EP0853731B1 - Ensemble a vannes de regulation electrohydraulique - Google Patents

Ensemble a vannes de regulation electrohydraulique Download PDF

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Publication number
EP0853731B1
EP0853731B1 EP96933364A EP96933364A EP0853731B1 EP 0853731 B1 EP0853731 B1 EP 0853731B1 EP 96933364 A EP96933364 A EP 96933364A EP 96933364 A EP96933364 A EP 96933364A EP 0853731 B1 EP0853731 B1 EP 0853731B1
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EP
European Patent Office
Prior art keywords
control valve
piston
main control
servo control
valve
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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
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EP96933364A
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German (de)
English (en)
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EP0853731A2 (fr
Inventor
Eckehart Schulze
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Individual
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Individual
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86606—Common to plural valve motor chambers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • the invention relates to an electrohydraulic control valve arrangement for controlling the pressure medium inflow and outflow to and from a linear or rotary hydraulic motor, with a main control valve designed as a 3-position valve, one in a hole in its housing in an alternative Has directions between the deflectable pistons, the maximum amounts in alternative functional positions I and II of the main control valve released cross sections of Flow paths correspond to those with increasing deflection the piston from a (functionally neutral) center position 0 released continuously, essentially proportional to deflection and accordingly when the piston approaches its central position can be reduced, the piston deflections using an electro-hydraulic pilot valve arrangement, which is controlled electrically by means of alternative pressurization and relief of two control chambers of the main control valve are controllable.
  • Such an electro-hydraulic Control valve assembly is the well-known proportional valve ("The hydraulic trainer", Vogel publishing house, Würzburg, 1st edition 1978, pages 143 to 145), in a typical Training as a 4/3-way valve as the main control valve and two by means of a proportional magnet, one for Actuating force proportional to current generated, controllable Pressure control valves as a pilot valve arrangement includes through which the control chambers of the main control valve with pressure can be acted upon and relieved of pressure.
  • the object of the invention is therefore a control valve arrangement of the type mentioned at the outset to improve that a largely hysteresis-free control of the main control valve and also a more sensitive response of the Control valve assembly is achieved overall.
  • an electrohydraulic overflow control valve which with electromechanically controllable position setpoint specification and mechanical position feedback feedback works.
  • this control principle includes the overrun control valve one in one with the housing of the main control valve fixed connection block arranged housing element, that is movable in a pressure-tight manner with respect to this connection block, and in turn movable in a pressure-tight manner in the housing element arranged piston element, one of these elements serves as a setpoint specification element, which by means of a controllable electric motor in alternative directions for execution incremental deflections to the other element is drivable, which in turn as an actual position feedback element serves that with the piston of the main control valve non-positively coupled, and thus for execution with the deflections of the setpoint specification element same-direction wake movements can be driven.
  • the control valve arrangement mediates at least the following functionally advantageous properties, for the explanation of which it is assumed that the setpoint specification element of the overrun control valve, its piston and as a position actual value feedback element whose the piston is coaxial surrounding sleeve-shaped housing element are used, wherein the piston by means of a stepper motor as a setpoint specification motor driven rack and pinion, the same time acts as a reduction gear for incremental execution Deflections in relation to the sleeve-shaped housing element of the follow-up control valve is drivable and the sleeve-shaped Housing element of the follow-up control valve - free of play - is motionally coupled to the piston of the main control valve, in such a way that its deflections correspond to those of the setpoint input piston follow, with the sleeve-shaped housing element in turn with the piston of the main control valve over a Gear can be motion-coupled with a defined Implementation ratio deflections of the main control valve piston in correlated follow-up movements of the
  • the overrun control valve regardless of the sense of change of the setpoint specification and that of the piston position of the main control valve in each case then in its functionally neutral middle position, if equality the actual position of the main control valve piston with their Setpoint is given by stepper motor-controlled displacement of the setpoint specification piston of the overrun control valve has been scheduled.
  • the increments of the incremental deflections of the setpoint input piston of the follow-up control valve are electronic easily controllable and in terms of their amount definable within wide limits, so that a sufficiently finely graduated, quasi-continuous adjustability of the main control valve to the required flow cross-sections is possible. Problems with the known Proportional valve from a "hum" (dither current) modulation resulting from magnetic excitation currents occur at the In principle, the control valve arrangement according to the invention does not.
  • claims 2 and 3 are alternative designs the control valve assembly specified, in which the respective position feedback element of the overrun control valve rigidly connected to the piston of the main control valve can be and so far a structurally particularly simple Structure of the control valve assembly is given.
  • the main control valve of the control valve assembly as Rotary slide valve and the overrun control valve as a linear one Slider valve be formed, then a gear device is provided the azimuthal deflections of the piston of the main control valve in linear displacements of the Feedback element of the follow-up control valve is implemented.
