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EP0226737A2 - Mécanisme de commande pour pompe, notamment pompe de dosage de liquides - Google Patents

Mécanisme de commande pour pompe, notamment pompe de dosage de liquides Download PDF

Info

Publication number
EP0226737A2
EP0226737A2 EP86114115A EP86114115A EP0226737A2 EP 0226737 A2 EP0226737 A2 EP 0226737A2 EP 86114115 A EP86114115 A EP 86114115A EP 86114115 A EP86114115 A EP 86114115A EP 0226737 A2 EP0226737 A2 EP 0226737A2
Authority
EP
European Patent Office
Prior art keywords
storage
pump
tappet
drive device
eccentric
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.)
Granted
Application number
EP86114115A
Other languages
German (de)
English (en)
Other versions
EP0226737B1 (fr
EP0226737A3 (en
Inventor
Rudi Siller
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.)
Cillit Wassertechnik & Co GmbH
Original Assignee
Cillit Wassertechnik & Co GmbH
Cillichemie Ernst Vogelmann 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 Cillit Wassertechnik & Co GmbH, Cillichemie Ernst Vogelmann GmbH and Co filed Critical Cillit Wassertechnik & Co GmbH
Priority to AT86114115T priority Critical patent/ATE47203T1/de
Publication of EP0226737A2 publication Critical patent/EP0226737A2/fr
Publication of EP0226737A3 publication Critical patent/EP0226737A3/de
Application granted granted Critical
Publication of EP0226737B1 publication Critical patent/EP0226737B1/fr
Expired 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/06—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means including spring- or weight-loaded lost-motion devices
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2142—Pitmans and connecting rods
    • Y10T74/2154—Counterbalanced
    • Y10T74/2158—Spring

