EP3258116B1 - Module hydraulique avec soupape de régulation 2-voies contrôlé par pression - Google Patents

Module hydraulique avec soupape de régulation 2-voies contrôlé par pression Download PDF

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Publication number
EP3258116B1
EP3258116B1 EP16174633.4A EP16174633A EP3258116B1 EP 3258116 B1 EP3258116 B1 EP 3258116B1 EP 16174633 A EP16174633 A EP 16174633A EP 3258116 B1 EP3258116 B1 EP 3258116B1
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EP
European Patent Office
Prior art keywords
control
pressure
valve
way flow
controlled
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Application number
EP16174633.4A
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German (de)
English (en)
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EP3258116A1 (fr
Inventor
Thomas Wechsel
Fridolin EISELE
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • 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
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • 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
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control valves

Definitions

  • the present invention relates to a hydraulic module according to the preamble of independent claim 1 and in particular to a hydraulic module with a pressure-controlled 2-way flow control valve.
  • proportional directional spools with a 2-way flow control valve are generally used to enable the simultaneous actuation of several consumers and / or to set a travel speed on one consumer. For example, in practice it is often necessary to control several consumers independently of the load pressure.
  • a proportional directional spool valve type PSL with connection blocks and an add-on block is known.
  • Fig. 1a is schematically an exemplary known hydraulic circuit with two proportional directional spool valves of the type PSL, in Fig. 1a denoted by the reference numerals PS1, PS2, and a suitable connection block for a constant pump 1 for operating two consumers V1, V2.
  • a supply pressure P output by the constant pump 1 is supplied through a supply line 6 to a plurality of consumers V1, V2, for example hydraulic cylinders, shown in a highly schematic manner via the respective proportional directional spool valves PS1, PS2 in order to drive the consumers V1, V2.
  • the inflow upstream of the proportional directional spool valves PS1, PS2 is regulated in each case by a pressure-controlled 2-way flow control valve 41, 42, which is upstream of the corresponding proportional directional spool valve PS1, PS2 (ie, upstream of the corresponding proportional directional spool valve PS1, PS2 ) is arranged. If at least one of the consumers V1, V2 is operated during operation, the associated proportional directional spool valve PS1, PS2 is deflected upwards or downwards from the blocking state shown, depending on whether a connection A1, A2 connected to the corresponding consumer V1, V2 or B1, B2 to be connected to the supply line 6. Via the stroke of the deflection, a volume flow to the respective consumer V1, V2 is predetermined by the proportional directional spool valves PS1, PS2, for example in order to set a speed at the corresponding consumer V1, V2.
  • the load pressure reported by the LS line LS1 or LS2 to the 2-way flow control valve 41 or 42 is applied to the 2-way flow control valve 41 or 42 in the up-control direction to support the biasing force of the biasing spring. Furthermore, each 2-way flow control valve 41, 42 is also applied with a pressure signal tapped on the output side of the respective 2-way flow control valve 41, 42 in the closed control direction (i.e. counteracting the bias) of the respective 2-way flow control valve 41, 42.
  • Each of the 2-way flow control valves 41, 42 is biased in the open control direction by a biasing spring, so that the 2-way flow control valves 41, 42 are opened in the idle state.
  • the volume flow to the consumer and the pressure difference between the pressure provided by the constant pump 1 and the pressure in the load circuit to the consumer are regulated to a constant value.
  • the 2-way flow control valve is controlled in the closed-control direction until a new force balance is established.
  • a control piston moves in the closed control direction and a throttle cross-section in the 2-way flow control valve 41 or 42 decreases.
  • the volume flow and the pressure difference (p A - p LS ) again (which counteracts the initial increase) and an equilibrium of forces is established in which the increase in the volume flow and the pressure difference are compensated.
  • Fig. 1b is the resulting characteristic of the 2-way flow control valve (cf. 41, 42 in Fig. 1a ) and the proportional directional spool (cf. PS1, PS2 in Fig. 1a ) is shown schematically.
