EP1331393B1 - Pompe solénoide à transmission hydraulique - Google Patents

Pompe solénoide à transmission hydraulique Download PDF

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Publication number
EP1331393B1
EP1331393B1 EP03000892A EP03000892A EP1331393B1 EP 1331393 B1 EP1331393 B1 EP 1331393B1 EP 03000892 A EP03000892 A EP 03000892A EP 03000892 A EP03000892 A EP 03000892A EP 1331393 B1 EP1331393 B1 EP 1331393B1
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EP
European Patent Office
Prior art keywords
piston
drive system
hydraulic drive
oil
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.)
Expired - Lifetime
Application number
EP03000892A
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German (de)
English (en)
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EP1331393A3 (fr
EP1331393A2 (fr
Inventor
Robert Poirtel
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Inventas AG
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Inventas AG
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Publication date
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Publication of EP1331393A3 publication Critical patent/EP1331393A3/fr
Application granted granted Critical
Publication of EP1331393B1 publication Critical patent/EP1331393B1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
    • F04B17/042—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the solenoid motor being separated from the fluid flow

Definitions

  • the invention relates to a hydraulic drive system with a Schwingankerkolbenpumpe according to the preamble of patent claim 1.
  • a magnet surrounds a pump housing and generates an axial magnetic field which moves a sealingly displaceably mounted in the pump housing piston in a working space.
  • the forward drive of the piston is effected by the applied magnetic field, while the return is effected by a corresponding return spring which acts on the piston.
  • this known piston pump according to the Schwingankerkal results in the advantage of a relatively small structure, so that this known pump can be used for example as a fuel delivery pump.
  • this pump is designed as a hydraulic drive system, so that the pump acts as an actuator with a working piston, for example.
  • an electromagnetic actuator utilizing a fluid pressure generated by an electromagnetic pump.
  • a control member is provided in the pump that is removable in response to fluid pressure when the fluid is forced into a second chamber from a first chamber.
  • the removable control part can operate a valve part or the like, which with this in an open-loop or a Proportional control associated with a long stroke in a Proven way.
  • a pump including a boost pressure increasing device including a cylinder connected between the suction side and the exhaust side of the pump.
  • a slidable and reciprocable piston mating with the cylinder and a passageway communicates between the suction and discharge side sides divided by the piston.
  • An adjustable spring biases the piston against the outlet side and a valve mechanism separates the outflow of the fluid from the outlet side to the suction side, the outflow occurring in response to movement of the piston to the suction side.
  • the EP 0 065 011 A discloses a hydraulic valve drive, wherein the hydraulic pressure is generated by an electromagnetic pump.
  • the drive includes an actuator for the simultaneous drive of a plurality of such valves.
  • the device opens and closes a plurality of valves connected in series with a main passage via a single valve drive device and can drive a freely selectable proportional valve to achieve a safe pumping function.
  • the invention is therefore the object of developing a hydraulic drive system such that an exchange of components is ensured due to a modular design.
  • the invention is characterized by the features of claim 1.
  • a backflow system is described, which is arranged between the pump piston of the pump system and the working piston of the hydraulic drive system.
  • a specific valve control is claimed as essential to the invention.
  • a magnetically moved valve is described with a second coil instead of a mechanically moving valve, which essentially consists of a magnetically movable control piston.
  • One of the possible variants and advantage of the system is, through different dimensions of the armature piston flow and pressure to vary.
  • the design allows a very simple replacement of the magnetic coil body without interfering with the closed drive part.
  • By using different coils, adapted electrical voltage and power requirements to the drive can be achieved.
  • the entire system can be modular. Both pump part and working cylinder part are self-contained units and can be connected together in a modular system.
  • linear drive can be used separately as a non-claimed pump.
  • the scope extends to all applications where linear motion is required and any lifting and force requirement is to be covered.
  • the suction can include an expansion element (spring-loaded piston, diaphragm, etc.), which applies a constant static pressure and thus on the one hand prevents harmful air formation in the suction and on the other hand takes into account the expansion behavior.
  • an expansion element spring-loaded piston, diaphragm, etc.
  • FIG. 1 In general, a rocking armature piston pump is shown, the pump housing is referred to as a tubular body 3.
  • the magnetic drive takes place via a magnetic coil 7, which is radially on the outer circumference of the Tube body 3 is arranged.
  • the tubular body is interrupted approximately in the middle region of the magnetic coil 7 by a non-magnetic central part 8.
  • a spring-loaded inlet valve 4 is arranged, which sucks the pressure oil from a suction chamber 19 arranged at the rear end side.
  • the suction chamber 19 consists essentially of a closure ring 51, which forms the suction chamber 19 inside, wherein for biasing the pressure oil in the suction chamber 19, a displaceable pressure piston 52 is arranged, which is displaced under the force of a spring 53 against the suction 19. In this way, it is always ensured that the pressure oil from the suction chamber 19 is biased in the direction of arrow 66 and flows over an associated inlet bore 29 to the inlet valve 4.
  • the inlet valve and an associated transverse bore 25 are hereby mounted in the rest in a fixed bearing part 17 in the tubular body 3.
  • the pressure oil flowing in via the inlet valve 4 flows into the working space 18 behind the piston 6.
  • This piston consists essentially of a front piston head and a firmly attached thereto piston rod 27 which carries at its rear end a transverse bore which is aligned in the position shown with a housing-fixed transverse bore 25 in the bearing part 17.
  • the piston head of the piston 6 is biased by means of a return spring 9 in the drawn rest position and acts in the working position against a fixed housing stop 31, which is part of a likewise housing-fixed bearing part 30.
  • control piston 11 radially outwardly forms a liquid-conducting gap 22, so that the pressure oil flows through this gap 22 axially forward into the arranged in front of the piston 11 piston chamber 21.
  • the piston 11 is in this case held by a return spring 15 in its closed position and is moved with appropriate action with a pressure surge in the axial direction forward against the force of the return spring 15.
  • This piston 11 is fixedly connected as a unit with a pipe section 12, which engages in an associated guide bore 68.
  • the piston 11 carries on its front side an axially forward approach with a return flow 13, which is associated with a counterbore 23 in the tubular body 3.
  • the piston 11 together with the front-side front projection and the rear pipe section 12 is completely penetrated by an axial bore.
  • the pressure oil is conveyed by the connecting piece 34 in the direction of arrow 43 into the rear cylinder chamber 43 and acts there on the back of the piston part 41, which is sealingly guided in the cylinder chamber 39.