  • Valve spring arrangement For the setpoint specification element of the overrun control valve in the non-activated state of the setpoint input motor in with the neutral central position of the main control valve piston linked setpoint default position urgent Valve spring arrangement are characterized by the features of claims 11 to 13 configurations that can be used alternatively or in combination specified, which are particularly useful if the Follow-up control valve of the control valve arrangement as a linear one Slider valve is formed while by the features of claims 14 and 15 designs of a functionally Valve spring arrangement are specified that are special for a follow-up control valve designed as a rotary slide valve the control valve assembly are suitable.
  • Control valve assembly includes one by hydraulic Pressure-actuated main control valve, designated overall by 11, through alternative pressurization and relief in control chambers 12 and 13 from his illustrated Home position 0 in alternative functional positions I and II is switchable, as well as a pilot valve with a total 14 designated follow-up control valve that with electrical controllable specification of the target position of the piston 16 of the Main control valve 11 and mechanical feedback of the actual position of the piston 16 works.
  • control valve assembly 10 as the circuit diagram representation of Fig. La removable, for operating control of a rotary hydraulic motor 17 is used, its alternative directions of rotation - clockwise and counterclockwise - the alternative functional positions I and II assigned to the main control valve 11 are, the speed of the motor by the him on the Main control valve 11 fed and discharged volume flow of the hydraulic operating medium is adjustable.
  • FIG. 1a The one shown in FIG. 1, designated 0 in FIG. 1a
  • the basic position of the main control valve 11 is at a standstill assigned to the rotary hydraulic motor 17.
  • the main control valve 11 is designed as a linear slide valve, whose piston 16 in the direction of the central longitudinal axis 18 one extending between the control chambers 12 and 13 Housing bore 19 can be pushed back and forth, where relevant end positions between impact End pieces 21 and 22 of the piston 16 with these in each case opposite end walls 23 and 24 of the control chambers 12 and 13 are marked.
  • the main control valve 11 is designed as a 4/3-way valve, in its illustrated basic position 0 with the pressure outlet a pressure supply unit, not shown, connected P supply port 26 and one with the unpressurized Storage tank of the pressure supply unit connected T-return connection 27 both against an A control connection 28 as well as against a B control connection 29 of the main control valve, through their alternative pressurization and relief the drive control of the consumer 17 takes place, shut off are.
  • a pressure supply unit not shown
  • P supply port 26 and one with the unpressurized Storage tank of the pressure supply unit connected T-return connection 27 both against an A control connection 28 as well as against a B control connection 29 of the main control valve
  • the main control valve 11 is designed as a proportional valve, with the increasing deflection of its piston 16 whose center position corresponding to the basic position 0, each according to the direction of this deflection, which in the alternative Function positions I and II released flow paths 31 and 32 or 33 and 34 with increasingly larger cross sections are released, each in the end positions of the piston reached their maximum values.
  • the main control valve 11 is used to achieve these functions in the usual way as follows:
  • This inner one Bore section 19 ' forms the radially outer, housing-fixed Limitation of an annular space 51 that with the P-supply connection of the main control valve 11 in constantly communicating Connection is established.
  • This annular space 51 is axially movable through the adjacent ring end faces of the through the central piston rod 42 interconnected central Piston flanges 37 and 38 limited to the outer Edges of their adjacent ring end faces on the piston side, form inner control edges 52 and 53, the axial Distance equal to that of the inner control edges 44 and 46 the A control groove 47 and the B control groove 48 are from each other.
  • the A control groove 47 and the B control groove 48 of the valve housing 49 close each one through the radially inner edge of their axially outer groove flank marked, outer control edge 54 or 56 to bore sections 19 ′′ or 19 ′′, which are fixed to the housing form radial boundaries of annular spaces 57 and 58, communicating with one another via a housing channel 59 connected and common to the return port 27 of the main control valve 11 are connected.
  • the one with the unpressurized reservoir of the supply unit connected T-ring spaces 57 and 58 are through the end flanges 36 and 39 of the piston 16 of the main control valve 11 against the control chambers 12 and 13 delimited movable pressure-tight.
  • the amounts in the alternative flow positions I and II released cross sections of the flow paths 31 and 32nd and 33 and 34 of the main control valve 11 are by means of Guide-up control valve 14 adjustable, by means of which the Pressurization and relief of the control chambers 12 and 13 of the main control valve 11 are controllable.
  • the overrun control valve 14 is in the particular embodiment shown in largely structural analogy to the main control valve 11 designed as a linear slide valve that with parallel course of the central longitudinal axis 68 to the central Longitudinal axis 18 of the main control valve 11 is arranged.
  • overrun control valve 14 mediates the function of 4/3-way valve, for which a total of 66 Piston and its housing 99, apart from cross-sectional dimensions and a larger axial distance from the central Piston flanges 87 and 88, between which there is the P-ring space 101 of the follower control valve 14 extends the same configuration piston-side control edges 102,103,111 and 112 as well Control edges 94,96,104 and 106 provided on the housing is, as with the main control valve 11.
  • the housing 99 of the follow-up control valve 14 is as one outside cylindrical sleeve formed in one with the central Longitudinal axis 68 of the follower valve 14 coaxial bore 113 of a housing block 114 which is fixed to the housing 49 of the main control valve 11 is connected, sliding pressure-tight is guided back and forth.