  • a volume flow Q is plotted along the abscissa in arbitrary units against a pressure difference ⁇ p (corresponds to the pressure loss across the 2-way flow control valve and the proportional directional spool valve) along the ordinate in arbitrary units.
  • the characteristic curve has three sections: in section a1 the 2-way flow control valve is fully open and the characteristic curve follows the dynamic pressure characteristic curve (the dynamic pressure is proportional to the flow velocity and the dynamic pressure curve shows that the pressure loss is proportional to Q 2 ).
  • a section a2 of the characteristic curve represents the transition between the dynamic pressure characteristic curve and a desired control of the 2-way flow control valve, the control behavior of the 2-way flow control valve depending on the mechanical properties of the preload spring and the reported pressure signals via the LS line and in the tap directly after the 2-way flow control valve.
  • the characteristic curve deviates in section a2 from the dynamic pressure characteristic and even small changes in ⁇ p lead to relatively large (in comparison to section a3) changes in the volume flow, so that no stable control is possible here.
  • the control functions in a stable manner and the volume flow can be kept constant, independently of the load pressure and independent of pressure fluctuations, at a value Q 0 , which is essentially predetermined by the proportional directional spool and means, for example, a desired speed at the consumer.
  • Q 0 which is essentially predetermined by the proportional directional spool and means, for example, a desired speed at the consumer.
  • a change in the spool position of the proportional directional spool valve leads to a different volume flow, which is to be kept pressure-dependent by the 2-way flow control valve.
  • the pressure losses represented by the characteristic curve lead to a power loss of ⁇ p * Q, which dissipates into the heating of a hydraulic medium.
  • the course of the characteristic curve in section a2 deviates from the course in section a1 and the pressure losses in section a2 are greater than in section a1.
  • Section a2 is energetically unfavorable compared to section a1.
  • a hydraulic module of this type is from the publication DE 4420459 already known.
  • a hydraulic module with a pressure-controlled 2-way flow control valve with a pressure-controlled 2-way flow control valve.
  • the pressure-controlled 2-way flow control valve is arranged in a supply line of the hydraulic module and is biased in the open control direction by a first biasing element. Downstream or upstream of the pressure-controlled 2-way flow control valve, a first pressure signal is tapped in the supply line and the first pressure signal can be applied to the pressure-controlled 2-way flow control valve in the closed-control direction or open-control direction via a first control line.
  • a control device is also arranged in the first control line for pressure control of the pressure-controlled 2-way flow control valve.
  • the control device is configured so that application of the first pressure signal to the pressure-controlled 2-way flow control valve is blocked in a first control state. In a second control state, the first pressure signal can be applied by the control device to the pressure-controlled 2-way flow control valve in the closed control direction.
  • the pressure-controlled 2-way flow control valve is controlled in such a way that a deviation of a pressure loss or differential pressure across the pressure-controlled 2-way flow control valve from a course according to a dynamic pressure characteristic curve is determined by the control device and thus energy losses can be kept low. and the entry into stable control mode in the hydraulic module can be reliably provided by the pressure-controlled 2-way flow control valve.
  • the first control line upstream of the pressure-controlled 2-way flow control valve can be tapped in the supply line.
  • the hydraulic module can further comprise a first signal line, which is branched upstream of the control device in the first control line, the control device being switchable to the first or second control state depending on a pressure signal tapped by the first signal line.
  • the first control line upstream of the pressure-controlled 2-way flow control valve can be tapped in the supply line.
  • the hydraulic module can further comprise a second control line, which is connected to the supply line upstream of the pressure-controlled 2-way flow control valve.
  • the control device can be switched to the second control state depending on a second pressure signal tapped by the second control line.
