EP0421461A1 - Pompe à piston axial - Google Patents

Pompe à piston axial Download PDF

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Publication number
EP0421461A1
EP0421461A1 EP90119160A EP90119160A EP0421461A1 EP 0421461 A1 EP0421461 A1 EP 0421461A1 EP 90119160 A EP90119160 A EP 90119160A EP 90119160 A EP90119160 A EP 90119160A EP 0421461 A1 EP0421461 A1 EP 0421461A1
Authority
EP
European Patent Office
Prior art keywords
piston
pump according
cylinder
piston pump
axial
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Withdrawn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
EP90119160A
Other languages
German (de)
English (en)
Inventor
Martin Gander
Hans Jürg Jösler
Elmar Morscher
Thomas Neher
Jean-Marie Zogg
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.)
Draegerwerk AG and Co KGaA
Original Assignee
Draegerwerk AG and Co KGaA
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 Draegerwerk AG and Co KGaA filed Critical Draegerwerk AG and Co KGaA
Publication of EP0421461A1 publication Critical patent/EP0421461A1/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Withdrawn legal-status Critical Current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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated

Definitions

  • the invention relates to an axial piston pump according to the preamble of claim 1.
  • Valve-less pumps of this type with a single rotary piston are used, for example, as metering pumps for liquids wherever precisely metered quantities have to be conveyed.
  • the pump direction is reversible depending on the direction of rotation of the rotary lobe.
  • the piston itself closes the pressure and suction side, so that no shut-off or check valves are required.
  • the delivery rate of the pump can be controlled particularly easily via the speed.
  • the periodic axial movement of the piston is generated by a type of crank mechanism, the crank being fastened to the rotary piston and the end of the crank being articulated on an eccentric disk on the drive shaft.
  • a transmission is shown for example in US-A-3,168,872.
  • the cylinder with the rotary piston movable therein is mounted in such a way that the piston axis can be deflected relative to the axis of the drive shaft.
  • the piston only rotates in the cylinder and does not travel any stroke.
  • the desired piston stroke can be set by the degree of deflection of the piston axis relative to the axis of the drive shaft.
  • a disadvantage of the known pump drives is that the sliding couplings are exposed to relatively high mechanical loads and are therefore prone to failure.
  • the drive shaft it is not possible or desirable in all cases for the drive shaft to be inclined relative to the piston axis.
  • the drive shaft should, if possible, run coaxially with the rotary piston.
  • cam carrier is a control surface that runs round and the piston and is fixedly arranged relative to it, and if the engagement member is directly or indirectly firmly connected to the piston and is rotatable on the control surface about the piston axis.
  • the engagement member can be pressed against the control surface either under the influence of gravity or under spring preload.
  • the drive shaft is arranged coaxially with the piston and if a compression spring is arranged between the drive shaft and the piston, wherein the compression spring can simultaneously serve as a coupling element for torque transmission.
  • the col ben performs its stroke movement under spring preload, the spring tension possibly being adjusted so that the friction on the control surface is not too great.
  • the control surface is particularly advantageously arranged directly on an end face of the cylinder.
  • a cylinder of this type can be produced particularly easily by being cut or ground obliquely on one side.
  • the stroke volume is determined by the angle of the control surface relative to the piston axis.
  • the control surface could, however, also be arranged on a control part which is interchangeable and / or adjustable.
  • the engagement difference can be a pin or a similar sliding element, or it can also be a rolling element that rolls on the control surface in order to reduce the friction.
  • the cylinder and the piston are made of a ceramic material, particularly good running properties can be achieved without the need for additional lubrication.
  • Piston seals or the like are also not necessary at low pressures, since the piston runs almost without play in the cylinder. Ceramic materials are also corrosion-resistant, so that e.g. chemically aggressive media could also be easily conveyed.
  • the axial piston pump 1 consists essentially of a cylinder 2 which is fixedly connected to a housing 11. At the lower end of the cylinder, a suction opening 3 and a pressure opening 4 are arranged in each case in the cylinder jacket, the two openings running coaxially. Accordingly, a connection 19 for a suction line and a connection 20 for a pressure line are respectively arranged in the pump housing 11.
  • a piston 6 is guided in the cylinder 2, which on the one hand is rotatable about its own axis in the direction of arrow X and on the other hand can execute an axial piston stroke in the direction of arrow Y.
  • a recess 7 is arranged, which enlarges the pump chamber.
  • the recess 7 communicates once with the suction opening 3 and once with the pressure opening 4, the respective other opening being closed.
