WO2010004008A1 - Soupape magnétique configurée comme une soupape multivoie et multiposition - Google Patents

Soupape magnétique configurée comme une soupape multivoie et multiposition Download PDF

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Publication number
WO2010004008A1
WO2010004008A1 PCT/EP2009/058763 EP2009058763W WO2010004008A1 WO 2010004008 A1 WO2010004008 A1 WO 2010004008A1 EP 2009058763 W EP2009058763 W EP 2009058763W WO 2010004008 A1 WO2010004008 A1 WO 2010004008A1
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WO
WIPO (PCT)
Prior art keywords
valve
valve element
solenoid valve
movable
movable valve
Prior art date
Application number
PCT/EP2009/058763
Other languages
German (de)
English (en)
Inventor
Eckehart Schulze
Luciano Zanolini
Vincenzo Cecconi
Horst Bendrich
Original Assignee
Hycos S.R.L.
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 Hycos S.R.L. filed Critical Hycos S.R.L.
Publication of WO2010004008A1 publication Critical patent/WO2010004008A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • F16K31/0679—Electromagnet aspects, e.g. electric supply therefor with more than one energising coil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides

Definitions

  • Solenoid valve which is designed as a multi-way / multi-position valve
  • the invention relates to a solenoid valve, which is designed as Mehrwege- / Mehr eins- spool valve, in which for setting the operation of a consumer associated functional positions I and Il a Doppelhubmagnetsystem is provided with two magnet windings, defined by the e- lektronisch controllable excitation in terms of magnitude variable deflections of a movable valve element with respect to a basic position (0) are einstrubar in which also different flow cross sections of the released in the respective functional positions flow paths are adjustable and with the other, mentioned in the preamble of claim 1, generic determining features.
  • the known solenoid valve is formed in a typical design as a 4/3-way solenoid valve having a centered by valve springs basic position 0, in which all valve ports are shut off from each other and two, by shifting a piston in alternative directions einsteubarer functional positions I and II z.
  • the sum of the excitation periods T1 and T2, for which the excitation windings are energized chosen sufficiently small that the deflection amplitudes in the equilibrium positions of the movable valve member are significantly smaller than its maximum Ausberichthub.
  • the alternative excitation of the two regulator windings takes place with a modulation frequency f m of the amount 1 / (T1 + T2), wherein this modulation frequency is preferably between 400 Hz and 800 Hz and the ratio T 1 ZT 2 between 1/100 and 100/1 is variable ,
  • an electronic control unit is provided by means of which the basic principle explained by way of driving the valve can be implemented.
  • the interior of the valve housing into which the housing-shaped piston-shaped valve element protrudes axially from the connection side is divided by the movable valve element into a relatively large cup-shaped space area and an annular space area communicating with each other via outer longitudinal grooves of the movable valve element.
  • cross-bores emanating from these longitudinal grooves enter into communicating connection.
  • the object of the invention is therefore to improve a solenoid valve of the type mentioned in that it is suitable for comparatively larger volume flows without prejudice to the favorable properties of said valve type, which can be seen in a rapid response.
  • housing-mounted connection channels via which the supply connections are communicatively connected to the housing-fixed circumferential grooves of the fixed valve element, symmetrical with respect to the transverse center plane of the valve, it is largely excluded that unilaterally, “asymmetrically” acting on the movable valve element forces arise and can lead to an undesirable displacement of the movable valve element.
  • connection channels are used in a preferred embodiment of the valve in such a way that is connected to a central supply port of the fixed valve element, the T-return port of the solenoid valve.
  • the proposed according to claim 4 embodiment of a solenoid valve according to the invention enables a particularly simple way of valve actuation or actuation of the movable valve element, in particular by means of an additional switching magnet whose armature is coupled in motion with an axially movable push-shaped actuating element.
  • a safety function position of the valve implemented according to claim 7 is advantageous, which can be represented in a simple manner according to claim 8.
  • position measuring system for its realization an inductive position sensor, for. B. an LVDT sensor may be suitable, the improved dynamics of the valve can be further increased, so that this is particularly suitable for the purposes of control technology.
  • an adjusting device is provided, by means of which the movable valve element for specifying a reference position, from which deflections of the valve body are electrically controlled in the electrically controllable, which is a structurally simple for this actuator by the features of claim 12 and easy-to-use design is specified.
