WO1994002741A1 - Pompe a entrainement electromagnetique - Google Patents

Pompe a entrainement electromagnetique Download PDF

Info

Publication number
WO1994002741A1
WO1994002741A1 PCT/EP1993/001955 EP9301955W WO9402741A1 WO 1994002741 A1 WO1994002741 A1 WO 1994002741A1 EP 9301955 W EP9301955 W EP 9301955W WO 9402741 A1 WO9402741 A1 WO 9402741A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
valve
piston
chamber
armature
Prior art date
Application number
PCT/EP1993/001955
Other languages
German (de)
English (en)
Inventor
Manfred Schienle
Eckehart Schulze
Original Assignee
Manfred Schienle
Eckehart Schulze
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 Manfred Schienle, Eckehart Schulze filed Critical Manfred Schienle
Priority to DE59307899T priority Critical patent/DE59307899D1/de
Priority to EP93917625A priority patent/EP0651858B1/fr
Publication of WO1994002741A1 publication Critical patent/WO1994002741A1/fr

Links

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
    • F04B17/046—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids the fluid flowing through the moving part of the motor

Definitions

  • the invention relates to a magnetically drivable pump as a pressure supply unit for a hydraulic consumer, according to the preamble of patent claim 1.
  • the known pump is designed as a single-piston pump, in which a double-stroke magnet system is provided as the drive system, which comprises two field windings of the same design arranged alongside one another along a central axis. These field windings coaxially surround a movable armature, which can be driven by alternating current supply to the two field windings to the current flow, which is carried out by the pump piston with to-and-fro movements, in the one with a volume increase of a pump chamber linked direction of movement of the piston via an inlet check valve, the pump chamber is filled from the pressure medium reservoir and in the opposite direction of movement of the pump associated with the pumping operation of the pump pressure medium is conveyed via an outlet check valve from the pump chamber to a pressure outlet of the pump.
  • a double-stroke magnet system is provided as the drive system, which comprises two field windings of the same design arranged alongside one another along a central axis.
  • These field windings coaxially surround a movable armature, which can be driven
  • the inlet check valve is at one end of the Housing, the outlet check valve is arranged at the opposite end of the housing.
  • An elongated tube is moved back and forth by means of the armature, in which a check valve, which in turn is designed as a non-return valve, is arranged centrally, which locks in the delivery stroke and opens in the suction stroke. Accordingly, liquid is displaced in the filling stroke via the shut-off valve into the tube section which is arranged pointing towards the outlet valve.
  • liquid also flows in via the inlet valve into the pre-filling space of the tube, which extends up to the shut-off valve, from which liquid is then displaced in the subsequent filling stroke via the opened shut-off valve into the delivery area of the pump.
  • the pump is designed as a double-piston pump with pump pistons and pump chambers of the same design arranged axially on both sides of the armature, the pump chambers being connected to a common pressure outlet via an outlet check valve in each case;
  • the pump pistons have permanently communicating, central through-channels in communication with the pump chambers, which are connected via inlet check valves arranged centrally in the armature to an inlet chamber arranged centrally in the armature, which via at least one radial channel with an outer groove of the armature in communicating connection is formed, which within its axial width is permanently overlapping with the opening cross-section of a radial feed pipe which is connected to the pressure medium storage container, and it is also the central channel within which the armature can be moved back and forth, kept permanently in communicating connection with the storage container.
  • the pump according to the invention designed in this way conveys at least the following advantages:
  • both the double-stroke magnet system and the pump arrangement ensures that the armature in operation of the pump, while its excitation windings are alternately energized in time with an alternating current frequency, always "oscillates" around a central position, which with optimal Exploitation of favorable, small air gap widths in the respective attracting magnet system goes hand in hand. While one part pump is pumping, the other is filled with pressure medium. As a result, the electrical power consumption of the field windings is optimally used for the conversion into hydraulic conveying capacity.
  • the frequency and / or the current intensity of the current to be alternated can be adjusted so that the delivery rate of the pump and also its outlet pressure can be controlled in a simple manner by changing these parameters.
  • the pump itself can be designed in a simple manner by suitable selection of the cross-sectional dimensions of the pump pistons and the design possible by suitable design of the double-stroke magnet system for suitable piston strokes at defined delivery rates and output pressures.
  • At least one of the pump pistons and one of the excitation windings of the pump are used as a valve body or switching winding of a relief valve designed as a solenoid valve, which, when this winding is excited, connects the pressure output of the pump with its pressure medium storage container when the winding is excited Flow position arrives and otherwise blocks, so that a rapid pressure reduction in a consumer connected to the pump can be brought about by electrical control of this valve.