  • the A control connection 78 is the one shown in FIG. 1 on the right Control chamber 13 of the main control valve connected during the B control port 79 of the follower valve 14 with the left Control chamber 12 of the main control valve 11 is connected.
  • the relevant connection channels are designated 116 and 117 respectively.
  • the piston 66 of the follow-up control valve 14 has one through valve springs 118 and 119 centered center position, which the Setpoint specification position for the basic position shown of the piston 16 of the main control valve 11, which has a schematically indicated bridge 121 with the housing 99 of the Follow-up control valve 14 is connected in a non-displaceable manner.
  • This assignment of the basic positions 0 of the overrun control valve 14 and the main control valve 11 is by the precision the manufacture and, if necessary, the adjustability the mechanical connection between the main control valve piston 16 and the piston 66 of the follow-up control valve 14 and the adjustability of the basic position of the valve piston 66 of the Follow-up control valve 14 reached.
  • the adjustability in this regard the piston position is shown in Fig. 1 by a Set screw 122 indicated, by means of which a support block 123, on which one valve spring 118 is supported on the housing side, is axially displaceable while the other valve spring 119 on an opposite end wall 124 of the Follow-up control valve 14 containing housing block 114 axially is supported.
  • the piston 66 is at its one end, as shown in FIG. 1, on the right with a slim, rod-shaped, the right valve spring 119 centrally penetrating extension 126 provided by a central bore 127 of the end wall 124 passes through and is designed as a rack 128 at its free end, with their teeth the drive pinion 129 of an electric Stepper motor 131 is in mesh-free engagement.
  • the stepper motor 131 is electronic by output pulses Control unit 132 for performing incremental rotary movements can be controlled in the possible alternative directions of rotation.
  • the main control valve 11 is in its functional position II controllable and to defined values of the opening cross-sections released in this functional position II Flow paths 33 and 34 adjustable.
  • the associated gradation of the opening cross sections of the main control valve 11 in its two functional positions I and II corresponds practically to a continuous change in the opening cross sections of the respective flow paths.
  • valve pistons used as the setpoint specification element 66 of the follower valve 14 attacking valve springs 118 and 119 are designed so that they are not energized State of the stepper motor 131 are able to Overcoming residual holding torque and the valve piston 66 in to bring its neutral middle position, with the result that as long as the pressure supply is working, that too Main control valve returned to its home position 0 becomes.
  • the feedback of the actual value of the position of the piston 16 'of the main control valve 11' is carried out by "Co-rotating" of the basic cylindrical-sleeve-shaped Housing element 99 'of the follow-up control valve 14' around it central longitudinal axis 68 ', the translation being more translational Movements of the main control valve piston 16 'along whose central longitudinal axis 18 in rotary movements of the used as a feedback element housing part 99 'of the follow-up control valve 14 'by positive engagement of one with the sleeve-shaped rotatable housing part 99 'of the follow-up control valve 14 'firmly connected coupling element 143 with a Annular groove 144 of the main control valve piston 16 'takes place, those in the middle area of the relatively elongated piston flange 36 'is arranged, on the one hand, the pressure-tight movable Limitation of the left control chamber 12 and the other also the one - left - pressure tight movable limit of the left T-ring space 57
  • the piston 66 'of the overrun control valve which serves as the setpoint specification element 14 'is rotationally fixed to the output shaft 146 of the stepper motor 131 connected via an external spur gear with an internal straight toothing of the piston 66 ' with this is in mesh-free engagement.
  • the setpoint-setting piston 66 'of the follow-up control valve 14' which is rotatably mounted in a pressure-tight manner in the central through bore 69 'of the sleeve-shaped housing element 99', which in turn is located in the bore 113 'centrally penetrating the connection block 114' of the follow-up control valve 14 ' of the connection block 114 'of the follow-up control valve 14', which is rotatably mounted in a pressure-tight manner about its central longitudinal axis 68 ', is connected in a rotationally fixed manner to a stop angle, generally designated by 147, which between free leg ends 148 and 149 (FIGS.
  • leg spring 151 protrudes leg spring, which is under an azimuthal bias, through which the free leg ends are exposed to oppositely directed azimuthal forces and are urged against opposite stop surfaces of the stop bracket 147.
  • the leg spring 151 is secured against rotation about the central longitudinal axis 68 'and, as a result of this, as well as its pretension, which is sufficient to overcome a holding torque which the stepper motor 131 still exerts in the de-energized state, the effect that the setpoint value Specification piston 66 'in the de-energized state of the stepping motor 131 reaches the defined azimuthal position ⁇ 0 shown in FIGS. 2 and 2a, which is assigned to the neutral central position 0 of the main control valve 11' shown as the setpoint specification position.