  • the displaceability of the movable valve element makes it possible to In this case, perform a "hydraulic" check of the basic valve position by looking for the position of minimal leakage when the valve is pressurized.
  • a position control circle as outlined by the features of claim 15, a high dynamics of the valve settings reached.
  • Such a control loop can be implemented in a simple manner using conventional microprocessor technology with the means of the software that are available to the person skilled in the art.
  • 1 is an overall view of a specific embodiment of the solenoid valve according to the invention, in section along a longitudinal center plane of the valve, spanned by the parallel axes of a P supply channel and a T return channel, on a scale of 1: 1,
  • FIG. 3 shows a partial view of the valve according to FIG. 1 for explaining a safety function position, in one of the FIGS. speaking sectional view, but on an enlarged scale,
  • FIGS. 1 to 3 or 6 shows a block diagram of a position control circuit suitable for controlling a valve according to FIGS. 1 to 3 or 6,
  • FIG. 5a-c timing diagrams for explaining the function of the position control loop of FIG. 4,
  • Fig. 6 shows another embodiment of an inventive
  • Solenoid valve with means for specifying special reference variables for the valve control, in a representation corresponding to FIG. 1.
  • the solenoid valve 10 has as an actuating system with respect to the central longitudinal axis 16 of the valve 10 is substantially rotationally symmetrical trained, designated overall by 17 Doppelhubmagnetsystem seen in the direction of the central longitudinal axis 16, juxtaposed excitation windings 18 and 19 of the same interpretation, by their alternati- ee excitation with control currents represented in Fig. 2 by its valve symbol solenoid valve from its illustrated home position 0, in which its load ports 13 and 14 are shut off both against the P supply port 11 and against the T-return port 12, in the alternative excited functional positions I and II are controllable.
  • the pressure supply connection 11 of the solenoid valve 10 is connected to the "opposite" A consumer connection 13 according to the valve symbol representation, and the T return connection 12 is communicatively connected to the B consumer connection 14.
  • the functional position II Consumer terminal 13 communicating with the T-return port 12 and the B-consumer port 14 communicating with the pressure supply port 11.
  • the exciter windings 18 and 19 are usually wound on cylindrical bobbins with radially outwardly pointing end flanges extending over the radial thickness of the field windings.
  • the exciter windings 18 and 19, including their bobbins, are embedded in a magnetic body, generally designated 26, made of ferromagnetic material, in particular soft iron, which is essentially symmetrical to its transverse central plane 27 extending at right angles to the central longitudinal axis 16.
  • Supply connection 11, the T-return port 12 and the A- load port and the B-load port of the valve are arranged.
  • This terminal block 33 is suitably made of a non-magnetic material, for. B. aluminum.
  • the cylinder jacket-shaped housing section On the side opposite to the terminal block 33 side of the solenoid valve 10 is connected to its formed by the magnetic body 26, the cylinder jacket-shaped housing section in turn a cylindrically annular housing 34 of a total of 36 designated position sensor, by means of which the position of a movable valve member 21 is detected by whose reciprocating movements take place in the direction of the central longitudinal axis 16, the alternative functional positions I and II are adjustable.
  • This movable valve element 21, which forms the armature of the two excitation windings 18 and 19 comprehensive double magnet system 17 is formed as a basic shape after circular cylindrical tubular, relatively thick-walled sleeve, which consists of magnetizable material, advantageously soft iron material. It encloses coaxially a housing-fixedly arranged, piston-shaped valve element 22, which mediates the centering of the sleeve and its axial guidance, which is slidably disposed on portions of its length, which are arranged between inner annular grooves of the sleeve on the fixed valve element with a sealing sliding fit.
  • a switching magnet designated as a whole by 37, whose armature 39, which is movable when its magnet winding 38 is energized, has a total of 41. recorded actuating tappet with the movable valve element 21 - the valve sleeve - is motion-coupled in the sense of a rigid connection.
  • the P supply port 11, the T return port 12, and the B consumer port 14 are communicatively connected to each other, but blocked off from the A consumer port 13.