  • the excitation winding of the double-stroke magnet system which is used as the switching winding of the relief valve, is acted upon by a current which is greater than the excitation current strength used for the pumping operation in order to switch on its relief position, the relief position being that of a Pump piston formed valve body of the relief valve is moved to a position in which the piston is a defined distance further away from its basic position assumed in the de-energized state of the excitation windings than in the reversal points of its filling and delivery strokes carried out in pump operation.
  • the relief valve can be designed as a simple 2/2-way valve which, in its open position, connects the pump chamber with the central channel of the master communicating with the reservoir.
  • this 2/2-way valve can be implemented in a simple manner by constructing a chamber block in the central bore of the relief valve housing, in which the Pump pistons forming the relief valve can be moved in a pressure-tight manner ar is guided, has an arranged inner groove which is connected via a relief channel to the central channel communicating with the storage container and, viewed in the axial direction, between the Pump chamber and the central channel of the Doppelhubmag ⁇ netsystem is arranged, and that the pump piston ei ⁇ ne via a radial channel with its axial channel communicating with the pump chamber communicatingly connected external groove, which, seen in the axial direction, between the
  • the inner groove of the pump chamber block and the ring end face forming an axially fixed boundary of the central channel are arranged and only overlap with the inner groove of the pump chamber block when the excitation winding coaxially surrounding the piston is energized with a direct current, the amount of which is greater than the maximum
  • a further relief valve designed as a solenoid valve which connects the pressure outlet of the pump to the pressure medium reservoir in the currentless state of its switching magnet and is otherwise blocked.
  • Such a valve ensures that the consumer becomes "depressurized" in the event of a power failure, i.e. does not carry out a work stroke, for example, and a situation of potential danger can thereby be avoided.
  • Such a normally open relief valve can be implemented in a structurally simple manner in that it comprises a valve body which is axially displaceably arranged in the outlet chamber of the respective outlet valve of the pump and consists of a magnetizable material and which can be urged by energizing a field winding in contact with a valve seat and thereby shuts off the discharge channel leading from the outlet chamber of the pump to the central channel of the double-stroke magnet system and passing through the respective chamber block, as long as the field winding is energized.
  • the valve seat of the normally open relief valve is formed by an O-ring which coaxially surrounds the outlet opening on the outlet side of the relief channel, the valve body being provided with a radial flange which can be supported on the O-ring and / or as is formed in the Auslrawkam ⁇ mer axially displaceably guided washer which can be urged against the restoring force of a return spring in contact with the O-ring.
  • the relief valve instead of such a design of the relief valve as a seat valve, it is also possible to design the relief valve as a slide valve, as is provided, for example, in a special design for the relief valve which opens when current is supplied to an excitation winding.
  • the pump is designed as a double-piston pump with pump pistons and pump chambers of the same design arranged axially on both sides of the armature, the pump chambers each having an outlet check valve to a common pressure outlet of the pumps ⁇ pe are connected, and that the pump chambers each have individually assigned inlet valves arranged in radial overflow channels, which extend between the pressure medium reservoir and one of the pump chambers, which in turn achieves low flow resistance for filling the pump chambers become.
  • inlet valves and outlet valves each associated with one of the pump chambers are integrated in a housing end block which delimits the respective pump chamber in a housing-fixed manner.
  • the object on which the invention is based is also achieved in that the pump has two annularly-shaped pump chambers which are movably delimited from one another within a central bore of its housing by an annular flange of the pump piston.
  • the overall pump consists of a hydraulic pump module and an electrically controllable drive module, which provides both manufacturing advantages and advantages in terms of a change in design, since, for example, the pump can be converted to a more powerful drive alone Replacement of the drive module is possible.
  • the valve seat of the inlet valve is the must open to fill the assigned pump chamber when the piston on the drive side, at the drive end of its bore and the valve seat of the inlet valve that has to open to fill the associated pump chamber when the pump piston is moved towards the compensation chamber, on the end of its valve bore facing this.
  • This arrangement facilitates the opening of the inlet valves for "sucking in” hydraulic fluid and is therefore expedient if the pump is operated with relatively high armature oscillation frequencies.
  • the pump according to the invention can be designed by the design of its double-stroke magnet system, the cross-sectional dimensioning of its pistons and the possible specification of its pump frequency within a wide range - the frequency with which the excitation windings of its double-stroke magnet system are alternately energized. and also by the specification or setting of the current strengths of the excitation currents with which the excitation windings are supplied with current, are optimally designed with regard to a large number of different purposes, resulting in a large number of interesting possible uses, a few of which are mentioned below as examples should:
  • Pressure supply unit for actuators of relatively low power their need-based pressure supply by means of a single - central - pressure supply unit essential for a central pump would require higher performance, but which would only be charged in rare cases according to its performance. Possible uses of this type are, for example, a hydraulic seat adjustment of chairs for medical purposes and / or of motor vehicles, drives for window regulators, sunroofs and the like.
  • Drive energy source for servo systems on motor vehicles such as servo steering and / or leveling control in motor vehicles, which currently require the use of pumps driven by the vehicle engine and which are "useless" for most of the service life of a vehicle, i.e. must be operated in idle mode.
  • FIG. 1 shows an electromagnetically drivable pump according to the invention in section along a radial plane containing the central axis of its double-stroke magnet system, in a scale representation, approximately on a scale of 1.5 / 1,
  • FIG. 2 shows details of the pump according to FIG. 1 in a sectional view corresponding to FIG. 1 but enlarged
  • FIGS. 1 and 2 are diagrams for explaining the function of the pump shown in FIGS. 1 and 2,
  • FIG. 4 shows a further exemplary embodiment of a double-piston pump according to the invention in a representation corresponding to FIG. 1 and
  • FIG. 5 shows a third exemplary embodiment of a pump according to the invention which can be driven by means of a double-stroke magnet system in a schematically simplified, greatly enlarged longitudinal sectional view.
  • FIG. 1 The electromagnetically driven device according to the invention shown in FIG. 1, to the details of which reference is expressly made, shown overall with 10 Pump is designed as a double-piston pump with two pump pistons 11 and 12 as well as pump chambers 13 and 14 and outputs 16 'and 16''assigned to them, which are connected to a common pressure output 16 to which a hydraulic consumer, for example as shown, is shown , a linear hydraulic cylinder 17 can be connected.
  • the two pump pistons 11 and 12 are firmly connected to the armature 18 of a double-stroke magnet system, which is provided as a pump drive and is generally designated 19 and which is arranged so that it can move back and forth centrally between the pump chambers 13 and 14
  • the longitudinal axis 21 of the pump chambers 13 and 14 is rotationally symmetrical and, seen in the spring-centered neutral position of the armature 18, which the armature 18 assumes when the double-stroke magnet system 19 is de-energized, also symmetrically with respect to the transverse central plane 22 which is perpendicular to the central longitudinal axis 21 is trained.
  • the armature 18 can be driven to move back and forth in the direction of the central longitudinal axis 21 in a defined manner with different deflection strokes , whereby - at given pressure against which the pump 10 must work, the delivery rate can be set in a defined manner.
  • the excitation windings are wound on the basic form of a cylindrical jacket-shaped bobbin 26 and 27, indicated only by dashed lines, which have outward-facing end flanges 28 and 29 which extend over the radial "thickness" of the excitation windings 23 and 24, whereby the coil formers and their end flanges are made of an electrically insulating plastic material.
  • the excitation windings 23 and 24 including their coil formers 26 and 27 are, apart from the excitation windings 23 and 24 each individually assigned, radially arranged annular gaps 31 and 32 - otherwise completely - enclosed by an overall ring-cylindrical jacket 33 which is magnetically conductive , ie made of magnetizable soft iron material.
  • This ring-cylindrical jacket 33 comprises, in the arrangement shown in FIG. 1, symmetrical to the transverse center plane 22 of the pump 10 and coaxial to its central longitudinal axis 21, a radially outer jacket tube 34 which encloses the field windings 23 and 24 on the outside, a radially inner, central jacket tube 36, which bears with its radially outer circumferential surface 37 on mutually adjacent sections of the bobbins 26 and 27 in the field windings 23 and 24 and with its narrow annular end faces 38 and 39 the inner boundaries of the annular gaps 31 and 32 as seen in the axial direction forms two further, radially inner casing tubes 41 and 42, which have conical inner end sections, which have bevel surfaces 43 and 44 which slope obliquely towards the central longitudinal axis 21, which form outer boundaries of the annular gaps 31 and 32 in the axial direction and with their outer, radially extending ones , narrow ring end faces 46 and 47 connect flush to the outer surfaces of annular disk-shaped yoke plates 48 and 49
  • a thin-walled tube 52 which is made of antimagnetic stainless steel and is in direct contact with the latter, is inserted, which is flush with its narrow annular end faces outer, radial boundary surfaces of the outer annular disk-shaped yoke plates 48 and 49 of the ring-cylindrical closes magnetizable jacket 33 and forms the radial boundary of a central channel 53, within which the armature 18 of the double-stroke magnet system 19 is slidably mounted to slide back and forth.
  • ring-cylindrical chamber blocks 54 and 56 are inserted in sections, which limit the two valve chambers 13 and 14 of the double-piston pump 10 and are pressure-tight in the end sections of the stainless steel tube 52 are used.
  • the chamber blocks 54 and 56 consist of magnetizable soft iron and are provided with radially outer flanges 57 and 58, which connect flush to the outer surfaces of the outer annular disk-shaped yoke plates 48 and 49 of the ring-cylindrical magnetizable jacket 33. They are held in this position by housing end blocks 59 and 61, which are firmly connected in a manner not shown with the ring-cylindrical jacket 33, which in turn forms part of the housing of the pump 10.