  • leg spring 151 and the stop arm 147 functionally the valve springs 118 and 119 of the "linear" Follow-up control valve 14 according to FIG. 1 corresponding reset device 147, 151 of the rotary slide valve control valve 14 'according to FIG. 2 is implemented in more detail as follows:
  • the stop bracket 147 comprises a stable, one section the output shaft 146 of the stepper motor 131 coaxially enclosing Fixing sleeve 152 on its valve side End is provided with an internal spur gear that with a short section of the outer splines of the output shaft 146 of the stepper motor 131 in meshing engagement stands and thereby rotatably connected to this output shaft 146 is.
  • the fixing sleeve 152 is by grub screws 153 against axial displacements with respect to the drive shaft 146 secured.
  • the leg spring 151 has the central axis 68 'of Follower control valve 14 'coaxial windings 158 of the same inner diameter, of the illustrated special embodiment equal to the diameter of bore 113 'of the terminal block 114 'of the follow-up control valve 14'.
  • the central longitudinal axis 162 of the anchor pin and the central longitudinal axis 163 of the stop pin 161 run parallel to the central longitudinal axis 68 'of the follow-up control valve 14 ', with the central longitudinal axis 163 of the Stop pin 161 and the central longitudinal axis 68 'of the follow-up control valve 14 'defines a "middle" radial plane 164 is also in the central longitudinal axis 157 of the stop leg 156 of the stop angle 147 extends, as well also its radial central plane 166, if the central one Piston 66 'of the follow-up control valve 14' in its basic position 0 of the main control valve 11 'assigned setpoint specification position located.
  • the leg spring 151 has four "inner”, self-contained windings 158 in the exemplary embodiment selected for explanation, which run radially from the fixing sleeve 152 of the stop bracket 147 and these each with the enclose a full circumferential angle of 360 ', and on each end of the leg spring an end turn 167 or 168 which, based on the housing-fixed, was marked by the central longitudinal axes 68' and 163 of the follow-up control valve 14 'or the stop pin 161 Radial plane 164 of orientation ⁇ 0 only extends over part of the circumference of inner turns 158. At these terminal partial windings 167 and 168, as can best be seen in FIG. 2a, the radially or approximately radially extending free leg ends 148 and 149 of the leg spring 151 connect with a smooth curvature which corresponds approximately to that of the stop pin 161.
  • One of the central turns between two "complete” turns 158 completely enclosing the fixation sleeve is arranged is within an azimuthal angular range of a total of about 60 ° with a U-shaped, radial bulge 169 provided by the anchor pin 159, the arranged diametrically opposite the stop pin 161 is, the form-fitting encompassing arrangement on the outside Leg spring 151 in the arrangement shown in FIG. 2a against rotation about the central longitudinal axis 68 'of the Follow-up control valve 14 'is secured.
  • the leg spring 151 In the relaxed state shown in FIG. 2b the leg spring 151 corresponding configuration thereof the partial turns 167 and 168 only extend over one - On the running between the free leg ends 148 and 149 Longitudinal median plane 171 related - peripheral area of about 160 °, so that between their free leg ends 148 and 149 a "clear" azimuthal distance of approximately 40 ° remains, i.e. a positive overlap of the terminal partial turns 167 and 168 is not given in the circumferential direction.
  • the setpoint specification piston 66 'of the follow-up control valve 14' in that Orientation that corresponds to the home position 0 of the Main control valve 11 'is assigned required azimuthal
  • the torsion spring 151 is impressed by preloading that these are pulled out during assembly in the in Fig. 2a Is presented in the configuration shown in the lines the outer, terminal partial turns 167 and 168, radially passing within the stop pin 161, on a circumferential area due to its diameter overlap and with their radial free Leg ends 148 and 149 each face away from each other Support the sides of the stop pin 161 on this - azimuthally.
  • the stepping motor 131 is positioned with the orientation of its stop angle 147 in which the stop leg 156 of the stop angle 147 radially outside the stop pin 161 engages between the free leg ends 148 and 149 of the partial windings 167 and 168 and is fixed in this position on the housing block 114 'of the follow-up control valve 14', which results in the radial orientation ⁇ 0 of the radial plane 164 of the stop angle 147, which with the output shaft of the stepper motor 131 is non-rotatably connected, the basic position 0 of the follow-up control valve 14 and
  • the overrun control valve 14 ' is designed so that it through a controllable rotation of its by means of the stepping motor 131 central valve piston 66 'in the direction of arrow 172 of Fig. 2a, i.e. seen in the direction of arrow 173 of Fig.
  • the main control valve is in an analogous manner 11 'by stepper motor controlled azimuthal rotation of the central piston 66 'of the follow-up control valve 14' in the direction of arrow 174 of FIG. 2a into its functional position II controllable, in which its valve piston 16 'related to its neutral center position 0, a deflection "after right "experienced with the azimuthal deflection of the central Follow-up control valve piston 66 'correlates monotonously is.