  • control device can comprise a pressure-controlled 2-way valve, which is actuated by a second biasing element (for example in the closed control direction if the first pressure signal is applied in the closed control direction; otherwise in the open control direction if the first pressure signal is in the open position Control direction is applied) is biased.
  • the pressure-controlled 2-way valve is controlled in the closed control direction or open-control direction in the first control state, while it is open-controlled or closed-control in the second control state, so that the first pressure signal depends on the control state of the control device to the pressure-controlled 2 -Way flow control valve can be applied or can be blocked.
  • the second pressure signal can be applied to the pressure-controlled 2-way valve in the closed-control direction via the second control line.
  • the pressure-controlled 2-way flow control valve is completely open-controlled in the first control state of the control device if the first pressure signal is tapped downstream of the 2-way flow control valve. Otherwise, the pressure-controlled 2-way flow control valve can be completely open-controlled in the second control state of the control device if the first pressure signal is tapped upstream of the 2-way flow control valve.
  • the hydraulic module can further comprise a third control line, which is connected downstream of the pressure-controlled 2-way flow control valve to the supply line, a third pressure signal being applied to the pressure-controlled 2-way flow control valve in the open-control direction via the third control line can be.
  • the third control line can be connected to the supply line downstream of a proportional slide valve arranged downstream in the supply line or in front of a consumer in order to tap a pressure signal corresponding to a consumer pressure via the third control line, pressure control of the 2-way flow control valve taking into account a Pressure downstream of the 2-way flow control valve, e.g. consumer pressure.
  • the hydraulic module can further comprise a fourth control line, which is connected to the third control line, wherein the third pressure signal can be applied to the control device via the fourth control line.
  • the control device can thus be switched to the first control state depending on the third pressure signal. This allows regulation depending on the third pressure signal.
  • the third pressure signal can be applied to the pressure-controlled 2-way flow control valve in the closed control direction in the first control state of the control device.
  • the control device can advantageously implement a control of the 2-way flow control valve that is dependent on the third pressure signal.
  • the hydraulic module can further comprise a proportional directional spool, which is arranged in the supply line downstream of the pressure-controlled 2-way flow control valve.
  • the first pressure signal can be tapped upstream of the proportional directional spool.
  • the third pressure signal can be tapped downstream of the proportional directional spool.
  • the 2-way flow control valve and the control device can be integrated in a valve block. This makes it easy to install the hydraulic module in existing hydraulic systems and / or replace it if necessary.
  • control device can comprise an adjustable prestressing element, by means of which the control device is prestressed in the first control state.
  • the time of switching between the first and second control states of the control device can be set in a user-dependent manner.
  • control device can only have the first and second control states as two discrete switching positions. This represents a simple structure for a control device.
  • a hydraulic module system comprising at least two hydraulic modules, only one of the at least two hydraulic modules being designed according to the hydraulic module according to the aspect described above.
  • Fig. 2 14 schematically shows a hydraulic module 100 according to some illustrative embodiments of the invention.
  • the hydraulic module 100 can, for example, be integrated in a valve block or alternatively can be composed of different sub-modules.
  • the hydraulic module 100 comprises a supply line 105 which is connected to a supply unit, for example a constant pump (such as in FIG Fig. 1a is shown) or a variable displacement pump, in order to supply the hydraulic module 100 with a hydraulic medium, for example a hydraulic oil or the like.
  • the supply line 105 is kept at a supply pressure P.
  • the hydraulic module 100 has a proportional directional spool 110 arranged in the supply line 105, through which the supply line 105 can be connected to one of two consumer lines A, B.
  • a hydraulic consumer (not shown), for example a hydraulic cylinder, can be connected to the consumer lines A, B.
  • a pressure-controlled 2-way flow control valve 120 is arranged upstream of the proportional directional spool valve 110 in the supply line 105.
  • a tank line (not shown) is also shown, which is connected to a tank connection R and can be coupled to a reservoir (not shown).