Definitions

  • the invention relates to a drive device for a pump, in particular a liquid metering pump, of the type specified in the preamble of claim 1.
  • Known metering pumps with an electromotive drive of this type have a reduction gear via which an eccentric or cam disk is driven, which in turn acts on the pump tappet.
  • the return stroke is carried out with a return spring.
  • a stroke limiter can also be provided, which is adjustable from the outside.
  • This principle can be used for both diaphragm pumps and piston pumps.
  • the motor power is only used to advance the pump tappet.
  • the engine is turned back empty on the return stroke.
  • the drive motor must be designed with regard to its power for the peak load. In the known metering pumps, however, this means that the available engine power remains unused over a large part of the stroke cycle, especially during the return stroke, so that on average an oversizing of the motor is required.
  • the invention is therefore based on the object of improving the known drive device to the effect that, despite the same peak load in the feed phase, a smaller motor dimensioning is made possible.
  • the solution according to the invention is based on the idea that during the return phase of the pump tappet motor energy is stored in the form of potential mechanical energy which can be used in the feed phase to support the motor force. Accordingly, an arrangement for storing mechanical energy is provided according to the invention, which can be charged to a state of higher potential energy in the course of the return phase of the pump tappet by the motor-driven eccentric or cam disc and through which a force directed against the force of the return spring can be transmitted to the pump tappet.
  • the storage arrangement has at least one spring under prestress as the storage member.
  • a compression spring in particular a disk spring package, is particularly suitable for this.
  • Coil springs, torsion springs or spiral springs are also possible as spring elements.
  • the storage arrangement expediently has a storage plunger which can be displaced by the motor-driven disk in opposition to the force of the storage member and a disk which is arranged between the pump tappet and the storage tappet bridging coupling link.
  • the coupling member keeps the mutually facing end faces of the two tappets acting against the disk at a distance from one another which is slightly larger, preferably by about 0.05 to 0.1 mm, than the disk diameter.
  • An optimal adaptation of the storage arrangement to the pump load is achieved if the force that can be transmitted from the storage arrangement to the pump tappet corresponds to approximately 25 to 50% of the peak load and if the force to be used by the motor-driven disk to load the storage arrangement is a maximum of approximately 50 to 75% of the corresponds to the peak load occurring on the side of the pump tappet.
  • Such a drive device can provide about 30% more pump power for a given power of the electric motor.
  • a correspondingly smaller and therefore cheaper motor than previously can be used for a given pump output.
  • the drive device shown in the drawing essentially consists of a motor-driven eccentric disc 10, a pump plunger 14 which can be displaced by the eccentric disc against the force of a return spring 12, and an arrangement 16 for storing mechanical energy.
  • the storage arrangement 16 has a storage tappet 20 guided in a guide 18 fixed to the housing and a set of disc springs 26 which are arranged on the tappet 20 and are preloaded between a tappet shoulder 22 and a shoulder 24 fixed to the housing.
  • a coupling member 28 is integrally formed on the storage plunger 20, which cages-like grips around the eccentric disk with its cantilevers 29 and can be abutted with its end face 30 against an annular shoulder 32 of the pump plunger 14.
  • the end face 30 of the coupling member 28 is formed by an annular stop shoe 30 'which is guided on the rear part 14' of the pump tappet 14.
  • the eccentric disk 10 which consists of an inner disk 34 and an eccentric disk 36 supported on this ball bearing 36, is mounted with its eccentric axis of rotation 38 on the output shaft of an electric gear or stepping motor, not shown.
  • This axis of rotation 38 is arranged in a fixed position between the two tappet guides 18, 40.
  • the eccentric disc is located between the mutually facing end faces 42, 44 of the two plungers 14, 20, against which it strikes alternately with its lateral surface 46, depending on the rotational position.
  • the coupling member 28 of the storage tappet 20, which abuts against the annular shoulder 32 of the pump tappet 14, defines a distance between the two end faces 42, 44, which is slightly larger, preferably about 0.05 to 0.1 mm, larger than the disk diameter than the ram stroke is.
  • the eccentric disk 10 In the initial state shown in FIG. 1, the eccentric disk 10 is maximally deflected towards the storage tappet 20 and bears centrally against its end face 44.
  • the spring assembly 26 is compressed between its two shoulders 22, 24 to its smallest extent and has the maximum potential energy in the course of a cycle.
  • the pump plunger 14 bears against the limiting pin 48 with its stop surface 52. Both the eccentric disc 10 and the coupling member 28 are lifted off the associated end or shoulder surface 32, 42 of the pump tappet.
  • the storage tappet 20 moves while expanding the spring assembly in the direction of the pump tappet 14 until the coupling member 28 with its stop shoe 30 'against the annular shoulder 32 of the pump tappet 14 strikes and this lifts under the action of the force of the spring assembly 26 against the force of the return spring 12 from the stop 50.
  • the counterforce to be overcome increases until it finally corresponds to the force transmitted by the spring assembly 26. From this point on, the eccentric disc 10 lifts off from the end face 44 of the storage tappet 20 and strikes against the rear end face 42 of the pump tappet 14, so that the missing force is now transmitted from the motor to the pump tappet 14.
  • spring assembly 26 contributes to a certain extent due to its pretensioning to overcome the counterforce.
  • spring properties and preload are selected so that when the peak load in the state of FIG. 3 is reached, approximately 25 to 50% of the feed force acting on the pump tappet 14 is still transmitted by the storage arrangement 16.
  • the pump plunger 14 is gradually moved back under the action of the return spring 12 until it strikes the limiting pin 48. From the point of the equilibrium of forces, but at the latest after the stop of the pump tappet 14, the eccentric disc 10 lifts off the end face 42 of the pump tappet 14 and acts on the end face 44 of the storage tappet 20. In this phase, the spring assembly 26 is compressed using motor power and brought to a state of higher potential energy.
  • the spring properties are expediently chosen so that the peak force to be applied in the state of FIG. 1 corresponds to approximately 50 to 75% of the peak load occurring on the side of the pump tappet.
  • the eccentric shaft 10 ' is rotatably mounted on an upper and a lower, not shown, lower ball bearing 64 with the help of the motor 66 and the reduction gear 68 about the eccentric axis 38.
  • the pump tappet 14 is under the action of the return spring designed as a helical compression spring 12 with its end face 42 against the outer ring 36 'of the ball bearing 60 on its outer surface 46', while the storage tappet 20 under the action of the helical compression spring 26 serving as a storage member with its end face 44 against the lateral surface 46 '' of the outer ring 36 '' of the ball bearing 62 abuts.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Loading And Unloading Of Fuel Tanks Or Ships (AREA)
EP86114115A 1985-10-19 1986-10-11 Mécanisme de commande pour pompe, notamment pompe de dosage de liquides Expired EP0226737B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86114115T ATE47203T1 (de) 1985-10-19 1986-10-11 Antriebsvorrichtung fuer eine pumpe, insbesondere eine fluessigkeitsdosierpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853537297 DE3537297A1 (de) 1985-10-19 1985-10-19 Antriebsvorrichtung fuer eine pumpe, insbesondere eine fluessigkeitsdosierpumpe
DE3537297 1985-10-19

Publications (3)

Publication Number Publication Date
EP0226737A2 true EP0226737A2 (fr) 1987-07-01
EP0226737A3 EP0226737A3 (en) 1987-10-21
EP0226737B1 EP0226737B1 (fr) 1989-10-11

Family

ID=6283996

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86114115A Expired EP0226737B1 (fr) 1985-10-19 1986-10-11 Mécanisme de commande pour pompe, notamment pompe de dosage de liquides

Country Status (6)

Country Link
US (1) US4753118A (fr)
EP (1) EP0226737B1 (fr)
JP (1) JPS62118071A (fr)
AT (1) ATE47203T1 (fr)
CA (1) CA1255153A (fr)
DE (2) DE3537297A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8807203U1 (de) * 1988-06-02 1988-08-04 Lang Apparatebau GmbH, 8227 Siegsdorf Motorantrieb für eine Pumpe, insbesondere eine Flüssigkeitsdosierpumpe