  • the main control valve 11 'and the wake control valve 14' of the control valve arrangement 10 'according to FIG. 2 are coordinated with one another in such a way that the maximum deflections ⁇ 1max and ⁇ 2max of the piston 16' of the main control valve 11 'in the sense of taking up the functional position I or II Azimuthal deflections ⁇ 1max or ⁇ 2max of the piston 66 'in the direction of arrows 172 and 174 of FIG. 2a correspond, which are each 30 °, as in FIG. 2a due to the azimuthal orientations ⁇ 1max and ⁇ 2max of the radial central plane 166 represents the stop angle 147 of the follow-up control valve 14 '.
  • the movement of the piston 16 'into translatory movements of the piston 16' in the direction of the central longitudinal axis 18 of the main control valve 11 'into rotational "feedback" movements of the sleeve-shaped feedback element 99' of the follow-up control valve 14 ' is as a slimmer, from the annular end edge 176 of the sleeve-shaped housing part 99 'of the follow-up control valve 14' is formed, provided at its end with a spherical head 177 rod 178, the central longitudinal axis 179 of which runs parallel to the central longitudinal axis 68 'of the follow-up control valve.
  • the diameter of the spherical head 177 of the coupling element 143 corresponds, apart from an undersize of a few hundredths of a millimeter, to the clear width of the annular groove 144 of the piston 16 ', into which the coupling element 143 projects radially or approximately radially.
  • the thickness of the rod-shaped part 178 of the coupling element 143 is smaller than the diameter of its spherical head 177.
  • This tensioning device 18 comprises a helical spring 183 which is under tension, on an azimuthal region which is slightly smaller than that of the total swivel range ⁇ 1max - ⁇ 2max of the sleeve-shaped housing part 99 'of the follow-up control valve 14' to a complementary angle of 360 °, from an outer, concave groove 184 of an only slightly extended in the axial direction, from the central bore 113 'of the connection block 114' to the main control valve 11 'protruding end portion 186 (Fig. 2) of the sleeve-shaped housing part 99 'is received.
  • the radius of curvature of this groove 184 is slightly larger than that of the spring coils, which are received by this concave groove 184 with a radially inner 180 ° region and are supported at the bottom thereof.
  • the short end section 186 of the sleeve-shaped housing part 99 'of the follow-up control valve 14' used as a mechanical feedback element passes through one relative to the central bore 113 'of the connection block 114' of the follow-up control valve 14 ', in which the sleeve-shaped housing part 99' is arranged so that it can be rotated in a pressure-tight manner over sections of its length , Extended bore step 187, the diameter of which is slightly larger than the outer diameter of the helical spring 183, the radial clear width of the annular gap 188 remaining between the bore step 187 and the outer circumferential surface of the end section 186 of the sleeve-shaped housing part 99 'carrying the helical spring 183 being smaller than that Diameter of the individual spring coils
  • the central valve piston 66 ' is in that of the end portion 186 of the sleeve-shaped housing part 99 'on the azimuthal range of approximately 300 ° coaxially enclosed, from the central bore 113 'of the terminal block 114' to Main control valve 11 'exiting area a stop pin 189 firmly inserted, the radial one-sided in the "free" Annular gap region 188 'protrudes, the azimuthal width by the azimuthal distance of radial end faces 191 and 192 is determined, which extends in the axial direction over the depth - axial extension - of the end section carrying the coil spring 183 186 of the sleeve-shaped housing part 99 'of the follow-up control valve 14 'extend.
  • the design of the sleeve-shaped housing part 99 'of the follow-up control valve 14' and the orientation of the stop pin 189 which is fixedly connected to the setpoint specification piston 66 'of the follow-up control valve 14' are coordinated with one another in such a way that the position setpoint value and actual position value of the Piston 16 'of the main control valve 11' corresponding to the central position 0 of the follow-up control valve 14 ', the radial plane containing the central longitudinal axis 193 of the stop pin 189 and the central longitudinal axis 68' of the follow-up control valve 14 'bisects the angle ⁇ by the radial end faces 191 and 192 of the helical spring 183 enclose supporting end portion 186 of the sleeve-shaped housing part 99 '.
  • This angle ⁇ is chosen to be sufficiently large that the central piston 66 'can be rotated clockwise and counterclockwise with respect to the sleeve-shaped housing part 99' in relation to the illustrated central position of the stop pin 189 by the maximum actuation angles ⁇ 1max and ⁇ 2max , without this backlash-free engagement with the piston 16 'of the main control valve 11' could be canceled.