  • the chamber blocks 54 and 56 have on their flanges 57 and 58 outwardly adjoining outer, peg-shaped sections 54 ′′ and 56 ′′, which are pressure-tightly received by blind bores 67 and 68 of the housing end blocks 59 and 61, the ones of which Flanges 57 and 58 from the measured axial depth is greater than the correspondingly measured axial expansion of the outer peg-shaped sections 54 ′′ and 56 ′′ of the chamber blocks 54 and 56, so that through the blind bores 67 and 68 and the outer radial end face ⁇ chen 69 and 71 of the outer peg-shaped sections 54 ′′ and 56 ′′ of the chamber blocks 54 and 56 remain fixedly defined outlet chambers 72 and 73, these outlet chambers 72 and 73 via radial transverse channels 74 and 76 of the housing end blocks with the pressure outputs 16 ' and 16 '' of the pump 10 are communicatively connected.
  • the outer peg-shaped sections 54 ′′ and 56 ′′ are provided with axial through bores 77 and 78, respectively, which are located between the pump chambers 13 and 14 and the respectively adjacent outlet chamber 72 and 73 extend.
  • the respective outer mouth edges 79 and 81 of these through bores 77 and 78 form the valve seats for outlet check valves 82 and 83 designed as ball seat valves, the valve balls 84 and 86 of which are under axial prestressing valve springs 87 and 88 in System with their associated valve seats 81 and 82 are pushed.
  • the armature 18 of the double-stroke magnet system 19, which is made of magnetizable soft iron, for the explanation of which reference should also be made to the detailed illustration in FIG. 2, is designed in its basic form as a thick-walled tube, within which two are provided by a central partition 89 a total of pot-shaped depressions 91 and 92, which extend over the major part of the length of the armature 18 and are open towards the chamber blocks 54 and 56, are delimited from one another into which the pump pistons 11 and 12 have flange-shaped inner end sections 93 and 94 the intermediate wall 89 adjoining each other and to the casing sections 96 'and 96''of the tube 96 of the armature 18 which delimit the recesses 91 and 92 radially on the outside are then mechanically fixed and pressure-tight.
  • the pump pistons 11 and 12 have central longitudinal channels 97 and 98 which are in communication with the respective pump chamber 13 and 14, respectively.
  • the intermediate wall 89 is provided with a central, axial through-bore 99 which, via radial transverse channels 101, which open into an outer annular groove 102 of the anchor tube 96, Ren clear cross section in any possible position of the armature 18 is in overlap with the cross section of a pressure medium supply pipe 103 radially crossing the magnetizable jacket 33 between the field windings 23 and 24, is held in communicating connection with the pressure medium storage container 104.
  • the channel 53 within which the armature 18 is arranged so as to be able to be moved back and forth, is via outer longitudinal grooves 105 of the outer tube 96 of the armature 18, which extend from its central outer annular groove 102 and into the sections arranged on both sides of the armature of the central channel 53 open, held in communicating connection with the storage container 104 and therefore filled with pressure medium.
  • valve chambers 106 and 107 are formed by step-widened end sections 97 'and 98' of the central longitudinal channels 97 and 98 of the pump pistons 11 and 12, into which the Central through bore 99 of the intermediate wall 89 of the armature 18, each with a chamfer surface 108 or 109 that widens conically towards the valve chambers 106 and 107.
  • valve balls 111 'and 112' each of a check valve used as an inlet valve 111 or 112 for filling the pump chambers 13 and 14, these valve balls 111 'and 112' passing through A weakly pre-tensioned valve spring 113 and 114, respectively, which settle on the valve chambers 106 and 107 against the regions of the longitudinal channels 97 and 98 which are smaller in cross section Support ring shoulders 116 and 117, and be pressed into the sealing contact with valve seat surfaces 108 and 109, respectively.
  • “Weakly preloaded" valve spring is intended to mean that the valve balls 111 'and 112' lift off their valve seat surface 108 or 109 when the pressure in the respective pump chamber 13 or 14 is increased by a small amount, eg is 0.2 bar lower than the pressure prevailing in the pressure medium reservoir 104, as a rule the atmospheric ambient pressure.
  • the abscissa in the diagram is the axial distance of the one, as shown in FIGS. 1 and 3, the left magnetically active surface 123 of the armature 18 from the inner annular end face 121 of the "left" pole core arranged axially opposite it, which through the axially inner pin-shaped extension 54 'of the left chamber block 54 is formed, applied and dinate the amount of the magnetic attractive force acting between the ring-cylindrical, magnetizable jacket 33 and the armature 18 when the left excitation winding 23 is energized.
  • the possible values of the magnetic attraction force are represented by a first curve 124, which result when the excitation winding 23 is acted upon by an excitation current of the - relatively low - current intensity I 0 , and thereby the armature 18 extends as far as Contact of its magnetically effective ring end face 123 against a radial stop face 126 of a so-called “anti-adhesive plate” 127 that faces it and is formed, for example, as a thin-walled plastic plate and onto the inner, magnetically effective ring end face 121 of the extension 54 through the inner pin-shaped extension 'of the left valve chamber block 54 formed pole core is applied, which is to prevent the magnetizable armature 18 from coming into direct contact with the magnetizable pole core and being able to "stick" to it due to magnetic remanence effects.
  • curve curves 124, 128 and 129 are only for the region of particular interest between the spring-centered basic position of the armature 18, which is marked in the diagram by the dashed plane 131 of its magnetically active ring face 123 and the abutment surface 126 of the anti-adhesive plate 127, the course plane 132 of which is also shown in dashed lines in the diagram in FIG. 3.
