve.
  • a displacer 6 is arranged displaceably within each of the cylinders 5.
  • the two pistons 6 are axially connected to one another with a continuous piston rod 7.
  • piston rings 8 for sealing against the inner wall of the cylinder 6 and guide rings 9 are provided.
  • Each cylinder 5 is provided with a wide, radially projecting flange 10 at any point along its longitudinal extent that can be adapted as required, in the present example at its end facing away from the pump chamber.
  • a can 11 is arranged between the flanges 10 of the two pumps, the diameter of which can be adapted to the desired pump output, and can consequently be considerably larger than the diameter of the pistons themselves.
  • seals 14 are provided on the outside.
  • the can 11 each carries a flange 14 'which is clamped to the cylinder flange 10 by means of screws and nuts.
  • the magnetic coupling 20 has an outer body 21 and an inner body 22.
  • the inner body 22 is axially immovably fixed on the piston rod 7. It has an axially parallel relief bore 23.
  • the inner body 22 sits centrally on the piston rod 7 so that it can be displaced equally far in both axial directions.
  • the diameter and the length of the magnetic coupling 20 or its inner and outer body depend on the power to be transmitted to the medium.
  • the ratio of the head to the flow rate is then determined for a given output in accordance with the basic laws of hydrostatics by the ratio of the cross-sectional areas of the can 11 and the piston 6.
  • the can 11, which separates the inner body 22 from the outer body 21 of the magnetic coupling, must consist of non-magnetic material and be designed according to the thermal and mechanical load.
  • the inner and outer bodies 22, 21 of the magnetic coupling 20 are provided with permanent magnet systems 27, 28, which are optionally composed of radially or axially magnetized ring magnets 24 and are therefore non-positively connected to one another.
  • the permanent magnet system 28 of the inner body 22 is accommodated in a protective sleeve 25 which is hermetically sealed on all sides or is provided with a protective layer, which is why it cannot come into contact with the conveyed medium. It is therefore beyond its aggressive influence.
  • Leakage fluid can accumulate within the spaces on both sides of the inner body 22 over time, which can emerge from the piston rings 8 of the piston 6 during the pressure stroke.
  • the inner body 22 of the magnetic coupling 20 is therefore provided with the relief bore 23 in order to achieve a mass balance of the leakage fluid within the can 11 during the movement sequence, if the ring or gap flow between the inner body 22 and the can 11 should not be sufficient for this.
  • the inner body 22 and the outer body 21, like each piston 6, are provided with guide rings 26.
  • the piston rod 7 can, as shown, be divided by means of joints 15 on both sides of the inner body 22 or, alternatively, can be made rigidly continuous.
  • the can 11 and, accordingly, the inner and outer bodies of the magnetic coupling 20 are each circular cylindrical.
  • the outer body 21 and the inner body 22 each carry the permanent magnet system 27 and 28 on the inside and outside, respectively.
  • the two following magnet arrangements are mainly used in the permanent magnet systems.
  • axially magnetized ring magnets these are arranged such that two permanent magnets 24 are separated from one another by one or more cutting disks 30, the sides of the permanent magnets 24 adjacent to the cutting disks 30 having the same polarity, but in a jacket body 31 opposite to the polarity of the permanent magnets 24 freely movable inner body 22.
  • the magnetic flux between the inner and outer body takes place here via the cutting disks 30, which are made of soft magnetic material. You close the magnetic circuit.
  • two permanent magnets arranged radially opposite each other are connected with opposite poles, but are connected to another pair of ring magnets with opposite polarity via cylindrical inferences made of soft magnetic material.
  • the magnetic circuit is thus formed by four ring magnets and two yoke bodies.
  • Ring magnets with large diameters and small wall thicknesses are expensive to manufacture. In this case it is advisable to build ring magnets from ring segments or rod segments into polygons.
  • the magnetic coupling 20 is only shown in section in the upper half of the figure, while a sectional view of the inner body 22 and the outer body 21 is omitted in the lower half of the figure.
  • At least two pins 33 are provided on the outside of the outer body 21 for the articulation of a linear drive with which the outer body 22 is moved back and forth.
  • the linear drive can be of conventional design. It can be designed as a mechanical, but also as a hydraulic drive.
  • the energy transfer to the delivery medium is carried out by the piston 6 which is connected to the inner body 22 in a form-fitting manner.
  • This is part of a piston pump head of a piston positive displacement pump that is integrated into the pump system.
  • the can 11 and the cylinder head are firmly and hermetically connected to one another by direct contact or via the annular seal 14 made of soft or hard materials.
  • a design without relief channels 23 and, if appropriate, with a can sealed off by a cover with only a single piston-cylinder unit, enables applications in refrigeration technology, since that Pumped medium in the interior of the canned tube is in the gaseous state and thus this piston pump supplies the pumped medium with only small amounts of energy in the form of heat and at the same time has the good overall efficiency known for the positive displacement pumps.
  • the canned tube and the pressure connection 3 ′ arranged beyond the pressure valve 3 are connected to one another by a relief line 3 ′′ (only indicated by dashed lines in the drawing).
  • a relief line 3 ′′ (only indicated by dashed lines in the drawing).
  • This pump is recommended for applications in which the spatial conditions do not allow the installation of a double-acting magnetic piston pump, as shown in the drawing.
  • the design form according to the drawing with two piston-cylinder units has the best efficiency, since the volume flow is about twice as large compared to the single-acting pressure pumps.
  • Drive powers of approximately 10 kW can be achieved with the pump according to the invention.
  • the drive efficiency is very high, especially since the drive can work at a low angular speed if it starts from a rotary movement. This enables precise dosing even at low revolutions per minute and high stroke.
  • the area of application of the pump is when using Al Ni Co magnets at temperatures up to approx. 450 ° C and with Co Se magnets at temperatures up to approx. 250 ° C.
  • the achievable pressure differences between suction and pressure ports 2 ', 3' are approx 200 bar, but the system pressure can easily reach 800 bar.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP80105279A 1979-09-13 1980-09-04 Pompe à piston, notamment pompe de dosage Withdrawn EP0025562A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2937157 1979-09-13
DE2937157A DE2937157C2 (de) 1979-09-13 1979-09-13 Kolbenverdrängerpumpe, insbesondere Dosierpumpe