  • the housing-fixed transverse bore 25 connects the piston rod 27 arranged in the movable piston 6, so that the oil enters via the arranged in the piston rod 27 transverse bore in the housing-fixed longitudinal bore 26 and flows from there into the storage room 19.
  • a device which provides a certain, by appropriate dimensioning of the parameters involved, spring force and effective flow of the oil, adjustable dead time for the release of the return line.
  • spring force and effective flow of the oil adjustable dead time for the release of the return line.
  • an actuator has been developed according to the invention, which is designed in the form of a piston 11 with valve function.
  • a large part of the per stroke of the pump piston 6 to be conveyed oils is conveyed through the disposed in the piston 11 through hole 12 (pipe section), which due to the effective cross section, the oil by the significantly lower resistance to the gap 22 towards the working piston first examined. Only when the piston 11 is immersed with its return flow opening 13 in the counterbore 23, oil will continue to flow through the gap 22 in the space 21 and from there into the connecting piece 34 back to the working piston.
  • the magnetic ring 28 may also form a unitary body together with the piston head and the piston rod.
  • the modular structure (pluggability) of the two parts is preferred because it allows easy replacement of the front drive system 35. This allows different working piston 1 can be used with different strokes.
  • connection of the two parts takes place in the rest by an attached on the front side of the cylinder liner 40 screw 49 which is screwed into an associated threaded bushing 50 on the pump housing of the tubular body 3.
  • the front working piston 1 is otherwise firmly connected to a piston neck 45 which is sealingly guided in the cylinder liner 40.
  • the piston boss 45 forms a reduced diameter neck by providing a vent bore 46. This vent hole opens into the atmosphere.
  • the stop of reduced diameter cooperates with a housing-fixed stop 47 in the cylinder liner 40.
  • the working piston 1 is sealingly guided in the longitudinal direction in a sealing manner in a front-side guide part 48 of the cylinder head 40.
  • the working piston 1 can move according to the operation of the metering and pump different fluids displace.
  • FIG. 2 shows generally the front view of the arrangement, where it can be seen that the magnetic coil 7 centrally forms a réellebohrugn 54 which is slid over the tubular body 3 of the pump system.
  • FIGS. 3 and 4 now show modifications of the control valve system FIG. 1 , Here is how the in FIG. 1 shown piston 11 can be replaced by other controls.
  • FIG. 3 in this case shows a magnetically driven control piston 56 which is acted upon by its own magnetic coil 55.
  • a magnetic separation 65 is again arranged in the pump housing in order to avoid a short circuit of the magnetic field.
  • an axial through hole 72 is provided in the control piston 56, which is associated with an associated, spring-loaded valve 73.
  • This valve opens into a through hole 74 and this in turn into the front piston chamber 20 of the pump.
  • valve holes complementary to each other in the transverse bearing bores 25 in the housing-fixed bearing part 18 and the associated transverse bore in the piston rod 27 is then no longer necessary.
  • FIG. 4 shows a further variant of a corresponding piston control, wherein also a magnetically movable spool 57 is used, which is driven by a magnetic coil 55.
  • the bearing member 30 Before the piston chamber 20, the bearing member 30 is arranged, which has the valve bore 33 through which the pressure oil generated by the piston, not shown, in the direction of arrow overcomes the pressure valve 5.
  • This pressure oil first enters the working space 75 in front of the spool 57, wherein the spool is held by a return spring 58 in its left end stop.
  • the spool 57 If, however, the spool 57 is activated by the solenoid, then it takes its first control position. In this position, the pressure oil in the working space 55 flows via the center channel 59 and an associated transverse bore into a housing-side transverse bore 76 adjoining it, from where the pressure oil flows in the direction of the arrow 77 into the drive system 35.
  • valve control described in the exemplary embodiment in conjunction with the piston rod 27 can be dispensed with and the entire control of the return flow already takes place in the region of the control slide 57.
  • the other displacement position of the spool 57 allows a comparison of the housing-fixed transverse bore 64 to an associated, arranged in the spool, transverse bore 63rd
  • FIG. 5 shows a further variant of the present invention, which compared to the embodiment in FIG. 3 equipped with a magnetically movable spool and modified pump piston.
  • spool 57 is the anchor part with piston 27, in contrast to previously mentioned embodiments in the suction chamber 19 and conveys the oil via the inlet valve 4 in the pressure chamber 20 and from there via the Druckvenitl 5 via the spool 57 in a working cylinder.
  • the special feature of this embodiment is that while the pressure chamber 20, the inlet valve 4, the pressure valve 5 and the return flow channel 24 can be integrated in one component, and thus consuming return flow channels in the tubular body 3 can be omitted.
  • the system comprises in a first embodiment, four pistons, which are responsible for the oil supply and power transmission. These are the piston 52, which is responsible for the permanent pressurization of the system, and thus ensures that the closed oil system works almost air entrapment, the piston 6, which is responsible for the compression and promotion of the oil, the piston 11, the is responsible for controlling the flow of oil, and finally the working piston 1 with its effective piston part 41 for the effective linear movement to be generated.
  • a targeted, adjustable in their speed provision of the working piston is carried out by dimensioning the pipe cross-section of the oil. By influencing the cross section is controlled according to the refluxing volume flow, which can ultimately affect the return speed.
  • the training as a double-acting cylinder is done by means of two appropriately controllable oil passages in the system designed as a pipe.
  • the oil in the front / outer part of the cylinder 39 is, caused by the outward movement of the piston member 41, pressed by the transverse bore 71 in the return system and so immediately fed back to the suction chamber 19, whereby the oil circuit is closed air-free.
  • the oil flow takes place in the reverse direction.
  • An influence on the feed of the working piston 1 is also provided according to the technical teaching of the present invention. These can be done by adjusting the magnetic coil force on the piston 6 promoting the oil. The control is carried out in such a way that the maximum feed rate at 100% delivery stroke takes place, and a reduction of the delivery to corresponding less than 100% accordingly also a reduced feed movement result, which also reduces their speed due to the known relationships.
  • the reduction of the delivery stroke takes place through the use of a correspondingly weaker selected magnetic coil 7, which is able to move the piston 6 only partially along its maximum working travel.
  • control of the piston can also be done by means of spring force and / or magnetic force.
  • a spool valve 57 causes the oil supply to feed, lock and return the working piston 1.
  • the spool can be operated by means of oil pressure and / or spring force and / or magnetic force to exert the desired control function.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Control Of Transmission Device (AREA)
  • Reciprocating Pumps (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (12)