  • the axial distance of the running plane 131 of its magnetically effective end face 123 from the inner end face 121 of the pole core or the stop face 126 of the anti-adhesive plate 127 is greater than their structurally predetermined distance from the radial plane 133 marked by the narrow free annular end face 62 'of the conical edge section 62 of the conical tube 41.
  • the force / displacement characteristic field formed by the curve 124, 128 and 129 of the diagram in FIG. 3 shows immediately that the mechanical configuration of the double-stroke magnet system 19 shown in solid lines is favorable if the pump 10 has a relative high delivery capacity - delivery volume per stroke - should have, but can work at a comparatively low output pressure level. It is then expedient to utilize a movement stroke of the armature 18 in which its magnetically active end face 123 reaches the radial plane 133 marked by the free ring end face 62 'of the conical region 62 of the conical tube 41.
  • the movement stroke H- ⁇ which results for the periodic pumping operation corresponds to the double value 2 hL of the deflection h- ⁇ which the armature 18 experiences in the introductory phase of a pumping operation in which it is marked by the plane 131 Basic position moved into the radial plane 133, which is marked by the free annular end face 62 'of the conical tube 41.
  • the magnetic ring end face 123 of the armature moves periodically back and forth between the radial plane 133 and the radial plane 136 seen from this, as illustrated in the lower part of FIG. 3 by a sinusoidal movement curve 135.
  • F A denotes the effective cross-sectional area of the pump pistons 11 and 12
  • H the piston stroke in the steady operating state
  • N the frequency of the alternating energization of the excitation windings is H because of the large amount - * L of the piston stroke is also particularly high.
  • a mechanical configuration of the double-stroke magnet system is advantageous in that the spring-centered basic position for the armature 18 is the position in which the radial plane 131 of its magnetically effective annular end face 123 coincides with the radial plane 133 marked by the free annular end face 62 'of the conical region 62 of the conical tube 41 and is used for the pumping A region "symmetrical" with respect to this radial plane 133 is used, which is delimited in FIG.
  • the decisive factor for the steady state of operation The value H 2 of the filling and delivery strokes of the armature 18 is, however, significantly lower compared to the case in which the pump 10 can work with a moderate outlet pressure, an increase in the delivery rate in the high pressure operation of the pump 10 however, at least in a limited but interesting area by increasing the frequency n of the alternating energization of the excitation windings 23 and 24 d double stroke magnet system 19 is possible.
  • a design of the double-piston pump 10, as explained with reference to FIGS. 1 to 3, to a high output pressure is also possible in that the stroke range, also associated with high magnetic attraction forces, is used in the diagram in FIG. 3, within which the steeply rising branches 124 v , 128 v and 129 v of the force / displacement characteristic curves 124, 128 and 129 run insofar as these characteristic curves correspond to amounts of magnetic attraction force which are higher than the relative maxima 124 ", 128" and / or 129 "which arise for the radial plane 133, which is marked by the narrow annular end face 62 'of the conical tube 41.
  • the output bridge that can be reached with such a design of the pump 10 would not be, at least not appreciably higher than with a design of the pump on the stroke range delimited by the radial planes 137 and 138, since the maximum output pressure of the pump 10 in any case by the minimum value of the usable attraction force is limited, which - in the steady state - can be reached when the armature 18 takes its greatest distance from the pole core face 121 of the respectively attracting pole core.
  • one of its left pistons 11, as shown in FIG. 1, is also formed as a valve body of a slide valve, designated overall by 140, which is energized by one current, which in turn is left-hand in FIG. 1, with a current which is higher than the maximum current with which the excitation windings 23 and 24 are alternately energized in pumping operation can be controlled into an open position in which the outlet valve 82 is also pushed open by the pump piston 11 and pressure medium from the consumer 17 via the open outlet valve 82, the Pump chamber 13, the central channel 97 of the left pump piston 11, a radial channel 141 communicating with it, which opens into a circumferential groove 142 of the pump piston 11, as well as an inner groove 143 of the left chamber block 54 which can be overlapped therewith and one this with the central channel 53 of the double stroke Relief channel 144 connecting the magnet system 19 can flow out to the storage container 104.
  • the inlet valve 82 is then opened by means of a plunger 146 which continues the pump piston 11 axially and which lifts the valve ball 84 of the outlet valve 82 from its seat 79.
  • the excitation winding 23 is used in this way as a switching magnet for the relief solenoid valve 140. If necessary, an additional excitation winding (not shown) can be provided to actuate the valve 140.
  • a relief valve 147 which is also designed as a solenoid valve, is provided, which has its own field winding 148, which is arranged within the housing end block 61 on the right in FIG. 1, which is supplied with direct current in normal pumping operation and thereby has an annular disk-shaped material made of magnetizable material Valve body 149, which is guided axially displaceably in the blind bore 68 of the right housing end block 61, pulls into sealing contact with an O-ring 151, which surrounds the blind bore-side mouth opening 152 of a relief channel 153, which extends within the right chamber block 56 between the central channel 53 of the double lifting magnet system 19 and the blind hole 68 of the right housing end block 61.