Publications (1)

Publication Number Publication Date
EP0025562A1 true EP0025562A1 (fr) 1981-03-25

Family

ID=6080864

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80105279A Withdrawn EP0025562A1 (fr) 1979-09-13 1980-09-04 Pompe à piston, notamment pompe de dosage

Country Status (6)

Country Link
EP (1) EP0025562A1 (fr)
JP (1) JPS5681278A (fr)
BR (1) BR8005867A (fr)
DE (1) DE2937157C2 (fr)
ES (1) ES8105830A1 (fr)
ZA (1) ZA805603B (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2538460A1 (fr) * 1982-12-27 1984-06-29 Festo Maschf Stoll G Appareil pour le transport des gaz et/ou des liquides
FR2751035A1 (fr) * 1996-07-15 1998-01-16 Serac Group Pompe doseuse a commande magnetique
WO2010027586A1 (fr) * 2008-09-08 2010-03-11 Cameron International Corporation Système de compression comportant un joint d'étanchéité avec couplage magnétique de pistons
WO2012152609A1 (fr) * 2011-05-06 2012-11-15 Electrolux Home Products Corporation N.V. Ensemble pompe alternative pour liquides
CN103670996A (zh) * 2012-09-14 2014-03-26 胜瑞兰工业设备（苏州）有限公司 一种无泄漏式磁力驱动往复泵
WO2015049021A1 (fr) * 2013-09-26 2015-04-09 Hydac System Gmbh Dispositif de refoulement permettant de distribuer un fluide sur une conduite de fluide
US9482235B2 (en) 2008-06-20 2016-11-01 Ingersoll-Rand Company Gas compressor magnetic coupler
EP3476469A1 (fr) * 2017-08-29 2019-05-01 Instytut Chemii Organicznej Polskiej Akademii Nauk Installations d'écoulement pour le traitement à haute pression en mode continu

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3127893A1 (de) * 1981-07-15 1983-02-03 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen "arbeitsmaschine zum foerdern von fluessigkeiten und gasen
JPS5926390U (ja) * 1982-08-13 1984-02-18 セーラー万年筆株式会社 両頭筆記具
JPH0542679U (ja) * 1990-12-07 1993-06-11 株式会社利根 往復動ポンプ装置
DE29706074U1 (de) * 1997-04-07 1997-07-31 Wagner Wilhelm Wiwa Dosierpumpe
DE19846711C2 (de) * 1998-10-09 2003-05-08 Trumpf Sachsen Gmbh Hochdruckpumpe mit Linearmotorantrieb
DE102006060147B4 (de) * 2006-12-18 2009-05-14 Andreas Hofer Hochdrucktechnik Gmbh Fluidarbeitsmaschine
CN115256286A (zh) * 2022-09-13 2022-11-01 成都银河动力有限公司 一种组合活塞油道进油孔定位销组件及装配方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE63803C (de) * H. AUMUND in Hannover, Nelkenstrafse 24 Gas-Compressor für Kälteerzeugungsmaschinen mit elektrischem Antriebe zum Zweck, den Gasaustritt aus der Stopfbuchse zu vermeiden
US2528415A (en) * 1945-07-10 1950-10-31 Henry A Boorse Pump
CH290430A (fr) * 1952-02-20 1953-04-30 Reutter Jean Leon Compresseur oscillant synchrone pour courant alternatif.
US2832919A (en) * 1953-03-10 1958-04-29 Reutter Jean Leon Movable equipment for electro-magnetically controlled devices
FR2125909A5 (fr) * 1971-02-15 1972-09-29 Omre Constr Elettro
DE2812481A1 (de) * 1978-03-22 1979-09-27 Teichmann Joachim Magnetkolbenpumpe zum foerdern von fluiden