  • the piston can suck in liquid or gas at the suction opening when the pressure opening 4 is closed and when the piston movement is reversed eject through the pressure opening when the suction opening is closed.
  • the piston as is also already known, could easily be designed as a duplex piston with two pump chambers.
  • the piston 6 is connected in a rotationally fixed manner to a clutch hub 12.
  • An engagement member 9 in the form of a slide pin is attached eccentrically to the coupling hub.
  • the end face of the cylinder 2 is chamfered at an angle alpha and thus forms a control surface 8 surrounding the piston 6.
  • a different curve shape could also be selected to achieve a certain pump characteristic.
  • a compression spring 10 is tensioned between the coupling hub 12 and the drive shaft 5, which is fixed relative to the cylinder 2. This compression spring presses the engagement member 9 against the control surface 8, so that the piston 6 is moved back and forth under spring preload.
  • the compression spring 10 also serves as a clutch for torque transmission and thus fulfills a double function.
  • the coupling hub 12 has a pin 33 in the upper region, which is provided with a tangential locking surface 15.
  • the pin engages in a coupling sleeve 13, on which a locking screw 14 can be clamped radially against the surface 15, so that the coupling hub 12 is detachably connected to the compression spring.
  • the compression spring 10 is non-rotatably connected to the coupling sleeve 13 and non-rotatably connected to the shaft hub 17 at the upper end.
  • the shaft hub 17 can be clamped to the drive shaft 5 with a locking screw 18, and the spring preload can also be set in the direction of the arrow f at the same time.
  • a coding disk 16 is also attached to the coupling hub 12 and is cut off on one side.
  • the encoder disc works with a sensor, e.g. with a light-sensitive sensor 36 together ( Figure 2) and is used for speed measurement.
  • the encoder disk can have a line marking 21, so that e.g. the exact relative position of the piston could also be determined using the principle of an incremental measuring system.
  • the piston 6 is shown in the lower stroke position, in which it closes the pressure opening 4 and the suction opening 3 and in which the entire pump volume has just been expelled.
  • the engagement member 9 slides upward on the control surface 8 into the position shown in FIG.
  • the piston 6 is pressed upward against the force of the compression spring 10 and reaches an upper stroke position, in which in turn both openings 3 and 4 are closed.
  • the piston 6 has increased the volume of the pump chamber 34 and in the process sucked in the corresponding amount of the conveying medium because the recess 7 communicates with the suction opening 3.
  • the engaging member 9 slides back into the lowest relative position on the control surface 8, so that the piston is pressed downward, expelling the contents of the pump chamber 34 via the pressure opening 3.
  • the piston shape is shown enlarged in Figures 7 and 8 again.
  • the recess 7 has the shape of a tangential cutout, which is rounded at the top.
  • the piston has been turned back by 90 ° compared to FIG. 1, closing the suction opening 3 and covering half of its stroke.
  • FIG. 4 shows an embodiment in which the angle alpha can be adjusted by a certain amount.
  • the control surface 8 is not arranged on the end face of the cylinder 2, but on a cam 22.
  • the cam disc 22 is held by two diametrically opposite set screws 23 which engage in nuts 24 on the cam disc. These nuts are designed as rotating or sliding pieces so that the inclination and the change in distance can be compensated for.
  • the desired angle alpha can obviously be set by turning the adjusting screws 23.
  • the engagement member is designed as a ball 25, which rolls on the control surface 8.
  • the cam bearer does not necessarily have to be fixed.
  • the piston 6 is fixedly connected to a swash plate 26, which forms the control curve.
  • the swash plate is pressed by the compression spring 10 against a sliding finger 27, which is fixed to the cylinder 2.
  • a sliding finger 27 which is fixed to the cylinder 2.
  • FIG. 6 shows an embodiment in which a spring preload is not absolutely necessary.
  • the cylinder 2 has a section 28 with an enlarged inner diameter. This section is on the inside an inclined or curved groove 29 is arranged.
  • the enlarged piston section 35 has a bolt 30 which engages radially in the groove 29.
  • the axial relative displacement between the drive shaft 5 and the piston 6 can be compensated for by an axial groove 31 which slides on the shaft 5 in a rotationally fixed manner via an axial guide 32.
  • the axial guide also serves to transmit torque.
  • the groove could also be arranged on the enlarged piston section 35, while the bolt 30 is fixed on the inner surface of the cylinder.
  • the cylinder 2 and the piston 6 are preferably made of a ceramic material. In this way, the piston can be guided in the cylinder without a seal up to approx. 1 bar pressure.
  • the parts are also very wear-resistant, which is particularly important if the control surface 8 is arranged directly on the cylinder 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP90119160A 1989-10-06 1990-10-05 Pompe à piston axial Withdrawn EP0421461A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3666/89A CH679172A5 (fr) 1989-10-06 1989-10-06
CH3666/89 1989-10-06