  • One end 194 of the helical spring 183 is at the free end section 189 'of the stop pin 189 attached while the other end 196 in the immediate vicinity of the radial end face 192, fixed to the sleeve-shaped housing part 99 ' whose azimuthal distance from the stop pin 189 is seen about the azimuthal in the direction of the spring 183 Alignment corresponds.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Sliding Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Fluid-Driven Valves (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (15)

  1. Ensemble de distributeur de commande électro-hydraulique pour commander le flux entrant et sortant de fluide hydraulique d'un moteur hydraulique (17) linéaire ou rotatif, avec un distributeur de commande principal (11) réalisé sous forme de distributeur à trois positions, qui possède un piston (16) pouvant être déplacé, dans un perçage (19) de son boítier, dans des directions alternatives entre des positions finales qui correspondent à des montants maximaux de sections de chemins d'écoulement qui sont libérées dans des positions fonctionnelles alternatives I et II du distributeur de commande principal, sections qui sont progressivement libérées, de façon essentiellement proportionnelle à l'excursion, avec l'augmentation de l'excursion du piston à partir d'une position médiane fonctionnellement neutre, et qui sont réduites d'une manière correspondante lorsque le piston se rapproche de sa position médiane, les excursions du piston pouvant être commandées, au moyen d'un ensemble de distributeur électro-hydraulique de pilotage (14) qui est dirigé électriquement en fonction d'une valeur de consigne, par des alternances d'alimentation en pression et d'évacuation de la pression de deux chambres de commande du distributeur de commande principal, caractérisé par les caractéristiques suivantes :
    a) il est prévu comme ensemble électro-hydraulique de pilotage un distributeur électro-hydraulique de régulation par poursuite (14 ; 14'), qui travaille avec allocation de consigne de position à commande électromécanique et quittance mécanique de valeur réelle de position,
    b) le distributeur de régulation par poursuite (14 ; 14') comprend un élément de boítier (99 ; 99') en forme de manchon, qui est disposé dans un bloc de raccordement (114, 114') fixement assemblé au boítier du distributeur de commande principal (11 ; 11') et qui est mobile en étanchéité à la pression par rapport à ce bloc, et un élément de piston (66 ; 66'), lui-même disposé en étant mobile en étanchéité à la pression dans l'élément de boítier (99 ; 99'), l'un de ces éléments servant d'élément d'allocation de valeur de consigne qui, au moyen d'un moteur électrique asservissable (131), peut être entraíné dans des directions alternatives afin d'accomplir des excursions incrémentielles par rapport à l'autre élément, qui sert d'élément de quittance de valeur réelle de position, qui est couplé en déplacement au piston (16 ; 16') du distributeur de commande principal (11 ; 11') par liaison à force et positive et peut ainsi être entraíné afin d'accomplir des mouvements de poursuite de même sens que les excursions de l'élément d'allocation de consigne,
    c) le distributeur de régulation par poursuite (14 ; 14') est pourvu d'un ensemble de ressort de soupape (118, 119; 151) qui, à l'état non asservi du moteur d'allocation de consigne (131), règle l'élément d'allocation de consigne à la position d'allocation de consigne qui est associée à la position médiane fonctionnellement neutre du distributeur de commande principal (11 ; 11').
  2. Ensemble de distributeur de commande selon la revendication 1, caractérisé en ce que le distributeur de commande principal (11) et le distributeur de régulation par poursuite (14) sont réalisés sous forme de soupapes à tiroirs linéaires qui sont disposées avec une allure parallèle de leurs axes longitudinaux centraux (18, 68), l'élément de quittance (99) du distributeur de régulation par poursuite (14) étant lié en translation axiale au piston (16) du distributeur de commande principal (11) et l'élément d'allocation de consigne (66) du distributeur de régulation par poursuite (14) pouvant être déplacé axialement en va-et-vient au moyen d'un entraínement linéaire électrique.
  3. Ensemble de distributeur de commande selon la revendication 1, caractérisé en ce que le distributeur de commande principal et le distributeur de régulation par poursuite sont réalisés sous forme de soupapes à tiroirs rotatifs qui sont disposées avec une allure parallèle, de préférence coaxiale, de leurs axes longitudinaux centraux, l'élément de quittance du distributeur de régulation par poursuite (14') étant lié en rotation au piston rotatif du distributeur de commande principal et l'élément d'allocation de consigne du distributeur de régulation par poursuite pouvant être déplacé azimutalement dans des directions alternatives au moyen d'un entraínement électrique en rotation.
  4. Ensemble de distributeur de commande selon la revendication 1, caractérisé en ce que le distributeur de commande principal est réalisé sous forme de soupape à tiroir rotatif et le distributeur de régulation par poursuite sous forme de soupape à tiroir linéaire, et en ce qu'il est prévu un mécanisme de transmission, qui transforme les excursions azimutales du piston du distributeur de commande principal en translations linéaires de l'élément de quittance du distributeur de régulation par poursuite, l'élément d'allocation de consigne de ce dernier pouvant être déplacé axialement en va-et-vient au moyen d'un entraínement linéaire électrique.
  5. Ensemble de distributeur de commande selon la revendication 1, caractérisé en ce que le distributeur de commande principal (11') est réalisé sous forme de soupape à tiroir linéaire et le distributeur de régulation par poursuite (14') sous forme de soupape à tiroir rotatif, dont l'élément de quittance de valeur réelle (99') est couplé en déplacement au piston (16') du distributeur de commande principal au moyen d'un mécanisme de couplage (143, 144) qui transforme les excursions linéaires du piston (16') du distributeur de commande principal (11') en excursions azimutales de l'élément de quittance de valeur réelle du distributeur de régulation par poursuite (14'), et dont l'élément d'allocation de consigne (66') est lié en rotation à l'arbre de sortie (146) du moteur électrique d'allocation de consigne (131).