  • a double piston pump 20 is explained as a further exemplary embodiment, which is functionally analogous to the pump according to FIG. 1 and is largely identical to the latter in terms of the double-stroke magnet system provided for the drive.
  • the pump pistons 11 'and 12' which extend in the axial direction on both sides of the armature 18, are designed as solid, circular-cylindrical rods which are designed as Project plunger into pump chambers 13 and 14.
  • the design of the armature 18 and the double-stroke magnet system 19 are completely analogous to the exemplary embodiment according to FIG. 1.
  • the inlet valves 111 'and 112' and the outlet valves 82 and 83 each individually assigned to the pump chambers 13 and 14 are each integrated in a housing end block 59 'and 61'.
  • the central channel 53 in which the armature 18 is arranged such that it can be moved back and forth in the axial direction, communicates with the pressure medium reservoir 104 via the external axial grooves 105 of the armature 18 and the radial transverse channel 101 .
  • this electromagnetically drivable pump 30 its hydraulic functional part 30 ', the actual "pump" on the one hand, and the drive element 161 on the other hand, which consists of the double-stroke magnet system with an axially reciprocating oscillating armature, are function elements that are in themselves uniform trained which can be mechanically coupled to one another in such a way that the piston of the pump 30 ', designated overall by 162, also carries out the oscillating movements of the armature of the drive element 161, which is not shown for the sake of simplicity.
  • the fastening and coupling elements in this regard are not shown for the sake of simplicity and can be implemented using conventional constructional means.
  • the drive element 161 With regard to the design of the double-stroke magnet system, in particular the arrangement of the excitation windings, the design of the air gaps and the magnetically conductive jacket, and the arrangement of return springs, which are the spring-centered basic position of the armature - and the piston 162 - determine the pump 30 ', assuming a structure, as explained in principle by means of FIGS. 1 and 4, to which reference is made in this regard.
  • 161 forms, seen, the housing of the pump unit 30 ', designated overall by 164, has a first bore step 166 which forms the radial boundary of an equalizing chamber 167 which is closed on one side by an end end wall 168 and is permanently communicating connection with the pressure medium reservoir 169.
  • This first bore step 166 is adjoined via a first radial annular shoulder 171 by a second diameter, which is smaller with the first coaxial bore step 172, in which the piston 162 has a piston section 173 on the left as shown in FIG. 5 is guided in a pressure-tight manner.
  • This second bore step 172 merges via a second radial annular shoulder 174 into a third, central bore step 176, which in turn has a somewhat larger diameter.
  • the piston is in this third bore step 176
  • This third, central one Bore step 176 adjoins a fourth bore step 179 via a third radial shoulder 178, the diameter of which corresponds to that of the second bore step 172, which extends between the first bore step 166 and the central bore step 176.
  • the piston 162 is guided so as to be pressure-tightly displaceable with a "right", second push-shaped section 181, which is formed within a drive-side chamber of the pump element housing 164, the radial boundary of which is formed by a fifth bore stage 182 again having a larger diameter the fourth bore step 179 in turn connects via a radial ring shoulder 183, with which the armature of the drive unit 161 is connected in a tension-resistant and shear-resistant manner.
  • a left, annular pump chamber 184 and a right, also annular pump chamber 186 are axially movably delimited by the central piston flange 177 of the pump piston 162, the axial boundaries of which are fixed to the housing and are formed by the central annular shoulders 174 and 178.
  • the right pump chamber 186 receives pressure medium from the compensating chamber 167 via an inlet valve 192 which is associated with the same and also represented as a check valve and which is integrated in the pump piston 162.
  • valve balls 196 of the inlet valves 192 and 194 are arranged in bores 197 and 198 of the piston 162, the central axes of which run parallel to the central axis 163 of the pump element 30 '.
  • the conical valve seat 199 of the inlet valve 194, which is assigned to the left pump chamber 184, is located to the right of its valve ball 198, so that its inertia opens of the valve favors when the pump element 30 'is operated at high frequency and the piston 162 moves to the right, ie executes the filling stroke for the left pump chamber 184.
  • the inlet valve 194 assigned to the right-hand pump chamber 186 is also arranged such that its valve seat 201 is arranged to the left of the valve ball 196, the opening of this valve 194 also being promoted by the inertia of the hydraulic fluid located in the compensating chamber 167 .
  • the pump element 30 ' can also be designed for high output pressures with relatively low drive powers or forces, since the ring end faces 201 and 202 of the central piston flange 177 which are decisive for the maximum achievable outlet pressure can be kept very small by choosing the diameter D 2 of this piston flange 177 and the central bore step 176 to be only slightly larger than the diameter DL of the ram-shaped piston sections 173 and 181.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Reciprocating Pumps (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)