  • the valve 10 is as it were hydraulically short-circuited, such that no significant hydraulic forces act on the movable valve element 21 and this is thus urged by the action of a suitably biased return spring 42 in the functional position III of the valve 10, by conditioning the armature 39 of the solenoid 37 is marked on a stop surface 43 remote from the fixed valve element 22, which is formed by the inner surface of the bottom of a pot-shaped housing part 44 of the generally designated 46 housing of the switching magnet 37, which, apart from an inner annular gap 47, the magnetizable Envelope of the magnetic winding 38 of the switching magnet 37 forms.
  • the movement coupling of the armature 39 and the switching magnet 47 with the sleeve-shaped movable valve element 21 conveys the basic shape after elongated rod-shaped actuating plunger 41, which passes through the bore-shaped interior of the housing 34 of the position sensor 36 and into the immediate vicinity of the substantially circular Endstirn Chemistry 48 of its basic form is cylindric risch-rod-shaped housing-fixed piston member 22 of the solenoid valve 10 extends, on which the valve spring 42 is supported, which forms the remindstellele- ment for the armature 39 of the solenoid 37, the thereby - in the de-energized state of its magnetic winding - with its annular end face 49 in Appendix with the inner bottom surface 43 of the cup-shaped housing part 44 of the housing 46 of the switching magnet 37 passes, or is held.
  • the position sensor 36 is without limitation of generality, i. H.
  • LVDT sensor Linear Variable Differential Transformer
  • the LVDT sensor 36 is assumed to be known in terms of its structure and function (see EUROPA Lehrstoff, "Fachismeinformationstechnik und Industrieelektronik, 1994, page 521).
  • This position sensor or displacement sensor is represented in the representations of FIGS. 1 and 3 by a movable valve element and its movements with an executing annular ferromagnetic core 51 and a total of three transformer windings 52, 53 and 54, namely a centrally arranged primary winding 53 and the one side of this arranged secondary windings 52 and 54th
  • the core 51 is arranged on the radially outer side of a pointing to the position sensor 36, thin-walled, tubular extension 56 of the movable valve member 21, which on the housing fixed piston member 22 of the valve 10 side facing away from one inserted into the tubular end portion 57 of the movable valve member 21 Spreng- rings 58 by means of its own, narrow radially inwardly facing support ring 59 is axially supported.
  • a screw spring 61 engages a screw spring 61, the annular end of which is supported on a radially projecting from the actuating plunger 41 support flange 62.
  • the radial dimension after about the switching magnet side support flange 62 corresponding inner support flange 63 of the actuating plunger 41 is provided.
  • a second prestressed coil spring 64 whose other end is in turn supported on a narrow support ring 66, which, the sensor-side support ring 59 opposite, is pressed and held in contact with the snap ring 58.
  • the inner diameter of the two support rings 59 and 66 is slightly larger than the diameter of the axially passing through these portions of the actuating plunger 41, so that smooth movement of the relative movements of the movable valve member 21 is ensured relative to the plunger when the movable valve member 21 by means of Doppelhubmagnetsys- 17 to Execution of actuating movements is controlled, which serve the setting of the functional positions I or Il and the effective in these functional positions flow cross sections. Such relative movements take place, starting from the position shown in FIG.
  • the two springs 61 and 64 have the same spring rate, typically 10 N / m.
  • the return spring 42 is impressed with a basic bias having a typical value around 15N. This basic bias voltage is dimensioned such that, in the currentless state of the switching magnet 37, it is sufficient to hold the armature 39 thereof in abutment with the abutment surface 43 of the cup-shaped housing part 44, irrespective of whether the double-stroke magnet system 17 is energized or not.
  • the actuating plunger 41 is, in order to facilitate the pre-assembly of the assembly comprising the plunger itself and the movable valve element 21, divided between its two support flanges 62 and 63, wherein the part comprising the inner support flange 63 by means of an anchor screw, which in a thread of the other sensor-side flange 61 comprehensive part of the actuating plunger is screwed, is firmly connected.
  • the head 69 of this anchor bolt 68 is recessed within a step bore 71 open towards the housing-fixed valve element, which part takes up the length of the return spring 42 whose other end is received in a pot-shaped depression of the housing-fixed valve element 22.
  • valve element 22 arranged at the housing and the movable, sleeve-shaped valve element 21 are designed in more detail as follows:
  • the cylindrical rod-shaped, fixed valve element 22 has a running inside the same, extending from the pump port over most of the length of the valve element extending inner longitudinal channel 72, in which the high output pressure P of the pressure supply unit can be coupled bar.