  6. Ensemble de distributeur de commande selon la revendication 5, caractérisé en ce que le distributeur de régulation par poursuite (14') est rapporté sur le distributeur de commande principal (11') avec une allure perpendiculaire de son axe longitudinal central (68) par rapport à l'axe longitudinal central (18) du distributeur de commande principal (11'), en ce qu'on utilise comme élément de quittance de valeur réelle de position du distributeur de régulation par poursuite (14') l'élément de boítier (99') en forme de manchon de ce dernier, auquel est lié en rotation un élément de couplage (143) qui, par engagement positif avec un élément entraíneur (144) du piston (16') du distributeur de commande principal, transforme les excursions axiales de ce dernier en mouvements azimutaux de poursuite de l'élément de quittance (99').
  7. Ensemble de distributeur de commande selon la revendication 6, caractérisé en ce que l'élément entraíneur du piston (16') du distributeur de commande principal est réalisé sous forme de rainure annulaire (144) de ce piston, en ce que l'élément de couplage (143) pénètre dans l'élément entraíneur (144) par une partie terminale réalisée en forme de barre, s'étendant perpendiculairement à l'axe longitudinal central (18) du piston (16') et parallèlement à l'axe longitudinal central (68) du distributeur de régulation par poursuite (14'), et en ce que la disposition de la rainure (144) sur le piston (16') du distributeur de commande principal (11') et celle de l'élément de couplage (143) sur l'élément de quittance (99') du distributeur de régulation par poursuite (14') sont mutuellement adaptées en ce sens que, dans la position médiane fonctionnellement neutre du distributeur de régulation par poursuite (14'), le plan matérialisé par l'axe longitudinal de la partie (143) en forme de barre de l'élément de couplage et l'axe longitudinal central (68') du distributeur de régulation par poursuite (14') s'étend perpendiculairement à l'axe longitudinal central (18) du distributeur de commande principal (11').
  8. Ensemble de distributeur de commande selon la revendication 7, caractérisé en ce que l'extrémité d'engagement de l'élément de couplage (143), disposée entre les parois de la rainure annulaire (144), est réalisée sous forme de tête sphérique (177), dont le diamètre est supérieur à celui de la partie terminale en forme de barre et approximativement égal ou au plus égal à l'écartement, mesuré en direction axiale, entre les parois de la rainure annulaire (144) du piston (16') du distributeur de commande principal.
  9. Ensemble de distributeur de commande selon la revendication 7 ou 8, caractérisé en ce qu'il est prévu un dispositif de serrage (181), qui produit un couple actif en permanence entre l'élément de boítier (99') en forme de manchon et le piston (66') du distributeur de régulation par poursuite (14'), couple qui presse l'élément de couplage (143) en application à force et positive contre une paroi de la rainure annulaire (144) du piston (16') du distributeur de commande principal (11'), et dont le montant est inférieur au couple de maintien du moteur d'allocation de consigne (131), et également inférieur au couple de rappel exercé, lorsque l'alimentation en pression est en service, par le piston (16') sur l'élément de boítier (99') côté piston du distributeur de régulation par poursuite (14').
  10. Ensemble de distributeur de commande selon la revendication 9, le montant total Ø de l'excursion azimutale du piston (66') du distributeur de régulation par poursuite (14') par rapport à l'élément de boítier (99') en forme de manchon étant inférieur à 180°, de préférence égal à environ 90°, caractérisé en ce que la plage d'excursion azimutale Ø est limitée par l'action de butée d'une tige radiale fixement assemblée au piston (66') avec les délimitations azimutales d'un trou oblong s'étendant en direction circonférentielle de l'élément de boítier (99') en forme de manchon, ou d'un évidement en forme de secteur ouvert sur le bord et disposé sur le côté frontal, et en ce que le dispositif de serrage comprend un ressort spiral, se trouvant sous précontrainte de traction et fixé en position d'une part à l'extrémité libre de la tige et d'autre part sur l'élément de boítier (99') en forme de manchon, ressort qui est reçu sur la région circonférentielle, complémentaire de la plage de pivotement Ø, d'une gorge, ouverte sur le bord, de l'élément de boítier (99') en forme de manchon.
  11. Ensemble de distributeur de commande selon une des revendications 1 à 10, caractérisé en ce que l'ensemble de ressort de soupape, qui à l'état non asservi du moteur d'allocation de consigne (131) presse l'élément d'allocation de consigne (66 ; 66') dans sa position d'allocation de consigne liée à la position médiane (0) du piston (16 ; 16') du distributeur de commande principal, comprend deux ressorts de pression précontraints (118, 119), qui agissent dans des directions opposées sur l'élément d'allocation de consigne du distributeur de régulation par poursuite ou sur une pièce fixement assemblée à cet élément.
  12. Ensemble de distributeur de commande selon la revendication 11, caractérisé en ce que la précontrainte des ressorts de pression (118, 119) est réglable.