Abstract

Une pompe à entraînement électromagnétique utilisable comme groupe d'alimentation en pression d'un consommateur hydraulique comprend, en tant que dispositif d'entraînement, un système magnétique à double course pourvu de deux enroulements d'excitation de même type situés l'un à côté de l'autre le long d'un axe central commun et qui entourent coaxialement un induit axialement mobile entraînable dans un mouvement de va-et-vient avec le piston de la pompe en cadence avec l'alimentation alternative en courant des deux enroulement d'excitation. Cette pompe est une pompe (10) à deux pistons pourvue de pistons (11, 12) et de chambres (13, 14) de pompage de même type situés de deux côtés de l'axe de l'induit. Les pistons (11, 12) comprennent des canaux centraux de passage (97, 98) en communication permanente avec les chambres (13, 14) de pompage et raccordés à une chambre d'admission ménagée dans l'induit (18) par des soupapes d'admission de non retour situées au centre de l'induit (18). La chambre d'admission de l'induit est maintenue en communication avec le réservoir (104) de fluide hydraulique. Le canal central (53) dans lequel l'induit (18) peut effectuer son mouvement de va-et-vient est lui aussi en communication avec le réservoir (104). La fréquence et/ou l'intensité de courant des impulsions d'excitation utilisées pour alimenter alternativement en courant les enroulements d'excitation (22, 23) sont réglables.
PCT/EP1993/001955 1992-07-22 1993-07-22 Pompe a entrainement electromagnetique WO1994002741A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE59307899T DE59307899D1 (de) 1992-07-22 1993-07-22 Elektromagnetisch antreibbare pumpe
EP93917625A EP0651858B1 (fr) 1992-07-22 1993-07-22 Pompe a entrainement electromagnetique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4224084A DE4224084A1 (de) 1992-07-22 1992-07-22 Elektromagnetisch antreibbare Pumpe
DEP4224084.0 1992-07-22

Publications (1)

Publication Number Publication Date
WO1994002741A1 true WO1994002741A1 (fr) 1994-02-03

Family

ID=6463780

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1993/001955 WO1994002741A1 (fr) 1992-07-22 1993-07-22 Pompe a entrainement electromagnetique

Country Status (4)

Country Link
EP (1) EP0651858B1 (fr)
AT (1) ATE161613T1 (fr)
DE (2) DE4224084A1 (fr)
WO (1) WO1994002741A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107143449A (zh) * 2017-07-03 2017-09-08 东莞市盈森汽车电喷科技有限公司 喷油器衔铁快速响应结构

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10201790A1 (de) * 2002-01-17 2003-11-06 Inventas Ag Baar Hydraulisches Antriebssystem mit Schwinganker-Kolbenpumpe
DE102006014280A1 (de) * 2006-01-26 2007-08-02 Continental Teves Ag & Co. Ohg Hydraulische Schaltungsanordnung
DE102007053549B4 (de) * 2007-11-07 2009-10-01 Hydraulik-Ring Gmbh Elektromagnetische Hydraulikpumpe
DE102014012977A1 (de) * 2014-09-08 2016-03-10 Albonair Gmbh Reduktionsmitteldosiersystem mit verbesserter Förderpumpe
DE102019129478A1 (de) * 2019-10-31 2021-05-06 Linz Center Of Mechatronics Gmbh Hydraulischer schrittmotor