  • the longitudinal channel communicates via two "radial" short slot-shaped connection channels 73I and 73R with flat outer grooves 74 / I and 74 / r of the fixed valve element 22, which extend over the entire circumference of the fixed valve element 22.
  • Design and arrangement of these outer grooves of the fixed housing member 22 are symmetrical with respect to a perpendicular to the central longitudinal axis 16 of the solenoid valve 10 extending plane 78, which is also the plane of symmetry of the arrangement of the excitation windings 18 and 19.
  • the further flat grooves 76 and 77 arranged between the P-connection grooves 70 / I and 74 / r are assigned to the load connections, the left outer groove 76 according to the illustration being the A consumer connection 13 and the other outer groove 77 being the B consumer connection 14 associated with the valve 10 of FIG. 3.
  • the consumer connection grooves are connected to connection channels 79 and 81 which are indicated by dashed lines only by short sections and which, with respect to the central longitudinal axis of the valve, also extend azimuthally within the stationary valve element 22.
  • This supply connection annular groove 82 communicates with the radially outward connection of the exciter windings 18 and 19 arranged parallel to the P supply channel 72 extending T-return port 12 via a generally designated 83 radial connection channel, the only outside the Doppelhubmagnetsystems in the terminal block 33rd again adapted to the standard corresponding connection diagram.
  • the radial connection channel 83 is formed in the embodiment chosen for explanation as an annular slot which connects the inner groove 82 with an outer groove 84 of the arranged between the exciter windings magnetizable housing part 86.
  • This outer groove 84 is opposite to an outer, substantially tubular cylindrical portion 87 of the magnetic body of the valve, in which the T-return port 12 extends, which in turn via a short connection channel 89 with the outer groove 84th communicatively connected, sealed by ring seals 88 / I and 88 / r.
  • the sleeve-shaped, axially movable valve element 21, which is displaceable guided by suitable energization of the excitation windings 18 and 19 in alternative directions "back and forth” on the stationary member 22 is on its radially inner side, with the valve member 22 toward open annular grooves 91th 1 and 91 / r provided on both sides of a central inner annular groove 92 of the movable valve element 21.
  • a further inner groove 93 of the movable valve member is provided, which in the illustrated , Special embodiment arranged on the actuating plunger 41 side facing away from the movable valve member 21 and the safety position III of the valve 10 is assigned, in which its cross section in positive overlap with the cross section of the adjacent outer groove 73 / I of the fixed valve member 22 is.
  • This further inner groove 93 is in the configuration shown in FIG. 1 of the valve 10, which corresponds to its locking home position 0, inoperative. Also within the deflection range of the movable valve element 21, within which only the functional positions I and II of the controlled by pulse width modulation solenoid valve 10 are adjustable, this inner groove 93 is inoperative. Said inner groove 93 for the functional position IM is in communication with at least one, radially outer longitudinal groove 94 of the movable valve member 21 with the central inner groove 92 of the movable valve member 21, said inner groove 92 in turn via a gap 95 with the annular gap 83 of the magnetic body 26th is in communicating connection, which in turn is communicatively connected via the short transverse channel 89 to the tank connection channel 12.
  • the width of the central inner groove 92 of the movable valve member 21 is dimensioned sufficiently large that this groove remains communicatively connected to the tank return passage 12 in any possible position of the movable valve member.
  • the P-pressure port 11 and the T-return port 12 are as it were short-circuited and connected to the B-consumer port 14, corresponding to the functional position III shown in FIG. 2.
  • this operates in circulation mode, and there is no pressure on the valve 10 coupled into the consumer.
  • a total of 100 is a position control circuit, by means of which the position of the explanatory example by the valve sleeve 21 fabricated Th armature of the armature of the Doppelhubmagnetsystems 17 of the valve under consideration according to the basic principle known pulse width modulation lations vide is adjustable.
  • FIGS. 5a to 5c For further explanation, reference should now also be made to FIGS. 5a to 5c.
  • a neutral middle position which would correspond to the blocking position between alternative flow positions I and II in the case of a 4/3-way valve assumed for explanation, results, according to the presumed pulse width modulation method, when the pulse duration of the pulses 101 and 102, with which the Windings 18 and 19 are controlled, are the same, d. H. half the period T / 2 correspond.