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2712552C2 (de) * 1977-03-22 1979-05-17 Joachim Dipl.-Ing. 4630 Bochum Teichmann Magnetkolbenpumpe zum Fördern von Fluiden

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE63803C (de) * H. AUMUND in Hannover, Nelkenstrafse 24 Gas-Compressor für Kälteerzeugungsmaschinen mit elektrischem Antriebe zum Zweck, den Gasaustritt aus der Stopfbuchse zu vermeiden
US2528415A (en) * 1945-07-10 1950-10-31 Henry A Boorse Pump
CH290430A (fr) * 1952-02-20 1953-04-30 Reutter Jean Leon Compresseur oscillant synchrone pour courant alternatif.
US2832919A (en) * 1953-03-10 1958-04-29 Reutter Jean Leon Movable equipment for electro-magnetically controlled devices
FR2125909A5 (fr) * 1971-02-15 1972-09-29 Omre Constr Elettro
DE2812481A1 (de) * 1978-03-22 1979-09-27 Teichmann Joachim Magnetkolbenpumpe zum foerdern von fluiden

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2538460A1 (fr) * 1982-12-27 1984-06-29 Festo Maschf Stoll G Appareil pour le transport des gaz et/ou des liquides
FR2751035A1 (fr) * 1996-07-15 1998-01-16 Serac Group Pompe doseuse a commande magnetique
WO1998002658A1 (fr) * 1996-07-15 1998-01-22 Serac Group Pompe doseuse a commande magnetique
US6132188A (en) * 1996-07-15 2000-10-17 Serac Group Dosing pump with magnetic control
US9482235B2 (en) 2008-06-20 2016-11-01 Ingersoll-Rand Company Gas compressor magnetic coupler
US8863646B2 (en) 2008-09-08 2014-10-21 Ge Oil & Gas Compression Systems, Llc Compression system having seal with magnetic coupling of pistons
WO2010027586A1 (fr) * 2008-09-08 2010-03-11 Cameron International Corporation Système de compression comportant un joint d'étanchéité avec couplage magnétique de pistons
GB2476597A (en) * 2008-09-08 2011-06-29 Cameron Int Corp Compression system having seal with magnetic coupling of pistons
GB2476597B (en) * 2008-09-08 2013-02-27 Cameron Int Corp Compression system having seal with magnetic coupling of pistons
CN103620217A (zh) * 2011-05-06 2014-03-05 伊莱克斯家用产品公司 用于液体的往复式泵组件
CN103620217B (zh) * 2011-05-06 2016-05-25 伊莱克斯家用产品公司 用于液体的往复式泵组件
WO2012152609A1 (fr) * 2011-05-06 2012-11-15 Electrolux Home Products Corporation N.V. Ensemble pompe alternative pour liquides
US9709047B2 (en) 2011-05-06 2017-07-18 Electrolux Home Products Corporation N.V. Reciprocating pump assembly for liquids
CN103670996A (zh) * 2012-09-14 2014-03-26 胜瑞兰工业设备（苏州）有限公司 一种无泄漏式磁力驱动往复泵
WO2015049021A1 (fr) * 2013-09-26 2015-04-09 Hydac System Gmbh Dispositif de refoulement permettant de distribuer un fluide sur une conduite de fluide
EP3476469A1 (fr) * 2017-08-29 2019-05-01 Instytut Chemii Organicznej Polskiej Akademii Nauk Installations d'écoulement pour le traitement à haute pression en mode continu

Also Published As

Publication number Publication date
BR8005867A (pt) 1981-03-24
JPS5681278A (en) 1981-07-03
ES495029A0 (es) 1981-06-16
ES8105830A1 (es) 1981-06-16
DE2937157C2 (de) 1982-06-16
DE2937157A1 (de) 1981-04-02
ZA805603B (en) 1981-08-26

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Inventor name: TEICHMANN, JOACHIM, DR.