  • the proportional spool 110 can be controlled electromagnetically in order to set a suitable stroke of the proportional spool 110, so that one of the three switch positions shown is adopted. In the switching position shown, the proportional directional spool valve 110 blocks a passage through the supply line 105. In the other two switching positions of the proportional directional spool valve 110, either the consumer line B is connected to the supply line 105 (upper switching position), or the consumer line A becomes the supply line 105 connected (lower switching position). In the upper and lower switching position, a volume flow from the supply line 105 into one of the consumer lines A, B proportional to the stroke of the proportional directional spool valve 110 is set, for example, via a control edge (not shown) in the proportional directional spool valve 110.
  • a desired speed can be set on a hydraulic consumer (not shown), for example a hydraulic cylinder.
  • the pressure-controlled 2-way flow control valve 120 permits pressure-independent control of the volume flow to the consumer to a constant value, as specified by the proportional directional spool valve 110.
  • the 2-way flow control valve 120 is pressure-controlled via a control device 130.
  • the control device is arranged in a first control line 123, which taps a first pressure signal downstream of the 2-way flow control valve 120, which can optionally be applied by the control device 130 in the closed control direction of the 2-way flow control valve 120 or in the illustrated state of the control device 130 is blocked and therefore cannot be applied to the 2-way flow control valve in the closed control direction.
  • the control device 130 can, according to illustrative embodiments, as in FIG Fig. 2 is shown as an example, designed as a 2-way valve with two discrete switching positions.
  • first control state 132 of the control device 130 application of the first pressure signal via the first control line 123 in the closed control direction to the 2-way flow control valve 120 is blocked.
  • second control state 134 of the control device 130 the first pressure signal tapped by the first control line 123 can be applied to the 2-way flow control valve 120 in the closed control direction.
  • the control device 130 can be controlled as a function of a signal 136.
  • the signal 136 represent a hydraulic control signal.
  • the signal 136 can represent an electromagnetic control signal (for example an electrical signal for actuating an electromagnet, which can optionally set the first control state 132 or the second control state 134).
  • a pressure sensor may be disposed in the supply line 105 upstream of the 2-way flow control valve 120 and / or downstream of the 2-way flow control valve 120 and / or downstream of the proportional directional spool valve 110, so that control of the control device 130 into a desired control state of the first and second control states 132, 134 depending on the at least one tapped pressure signal.
  • the 2-way flow control valve 120 is prestressed in the open control direction by means of a prestressing element 122, for example a mechanical spring element. According to specific illustrative examples herein, the 2-way flow control valve may be fully open only by the action of the biasing member 122 in the up-control direction. Downstream of the 2-way flow control valve, for example downstream of the proportional directional spool valve 110, an LS pressure signal is applied to the 2-way flow control valve 120 in the up-control direction by means of an LS line LS1 in support of the biasing by the biasing element 122.
  • a throttle element can be provided in the LS line LS1 in order to set a desired throttling in the LS line LS1.
  • the control device 130 is switched to the first control state 132, the first pressure signal is applied to the 2-way flow control valve 120 in the closed control direction, in particular only the biasing element 122 and possibly the LS pressure signal act via the LS line LS1 in Up-control direction Up-controlling to the 2-way flow control valve 120.
  • the 2-way flow control valve can be completely open-controlled in the first control state 132.
  • a volume flow through the 2-way flow control valve 120 and the proportional directional spool valve 110 in the first control state 132 is thus set to a maximum corresponding to the stroke of the proportional directional spool valve 110.
  • the volume flow through the proportional directional spool valve 110 thus essentially follows a dynamic pressure characteristic curve, ie the pressure loss across the proportional directional spool valve 110 and the 2-way flow control valve 130 is essentially proportional to the square of the volume flow rate and indirectly proportional to the control cross section in the proportional directional spool valve 110
  • the control device 130 is now controlled in the second control state 134
  • the first pressure signal is activated, which is now applied to the 2-way flow control valve 120 in the closed control direction by the first control line 123 and thus the effect of the biasing element 122 and can at least partially compensate the LS pressure signal, in particular a function as a pressure compensator for regulating the volume flow can be provided by the proportional directional spool valve 110.