  1. Système d'entraînement hydraulique à pompe à piston solénoïde avec un entraînement magnétique, dans lequel il est prévu à la suite d'une pompe à piston de dosage (3), sur le corps de celle-ci, une douille cylindrique (40) qui est directement étanche, qui est dirigée axialement et dans laquelle au moins un piston moteur (1) mobile par voie hydraulique est apte à coulisser, de sorte qu'ils forment ensemble un corps d'élément continu, et il est prévu pour contraindre l'huile sous pression dans l'espace d'aspiration (19) un piston de pression (52) apte à coulisser qui est déplacé vers ledit espace d'aspiration (19) sous la force d'un ressort (53), caractérisé en ce que le système d'entraînement hydraulique (35) est apte à être relié de manière amovible au corps tubulaire (3) du corps de pompe par l'intermédiaire d'éléments de liaison (37) et (34).
  2. Système d'entraînement hydraulique selon la revendication 1, caractérisé en ce que la bobine magnétique (7 ; 55) est disposée sur la circonférence extérieure du corps de pompe de manière à pouvoir être remplacée facilement.
  3. Système d'entraînement hydraulique selon la revendication 1 ou 2, caractérisé en ce que l'huile pompée grâce à la pompe à piston de dosage (3) circule dans un circuit fermé sans air.
  4. Système d'entraînement hydraulique selon l'une des revendications 1 à 3, caractérisé en ce que le circuit pour l'huile entraîne le piston moteur (1) suivant une fonction à double effet.
  5. Système d'entraînement hydraulique selon l'une des revendications 1 à 4, caractérisé en ce que l'avance du piston moteur (1) peut être commandée à l'aide de l'intensité magnétique de la bobine magnétique (7).
  6. Système d'entraînement hydraulique selon l'une des revendications 1 à 5, caractérisé en ce que le rappel du piston moteur (1) peut être réglé et/ou bloqué grâce à la commande du débit volumique d'huile, à l'aide d'actionneurs appropriés (11 ; 56 ; 57).
  7. Système d'entraînement hydraulique selon l'une des revendications 1 à 6, caractérisé en ce que l'actionneur (11 ; 56 ; 57) est actionné à l'aide d'un aimant et/ou d'une pression d'huile et/ou d'une force de ressort.
  8. Système d'entraînement hydraulique selon l'une des revendications 1 à 7, caractérisé en ce que la course de chaque élément de refoulement ou de commande (6 ; 11 ; 56 ; 57) du système peut être réglée grâce à un paramétrage approprié des éléments actifs de telle sorte que ledit élément ne heurte pas, côté frontal, l'élément associé.
  9. Système d'entraînement hydraulique selon l'une des revendications 1 à 8, caractérisé en ce que les conduits d'amenée et de retour pour l'huile passent en partie dans les parois du corps tubulaire (3) et du cylindre moteur (40).
  10. Système d'entraînement hydraulique selon l'une des revendications 1 à 9, caractérisé en ce que le liquide sous pression est fourni par la pompe à piston solénoïde (3) directement dans le sens axial et est amené dans le corps de pompe (40) du système d'entraînement hydraulique grâce à une communication fluidique.
  11. Système d'entraînement hydraulique selon l'une des revendications 1 à 10, caractérisé en ce que la pompe à piston solénoïde présente une construction modulaire.
  12. Système d'entraînement hydraulique selon l'une des revendications 1 à 11, caractérisé en ce qu'il est possible simplement de transmettre des puissances d'entraînement différentes pour le piston de pompe ou de changer des bobines défectueuses sans qu'il faille démonter entièrement le système.
EP03000892A 2002-01-17 2003-01-16 Pompe solénoide à transmission hydraulique Expired - Lifetime EP1331393B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10201790A DE10201790A1 (de) 2002-01-17 2002-01-17 Hydraulisches Antriebssystem mit Schwinganker-Kolbenpumpe
DE10201790 2002-01-17