  • the period duration 7 of the drive cycles, within which both windings 18 and 19 are each exposed to an energizing pulse 101 and 102, is tuned to the valve 10 and its Doppelhubmagnetsystem 17 such that the armature 21 due to its mechanical inertia from the Bestromungsimpulsen 101 and 102nd resulting, in alternative directions acting on him forces can not follow, but in accordance with the resulting forces in an equilibrium position, but in this sense in the sense of a dithering movement with small amplitudes can follow so far that the static friction of this armature is virtually eliminated and only the lower sliding friction must be considered as resistance for deflections.
  • pulse repetition frequencies around 300 Hz are expedient. This means, however, that a sudden change in the setpoint for the position of the armature of Doppelhubmagnetsystems 17 may result in a delay of the armature movement by a "dead time", which may be up to the period 7.
  • the position control loop 100 is designed as follows:
  • the input stage of the position control loop 100 is formed by a summing junction 121, which is connected to a (+) input 122 for a nominal position of the kers 21 of the Doppelhubmagnetsystems 17 or the opening cross section of the actuated by this valve in response to its position characteristic position command signal (S So ⁇ ) is supplied.
  • a (-) - input 123 the summation point 121 is fed the position actual value signal of a position sensor 124, which is a measure of the actual position (S / Sf ) of the position of the armature 21 of the Doppelhubmagnetsystems 17 in a format corresponding to the setpoint signal (S So ⁇ ) is.
  • the output signal of the summation point 121 which is characteristic of the control deviation ⁇ and corresponds to the algebraic sum of the (positively counted) setpoint value signal and the (negatively counted) actual value signal and stands in monotonous relation to the deviation signal ⁇ in the sense of a gain, is a regulator 125 whose output signal (Y signal) is fed to a first input 126/1 of a pulse width modulator 126 which receives the error output signal ⁇ (t) of the summing point 121 at a second input 126/2, which also forms the input variable for the controller 125.
  • the error signal which may be positive or negative, is also input to a processing stage 132 whose output is a measure of the magnitude of the error output Amount of the error signal is greater than a threshold value ⁇ s , a third input 126/3 of the PWM modulator, a signal characteristic for exceeding the value zuchel.
  • the pulse width modulator 126 From a processing of the error output signal ⁇ and the controller output signal (Y), the pulse width modulator 126 generates the driving signals for the magnet windings 18 and 19 according to a fixed or variably definable algorithm in such a manner as to be hereafter apparent Deflection of the armature 21 of the Doppelhubmagnetsystems 17 leads to a reduction of the spring signal ⁇ or the tracking error of the control.
  • the pulse width modulator 126 is implemented with the property that a for the amount exceeding said threshold ⁇ s , which usually occurs when the change takes place between extreme values of the desired position, ie, as shown in Fig. 5a , From a position which corresponds to a predominant time control of one of the two field windings 18 or 19, in a position - beyond the neutral center position of the armature - leads, which lies at a relatively large distance from the center position and in this case the setpoint change in terms of magnitude is significantly greater than the counted from a defined starting position from threshold ⁇ s (see Fig. 5a).
  • the pulse width modulator 126 interrupts the drive period of the duration T which is in progress until the said threshold value is exceeded, which comprises energizing one field winding 18 and energizing the other field winding 19, and starts immediately again a new drive cycle, which begins with the energization of that field coil whose energization leads to a deflection of the armature 21 in the sense of a reduction of the control deviation.
  • FIG. 5b in conjunction with FIG. 5a:
  • the z. B. 2 I 3 may have been the maximum deflection, has been held in one of its two possible flow positions I or Il, to be switched to its other flow positions Il and I, and that this so quickly as possible and with the same amount of deflection compared to a neutral middle position, the z. B. is assumed as a blocking position between the two alternative flow positions of the valve presupposed as a 4/3-way valve.
  • the position command value setting is to be changed from a position one-sided "right" of the neutral position of the armature 21 of the double-stroke magnet system 17 and thus its valve body by the command value level S r to a position "left" of the neutral position, illustrated by the setpoint signal level Si of Fig. 5a, such that the setpoint waveform of the jump function 103 of FIG. 5a corresponds.