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4005110C1 (fr) * 1990-02-17 1991-07-25 Philips Patentverwaltung Gmbh, 2000 Hamburg, De
JPH0561466U (ja) * 1992-01-27 1993-08-13 自動車電機工業株式会社 プランジャポンプ
US6164924A (en) * 1998-09-01 2000-12-26 Oil-Rite Corporation Piston and drive assembly for use in a pump
DE102004026584A1 (de) * 2004-05-28 2005-12-22 Robert Bosch Gmbh Kolbenpumpe mit verringertem Verschleiß
NL1033204C2 (nl) * 2007-01-10 2008-07-11 Weir Minerals Netherlands Bv Enkelwerkende verdringerinrichting.
DE102011089516B4 (de) 2011-12-22 2021-08-12 Robert Bosch Gmbh Pumpe zum Rücksaugen für ein flüssiges Abgasnachbehandlungsmittel, Dosieranordnung und Verfahren zum Dosieren und Rücksaugen
DE102016013739A1 (de) * 2015-12-08 2017-06-08 Wabco Gmbh Doppelkolbenkompressor einer Druckluft-Versorgungseinrichtung
US20240141881A1 (en) * 2022-10-31 2024-05-02 Stanadyne Operating Company Llc Energy accumulator for piston-type fuel pump

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2287627A (en) * 1940-01-23 1942-06-23 Job F Malsbary Diaphragm pump
CH292182A (de) * 1951-02-10 1953-07-31 Siemens Ag Einrichtung zur Umwandlung einer Drehbewegung in eine hin- und hergehende Bewegung mit Hilfe eines Exzenters.
GB881430A (en) * 1959-04-16 1961-11-01 Norton Tool Company Ltd Improvements in or relating to pumps, compressors and engines
GB1221827A (en) * 1968-04-18 1971-02-10 Girling Ltd A new or improved reciprocating pump for liquids
DE2826045A1 (de) * 1977-12-01 1979-06-13 Lear Siegler Inc Kolbenpumpe
DE3013146A1 (de) * 1979-04-04 1980-10-30 Metering Pumps Ltd Antriebsmechanismus fuer zumesspumpe
DE3031067A1 (de) * 1979-09-19 1981-04-09 Seeger Corp., Saint Paul, Minn. Dosierpumpe fuer zwei komponenten
FR2565653A1 (fr) * 1984-06-12 1985-12-13 Milton Roy Dosapro Mecanisme d'entrainement d'un organe dans un mouvement alternatif a course variable

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1697786A (en) * 1926-12-02 1929-01-01 Ole M Sholberg Pump-counterbalancing means
US1775653A (en) * 1928-06-14 1930-09-16 William J Mundt Pump-operating mechanism
FR771337A (fr) * 1934-04-06 1934-10-05 Lescuyer & Villeneuve Ets Mécanisme de commande à excentriques et ses applications
US3067624A (en) * 1959-04-16 1962-12-11 Norton Tool Company Ltd Pumps, compressors and engines
FR1241097A (fr) * 1959-11-26 1960-09-09 Procédé de liaison entre les pistons et l'arbre d'une machine à pistons en étoile à plusieurs plans de pistons et machine pour sa mise en ceuvre
CH405078A (de) * 1962-03-28 1965-12-31 Licentia Gmbh Kolbenpumpe
DE3338112A1 (de) * 1983-10-20 1985-05-09 Bran & Lübbe GmbH, 2000 Norderstedt Kolbenpumpe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2287627A (en) * 1940-01-23 1942-06-23 Job F Malsbary Diaphragm pump
CH292182A (de) * 1951-02-10 1953-07-31 Siemens Ag Einrichtung zur Umwandlung einer Drehbewegung in eine hin- und hergehende Bewegung mit Hilfe eines Exzenters.
GB881430A (en) * 1959-04-16 1961-11-01 Norton Tool Company Ltd Improvements in or relating to pumps, compressors and engines
GB1221827A (en) * 1968-04-18 1971-02-10 Girling Ltd A new or improved reciprocating pump for liquids
DE2826045A1 (de) * 1977-12-01 1979-06-13 Lear Siegler Inc Kolbenpumpe
DE3013146A1 (de) * 1979-04-04 1980-10-30 Metering Pumps Ltd Antriebsmechanismus fuer zumesspumpe
DE3031067A1 (de) * 1979-09-19 1981-04-09 Seeger Corp., Saint Paul, Minn. Dosierpumpe fuer zwei komponenten
FR2565653A1 (fr) * 1984-06-12 1985-12-13 Milton Roy Dosapro Mecanisme d'entrainement d'un organe dans un mouvement alternatif a course variable

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8807203U1 (de) * 1988-06-02 1988-08-04 Lang Apparatebau GmbH, 8227 Siegsdorf Motorantrieb für eine Pumpe, insbesondere eine Flüssigkeitsdosierpumpe

Also Published As

Publication number Publication date
EP0226737B1 (fr) 1989-10-11
JPS62118071A (ja) 1987-05-29
US4753118A (en) 1988-06-28
DE3666267D1 (en) 1989-11-16
ATE47203T1 (de) 1989-10-15
CA1255153A (fr) 1989-06-06
DE3537297A1 (de) 1987-04-23
EP0226737A3 (en) 1987-10-21

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