Publications (1)

Publication Number Publication Date
EP0421461A1 true EP0421461A1 (fr) 1991-04-10

Family

ID=4260897

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90119160A Withdrawn EP0421461A1 (fr) 1989-10-06 1990-10-05 Pompe à piston axial

Country Status (4)

Country Link
US (1) US5102310A (fr)
EP (1) EP0421461A1 (fr)
JP (1) JPH03124976A (fr)
CH (1) CH679172A5 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108843558A (zh) * 2018-06-15 2018-11-20 深圳市益思精密五金有限公司 高压恒流泵、其柔性柱塞杆及降低压力脉动的方法

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5635070A (en) * 1990-07-13 1997-06-03 Isco, Inc. Apparatus and method for supercritical fluid extraction
DE4409994A1 (de) * 1994-03-23 1995-09-28 Prominent Dosiertechnik Gmbh Verdrängerkolbenpumpe
US6398513B1 (en) * 2000-09-20 2002-06-04 Fluid Management, Inc. Fluid dispensers
US20060037971A1 (en) * 2004-08-19 2006-02-23 Minard James J Positive displacement pump
DE102004062300A1 (de) * 2004-12-23 2006-07-13 BSH Bosch und Siemens Hausgeräte GmbH Linearverdichter
US20080187449A1 (en) * 2007-02-02 2008-08-07 Tetra Laval Holdings & Finance Sa Pump system with integrated piston-valve actuation
WO2012171572A1 (fr) 2011-06-16 2012-12-20 Tecpharma Licensing Ag Dispositif pour administrer un produit fluide
US10309380B2 (en) 2011-11-16 2019-06-04 Ocean Pacific Technologies Rotary axial piston pump
US10094364B2 (en) 2015-03-24 2018-10-09 Ocean Pacific Technologies Banded ceramic valve and/or port plate
CA2985213C (fr) * 2015-06-22 2020-09-15 Medtronic Minimed, Inc. Techniques de detection d'occlusion pour un dispositif de perfusion de fluide ayant un mecanisme de pompe a rotor
US11559468B2 (en) 2017-03-24 2023-01-24 Carefusion 303, Inc. Syringe pump for automatic drug compounders
EP4375507A1 (fr) * 2022-11-25 2024-05-29 Sensile Medical AG Micropompe
CN116812467B (zh) * 2023-07-03 2024-06-07 江苏华兴压力容器有限公司 一种可控制进料的反应釜进料旋转阀

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2896459A (en) * 1957-02-15 1959-07-28 Thunderbird Engineering Compan Fluid pump
FR1416519A (fr) * 1964-09-23 1965-11-05 Cem Comp Electro Mec Pompe à faible débit, du type à piston plongeur animé d'un mouvement de rotation
US3230892A (en) * 1963-09-19 1966-01-25 Burns Nathan Reciprocating mechanism with fluid conducting means
DE1528357A1 (de) * 1964-04-06 1969-09-25 Partner Ab Anordnung fuer Schmieroelpumpen
US3914073A (en) * 1974-12-17 1975-10-21 Ralph L Fusco Printing ink pump
GB1411844A (en) * 1973-03-03 1975-10-29 Birmingham Small Arms Co Ltd Lubricating pumps for internal combustion engines