  • the amount of this difference is significantly greater than a predetermined threshold ⁇ s , beyond which the pulse width modulator is immediately switched to that operating mode in which that pulse shape of the excitation current pulses 101 and 102 is given, which for the approach of the armature position at the new setpoint Si is suitable.
  • the left coil with the train of pulses 101 ', for 3 A of the period T energizing the left winding 18 and their currentless state corresponds to% of the period duration, while the other excitation winding 19 is energized for 3 A of the period without current and only for% of the cycle duration with exciter current.
  • the previous control cycle which in the illustrated case example begins with a high level pulse 102 / a of the "right" solenoid coil energization 19 and a pulse break of corresponding duration for the "left" solenoid coil 18 and the falling edge 101 e of a field current pulse 101 with which the magnetic coil 18 is energized or with the onset of the next high-level pulse for the right solenoid coil 19 after the time t u , ends, in which the change of the position command value setting starts, continued until after the expiration of the period T, calculated from the time t B , in which this control cycle had begun, with the changed Setpoint associated control cycle begins, which in the case of explanation chosen for the case only at the time t Sn is the case.
  • FIG. 1 to 3 simplified embodiment shows, in which a posi- tion monitoring is not provided and the valve 10 'itself in the type is designed as a common 4/3-way valve, the two alternative flow positions I and II has, in which the flow cross-section with increasing deflection from a provided as a center position "neutral" blocking position in which all four valve ports against each other and against the consumer and against the pressure supply are shut off, depending on the deflection - eg proportional to this - increases.
  • valve 10 the safety position (III) explained with reference to FIG. 2 is not provided, nor is a distance measuring system for monitoring the armature position provided. Nevertheless, the features described below with reference to FIG. 6 are also with valves, as previously explained, can be used for the specified purpose, of course, with expert adaptation of the same to the structural conditions, which are predetermined by the implementation of the additional functions of the aforementioned valve designs.
  • valve 10 Insofar as reference numerals are used in FIG. 6, the elements of the valve 10 described with reference to FIGS. 1 to 3 have already been assigned, this is intended to avoid repetition, the reference to the construction and functional equality or analogy of identical signify elements and also include the reference to the parts of the description assigned to them.
  • the following description of the valve 10 'according to FIG. 6 is therefore intended to be limited to those features which are not realized in the embodiment described with reference to FIGS. 1 to 3.
  • the valve 10 is provided, without loss of generality, as a "simple" 4/3-way valve having two alternative flow positions I and II and a blocking position "0" when switching from one is taken into the other flow position at least for a short time. Further, it is assumed that the flow positions with the blocking position or with each other have no overlap, ie a displacement of the valve body, in the given case, the valve sleeve 21, from a flow position, with the z. B.
  • a piston movement of a linear cylinder is accompanied, in which a piston rod is extended extended, in the other flow position, which is linked to the return movement of the piston rod, at the moment leads to the reversal of the direction of movement, in the "sharp" control edges of the movable valve member 21 with traverse this corresponding control edge of the fixed valve member 22, ie, the associated control edges of the movable valve member 21 and the fixed valve element 22 coplanar ver. to run.
  • the movable valve element 21 including a tubular extension portion 57, within which the coil springs 61 and 64 are arranged, which are supported on support flanges 62 and 63 of the rod-shaped spring support 41 'comprehensive assembly of the valve 10' according to Fig. 6 in the direction of the longitudinal axis 16 back and forth;
  • one end of the housing 32 protruding end portion 131 of the rod-shaped spring support 41 ' is formed as a threaded rod, which is with its thread with an internal thread of a threaded sleeve 129 engages anchored to a cup-shaped Genzousede- disgust 128 shear.
  • the movable valve member 21 can be fixed by tightening a lock nut 127 in a defined position.
  • an initial position of the movable valve element 21 is selected, with which a relatively small flow cross-section of the valve 10' is given in one of its two flow positions. Then, by turning the assembly comprising the movable valve element 21, the blocking position is determined as the position in which only a minimal amount of leakage oil is left. current occurs. It is understood that this approach to the blocking position can be carried out from both flow positions forth and should also be performed for control purposes, possibly several times.