Publications (3)

Publication Number Publication Date
EP1331393A2 EP1331393A2 (fr) 2003-07-30
EP1331393A3 EP1331393A3 (fr) 2003-12-03
EP1331393B1 true EP1331393B1 (fr) 2008-03-12

Family

ID=7712475

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03000892A Expired - Lifetime EP1331393B1 (fr) 2002-01-17 2003-01-16 Pompe solénoide à transmission hydraulique

Country Status (4)

Country Link
EP (1) EP1331393B1 (fr)
AT (1) ATE389112T1 (fr)
DE (2) DE10201790A1 (fr)
ES (1) ES2304473T3 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004042208B4 (de) * 2004-09-01 2014-07-17 Volkswagen Ag Kolbenpumpe zur Förderung eines Fluids

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1049314A (en) * 1965-01-01 1966-11-23 Int Standard Electric Corp Electromagnetic position controlling arrangement
JPS5416703A (en) * 1977-07-08 1979-02-07 Taisan Kougiyou Kk Boosting delay apparatus for solenoid plunger pump and so on
WO1982001576A1 (fr) * 1980-10-31 1982-05-13 Uchihama Tetsuo Dispositif de vanne entrainee par une pompe
EP0065012A4 (fr) * 1980-10-31 1983-03-15 Yamatake Honeywell Co Ltd Dispositif d'actionnement electromagnetique.
DE4224084A1 (de) * 1992-07-22 1994-04-14 Manfred Schienle Elektromagnetisch antreibbare Pumpe

Also Published As

Publication number Publication date
EP1331393A3 (fr) 2003-12-03
EP1331393A2 (fr) 2003-07-30
DE50309351D1 (de) 2008-04-24
DE10201790A1 (de) 2003-11-06
ATE389112T1 (de) 2008-03-15
ES2304473T3 (es) 2008-10-16

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