Family Cites Families (25)

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Publication number Priority date Publication date Assignee Title
CA525963A (fr) * 1956-06-05 Zaba Joseph Plongeur a gaz pour elever des liquides
US1846000A (en) * 1924-10-27 1932-02-16 Hughes Tool Co Pneumatic swab
US1819994A (en) * 1925-03-04 1931-08-18 Charles Paul Mackie Fluid lift for liquids
US1836871A (en) * 1928-11-08 1931-12-15 Hughes Tool Co Well pumping swab
US1919547A (en) * 1931-10-27 1933-07-25 Hughes Tool Co Pneumatic swab plunger
US1947511A (en) * 1932-12-20 1934-02-20 Hughes Tool Co Plunger lift control device
US2001012A (en) * 1933-11-01 1935-05-14 Everett K Burgher Piston lift for pumping of liquids
US2237408A (en) * 1938-11-18 1941-04-08 Everett K Burgher Well pumping apparatus
US2267902A (en) * 1939-09-08 1941-12-30 William N Eddins Pump
US2865455A (en) * 1950-10-25 1958-12-23 Pan American Petroleum Corp Tubing scraper
US2714855A (en) * 1952-05-01 1955-08-09 N F B Displacement Co Ltd Apparatus for gas lift of liquid in wells
US2937598A (en) * 1956-11-05 1960-05-24 Us Industries Inc Free piston
US3095819A (en) * 1959-12-02 1963-07-02 Us Industries Inc Free piston pumping system
US3424066A (en) * 1966-02-28 1969-01-28 Earl K Moore Jr Free piston type plunger
US3410217A (en) * 1967-04-25 1968-11-12 Kelley Kork Liquid control for gas wells
JPS5214722B2 (fr) * 1972-06-19 1977-04-23
JPS5169202A (fr) * 1974-12-11 1976-06-15 Automobile Antipollution
US4070134A (en) * 1975-04-17 1978-01-24 William Dwight Gramling Gas powered swabbing device
US4465435A (en) * 1982-04-26 1984-08-14 Copas James I Apparatus for using natural gas pressure for pumping a well
US4869646A (en) * 1984-10-15 1989-09-26 American Hospital Supply Corp. Continuous peristaltic pump
DE3447091A1 (de) * 1984-12-22 1986-07-03 Fa. Andreas Stihl, 7050 Waiblingen Oelpumpe
SE458623B (sv) * 1985-12-16 1989-04-17 Boerje Aarnedal Anordning foer omvandling av mekanisk rotation till tryckenergi och/eller vice versa
US4712981A (en) * 1986-02-24 1987-12-15 Gramling William D Pressure-operated valving for oil and gas well swabs
US4696624A (en) * 1987-04-08 1987-09-29 Bassco, Inc. Casing pump
JPH01211668A (ja) * 1988-02-18 1989-08-24 Sanyo Electric Co Ltd ２シリンダー密閉型電動圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2896459A (en) * 1957-02-15 1959-07-28 Thunderbird Engineering Compan Fluid pump
US3230892A (en) * 1963-09-19 1966-01-25 Burns Nathan Reciprocating mechanism with fluid conducting means
DE1528357A1 (de) * 1964-04-06 1969-09-25 Partner Ab Anordnung fuer Schmieroelpumpen
FR1416519A (fr) * 1964-09-23 1965-11-05 Cem Comp Electro Mec Pompe à faible débit, du type à piston plongeur animé d'un mouvement de rotation
GB1411844A (en) * 1973-03-03 1975-10-29 Birmingham Small Arms Co Ltd Lubricating pumps for internal combustion engines
US3914073A (en) * 1974-12-17 1975-10-21 Ralph L Fusco Printing ink pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108843558A (zh) * 2018-06-15 2018-11-20 深圳市益思精密五金有限公司 高压恒流泵、其柔性柱塞杆及降低压力脉动的方法

Also Published As

Publication number Publication date
CH679172A5 (fr) 1991-12-31
JPH03124976A (ja) 1991-05-28
US5102310A (en) 1992-04-07

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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