  • At least one adjusting screw 141 is provided, by means of which the tubular magnetic body member 140 against or by the spring force of a biased return spring 142 in alternative directions is displaced.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

Dans une soupape magnétique (10) configurée pour un fonctionnement de base comme une soupape à coulisseau à 4/3 voies, pour établir les positions de fonctionnement I et II associées au fonctionnement d'un consommateur, un système magnétique (17) à double course est doté de deux enroulements d'excitation (18 et 19) dont l'excitation commandée électroniquement définit des déplacements variables d'un élément mobile de soupape (21) dans différentes directions par rapport à un élément fixe de soupape (22) de la soupape (10). Différentes sections transversales de passage des parcours d'écoulement libérés peuvent être établies. Les rainures annulaires (91/l, 92 et 91/r) de l'élément mobile de soupape (21) associées aux raccordements de consommateurs (11, 12) et aux raccordements d'alimentation (13, 14) sont disposées symétriquement par rapport à un plan central (78/V) qui s'étend perpendiculairement à l'axe longitudinal (16) de la soupape (10). L'élément mobile de soupape (21) forme l'induit du système magnétique (17) à double course qui est entouré par un corps magnétique cylindrique (26) constitué d'un matériau magnétisable et qui forme une partie globalement en forme d'enveloppe cylindrique du boîtier de soupape. Un circuit électronique est prévu pour exciter de manière contrôlée les enroulements magnétiques (18 et 19) et réalise la commande des déplacements en va-et-vient de l'élément mobile de soupape (21) selon le principe de la modulation de la largeur d'impulsion des courants d'excitation apportés aux enroulements d'excitation. L'agencement de canaux de raccordement (73/l, 73/r, 83, 89) fixes sur le boîtier par lesquels les raccordements d'alimentation (11, 12) peuvent être raccordés aux rainures périphériques (73/l, 73/r, 76, 77) fixes sur le boîtier de l'élément fixe central de soupape (22) est également symétrique par rapport audit plan central (78) de la soupape (10) et le raccordement de retour (12) de préférence en forme de T de la soupape magnétique (10) est raccordé à la rainure centrale de raccordement d'alimentation de l'élément fixe de soupape (22).
PCT/EP2009/058763 2008-07-09 2009-07-09 Soupape magnétique configurée comme une soupape multivoie et multiposition WO2010004008A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810032219 DE102008032219A1 (de) 2008-07-09 2008-07-09 Magnetventil, das als Mehrwege-/Mehrstellungsventil ausgebildet ist
DE102008032219.9 2008-07-09

Publications (1)

Publication Number Publication Date
WO2010004008A1 true WO2010004008A1 (fr) 2010-01-14

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
JP2016035302A (ja) * 2014-08-04 2016-03-17 株式会社デンソー 電磁弁

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010039711A1 (de) 2010-08-24 2012-03-01 Bucher Hydraulics Gmbh Rasteneinrichtung

Citations (4)

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Publication number Priority date Publication date Assignee Title
EP0574408A1 (fr) * 1991-03-08 1993-12-22 Eckehart Schulze Procede de commande d'une vanne a tiroir con ue comme une vanne magnetique et vanne magnetique permettant de mettre en uvre le procede.
DE19607773A1 (de) * 1996-03-01 1997-09-04 Bosch Gmbh Robert Elektromagnetisch betätigtes Wegeventil
EP1108935A2 (fr) * 1999-12-14 2001-06-20 Bucher Hidroirma S.P.A. Distributeur
WO2005027162A2 (fr) * 2003-09-11 2005-03-24 Continental Hydraulics Valve de distribution proportionnelle avec capteur de positionnement magnetique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0574408A1 (fr) * 1991-03-08 1993-12-22 Eckehart Schulze Procede de commande d'une vanne a tiroir con ue comme une vanne magnetique et vanne magnetique permettant de mettre en uvre le procede.
DE19607773A1 (de) * 1996-03-01 1997-09-04 Bosch Gmbh Robert Elektromagnetisch betätigtes Wegeventil
EP1108935A2 (fr) * 1999-12-14 2001-06-20 Bucher Hidroirma S.P.A. Distributeur
WO2005027162A2 (fr) * 2003-09-11 2005-03-24 Continental Hydraulics Valve de distribution proportionnelle avec capteur de positionnement magnetique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016035302A (ja) * 2014-08-04 2016-03-17 株式会社デンソー 電磁弁

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