  13. Ensemble de distributeur de commande selon la revendication 11 ou 12, caractérisé en ce que les courses de relâchement des ressorts de soupape (118, 119) sont limitées, en entravant les ressorts, au montant pour lequel est atteinte la position de l'élément d'allocation de consigne qui est liée à la position médiane (0) du piston (16 ; 16') du distributeur de commande principal.
  14. Ensemble de distributeur de commande selon une des revendications 5 à 10, caractérisé en ce que l'ensemble de ressort de soupape, qui à l'état non asservi du moteur d'allocation de consigne (131) presse l'élément d'allocation de consigne (66 ; 66') dans sa position d'allocation de consigne liée à la position médiane (0) du piston (16 ; 16') du distributeur de commande principal, comprend un ressort à branches (151) azimutalement précontraint, qui est réalisé sous forme de ressort spiral dont les spires entourent coaxialement l'axe central (68) du distributeur de régulation par poursuite (14 ; 14') et qui comporte deux extrémités libres de branches, partant de ses spires partielles terminales et se raccordant à ces dernières avec une allure radiale ou approximativement radiale, entre lesquelles sont disposés un tenon de butée, fixement assemblé au bloc de raccordement (114') du distributeur de régulation par poursuite (14'), et une branche de butée (156) liée en rotation à l'élément d'allocation de consigne.
  15. Ensemble de distributeur de commande selon la revendication 14, caractérisé en ce qu'au moins une des spires (158) du ressort à branches (151) entourant coaxialement l'axe central du distributeur de régulation par poursuite (14') est pourvue d'un renflement, qui s'engage positivement autour d'un tenon de butée fixement assemblé au bloc de raccordement (114') du distributeur de régulation par poursuite (14') et s'étendant parallèlement à l'axe longitudinal central (68) de ce dernier.
EP96933364A 1995-09-30 1996-09-24 Ensemble a vannes de regulation electrohydraulique Expired - Lifetime EP0853731B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19536553A DE19536553A1 (de) 1995-09-30 1995-09-30 Elektrohydraulische Steuerventilanordnung
DE19536553 1995-09-30
PCT/EP1996/004156 WO1997013074A2 (fr) 1995-09-30 1996-09-24 Ensemble a vannes de regulation electrohydraulique

Publications (2)

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EP0853731A2 EP0853731A2 (fr) 1998-07-22
EP0853731B1 true EP0853731B1 (fr) 2000-12-06

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EP96933364A Expired - Lifetime EP0853731B1 (fr) 1995-09-30 1996-09-24 Ensemble a vannes de regulation electrohydraulique

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US (1) US6039077A (fr)
EP (1) EP0853731B1 (fr)
JP (1) JP3242115B2 (fr)
AT (1) ATE197985T1 (fr)
DE (2) DE19536553A1 (fr)
WO (1) WO1997013074A2 (fr)

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WO2017151618A1 (fr) * 2016-03-02 2017-09-08 Moog Inc. Valve de régulation de pression de débit centrale fermée
CN108825818A (zh) * 2018-08-27 2018-11-16 东莞海特帕沃液压科技有限公司 一种用于非道路车辆的防打滑控制阀
US10344888B2 (en) 2014-10-01 2019-07-09 Moog Inc. Two-stage closed center electro-hydraulic valve

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CN102261483B (zh) * 2011-04-20 2012-11-28 上海交通大学 采用螺旋阀口的液压滑阀
SE538239C2 (sv) * 2013-07-08 2016-04-12 Freevalve Ab Aktuator för axiell förskjutning av ett objekt
CN104514763B (zh) * 2014-12-30 2017-01-18 南京萨伯工业设计研究院有限公司 改进型伺服控制阀及其控制方法
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US10344888B2 (en) 2014-10-01 2019-07-09 Moog Inc. Two-stage closed center electro-hydraulic valve
WO2017151618A1 (fr) * 2016-03-02 2017-09-08 Moog Inc. Valve de régulation de pression de débit centrale fermée
CN109072949A (zh) * 2016-03-02 2018-12-21 莫戈公司 闭式中央压力流量控制阀
US10180194B2 (en) 2016-03-02 2019-01-15 Moog Inc. Closed center pressure flow control valve
CN109072949B (zh) * 2016-03-02 2020-06-16 莫戈公司 闭式中央压力流量控制阀
US10865905B2 (en) 2016-03-02 2020-12-15 Moog Inc. Closed center pressure flow control valve
CN108825818A (zh) * 2018-08-27 2018-11-16 东莞海特帕沃液压科技有限公司 一种用于非道路车辆的防打滑控制阀

Also Published As

Publication number Publication date
ATE197985T1 (de) 2000-12-15
JP3242115B2 (ja) 2001-12-25
JPH10510616A (ja) 1998-10-13
DE19536553A1 (de) 1997-04-03
WO1997013074A3 (fr) 1997-05-01
US6039077A (en) 2000-03-21
EP0853731A2 (fr) 1998-07-22
WO1997013074A2 (fr) 1997-04-10
DE59606197D1 (de) 2001-01-11

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