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR589808A (fr) * 1923-12-05 1925-06-05 Pompe électrique
US2043270A (en) * 1934-12-22 1936-06-09 F E Twiss Co Inc Pump
US3437044A (en) * 1966-05-27 1969-04-08 David H Sanders Fluid cooled,double solenoid pumping mechanism
US3884125A (en) * 1971-02-08 1975-05-20 Philip E Massie Variable displacement sealed pump
WO1981000888A1 (fr) * 1979-09-27 1981-04-02 J Mcmullen Pompe, et appareil comprenant la pompe pour infuser un medicament liquide
DE8523214U1 (de) * 1985-08-12 1986-01-30 Innerhofer, Ruth, 8039 Puchheim Vorrichtung zum Fördern von Flüssigkeiten

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR589808A (fr) * 1923-12-05 1925-06-05 Pompe électrique
US2043270A (en) * 1934-12-22 1936-06-09 F E Twiss Co Inc Pump
US3437044A (en) * 1966-05-27 1969-04-08 David H Sanders Fluid cooled,double solenoid pumping mechanism
US3884125A (en) * 1971-02-08 1975-05-20 Philip E Massie Variable displacement sealed pump
WO1981000888A1 (fr) * 1979-09-27 1981-04-02 J Mcmullen Pompe, et appareil comprenant la pompe pour infuser un medicament liquide
DE8523214U1 (de) * 1985-08-12 1986-01-30 Innerhofer, Ruth, 8039 Puchheim Vorrichtung zum Fördern von Flüssigkeiten

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107143449A (zh) * 2017-07-03 2017-09-08 东莞市盈森汽车电喷科技有限公司 喷油器衔铁快速响应结构

Also Published As

Publication number Publication date
DE4224084A1 (de) 1994-04-14
ATE161613T1 (de) 1998-01-15
EP0651858A1 (fr) 1995-05-10
DE59307899D1 (de) 1998-02-05
EP0651858B1 (fr) 1997-12-29

Similar Documents

Publication Publication Date Title
DE19856917B4 (de) Pumpenaggregat
DE102006019584B4 (de) Dosierpumpe
DE3900718C2 (fr)
DE3511820A1 (de) Ventilsteuervorrichtung fuer eine hubkolben-brennkraftmaschine
DE19806720A1 (de) Bistabiler Magnetantrieb mit permanentmagnetischem Hubanker
DE102012204994A1 (de) Geräuscharme hocheffiziente Magnetpumpe
DE19747850A1 (de) Kolbenpumpe
DE3729579A1 (de) Taumelscheibenkompressor mit variabler foerderleistung
DE3929072A1 (de) Ventilsteuervorrichtung mit magnetventil fuer brennkraftmaschinen
DE19937988A1 (de) Vorrichtung zum Fördern und/oder Abspritzen von fliessfähigen Medien, insbesondere von Fluiden
DE19522187C2 (de) Fluidsteuerventil
EP0558714A1 (fr) Systeme de suspension pour vehicules
DE102008013440A1 (de) Magnetbetätigte Hubkolbenpumpe mit hydraulischer Dämpfung
WO1994002741A1 (fr) Pompe a entrainement electromagnetique
DE2929061A1 (de) Magnetventilbetaetigte heizoelpumpe
DE19707654A1 (de) Motor-Pumpenaggregat mit Linearantrieb
DE102016115300B4 (de) Aktuatoranordnung zum Betätigen einer Stelleinheit in einem Kraftfahrzeug und Kupplungsanordnung mit einer solchen Aktuatoranordnung
EP0708243B1 (fr) Pompe pour délivrer des liquides
EP2880312B1 (fr) Pompe électromagnétique
DE19918122A1 (de) Kolbenpumpe
DE4107496A1 (de) Verfahren zur ansteuerung eines als magnetventil ausgebildeten schieberventils sowie fuer eine anwendung des verfahrens geeignetes magnetventil
DE3933125A1 (de) Elektromagnetisch betaetigbare pumpe
DE2206882A1 (de) Elektromagnetisch betätigte Kolben pumpe fur Flüssigkeiten
EP3586696B1 (fr) Pompe à boisson
DE10100217A1 (de) Scheibenbremsensystem für ein Fahrzeug mit super-magnetostriktivem Element

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): BR CZ JP SK US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 1993917625

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 1993917625

Country of ref document: EP

WWG Wipo information: grant in national office

Ref document number: 1993917625

Country of ref document: EP