  • the control signal 136 can, for example, regulate the control device 130 from the first control state 132 to the second control state 134 when the first pressure signal is sufficiently high, so that, in particular, a pressure balance function of the 2-way flow control valve 120 only takes place at higher pressure differences and thus a section the characteristic curve in accordance with section a2 in Fig. 1b is minimized or avoided as far as possible above.
  • the 2-way flow control valve 120 can be given a certain inertia, so that undesired rocking with an upstream further control valve (not shown) or an upstream control device for controlling a supply pump (not shown, for example with regard to 1a and 1b is described above), is prevented since regulation is not carried out in this case and thus the rocking is prevented by the decoupled regulating action of the 2-way flow regulating valve 120 in the first regulating state 132 of the regulating device 130.
  • Fig. 3 schematically shows a characteristic curve in a diagram in which a volume flow Q through the 2-way flow control valve 120 and the proportional directional spool valve 110 along the abscissa against a pressure difference ⁇ p LS across the 2-way flow control valve 120 and the proportional directional spool valve 110 is plotted along the ordinate.
  • the characteristic curve figure 3 has three sections, a characteristic curve course K1 (similar to section a1 in the characteristic curve) in a first section a indicative of small pressures in Fig. 1b ) corresponds to a dynamic pressure characteristic.
  • a characteristic curve course K1 similar to section a1 in the characteristic curve
  • a second section b the characteristic curve now gives way to Fig.
  • a characteristic curve curve S now designates a transition from the characteristic curve curve K2 corresponding to the dynamic pressure characteristic curve to stable control operation according to a characteristic curve curve K4.
  • Fig. 4 shows a hydraulic module 200 with a supply line 205 and a 2-way flow control valve 220 arranged in the supply line 205.
  • the 2-way flow control valve 220 can correspond to the 2-way flow control valve 120 in Fig. 2 be arranged in front of a proportional directional spool valve, as in Fig. 2 is shown according to the proportional directional spool 110.
  • a first control line 223 can be branched off downstream of the 2-way flow control valve 220 at a branch point 209, wherein a first pressure signal is tapped off from the supply line 205 downstream of the two-way flow control valve 220 by means of the first control line 223 at the branch point 209.
  • a control device 230 is arranged on the first control line 223.
  • the first control line 223 is connected to an input E of the control device 230.
  • At an output A of the control device 230 there is an end section 231 of the first control line 223, which is connected to a connection AS2 of the two-way flow control valve 220, so that a pressure medium in the end section 231 in the closed-control direction to the 2-way flow control valve 220 can act.
  • the 2-way flow control valve 220 is biased in the open control direction by a biasing element 222, for example a mechanical spring element, counter to the action of a pressure medium in the end section 231.
  • first control state 232 of the control device 230 a transmission of the first pressure signal in the first control line 223 at the input E of the control device 230 to an output A of the control device 230, and consequently into the end section 231 of the first control line 223.
  • the first pressure signal in the first control line 223 can enter the input E of the control device 230 and enter the end section 231 at the output A of the control device 230 in order to connect to the connection AS2 of the two-way flow control valve 220 in the closed control direction to act on this.
  • the control device 230 has a pretensioning element 235, for example a mechanical pretensioning element, which prestresses the control device 230 in the closed-control direction.
  • the prestressing element 235 can be adjustable or a prestressing can be set by the prestressing element 235. This means that, for example in the case of a mechanical pretensioning element, it can be set and / or exchanged by an operator or user of the hydraulic module, for example against a pretensioning element with different spring hardness, or a spring force can be changed. In this way, for example, a hard or soft switching characteristic of the control device 230 can be specified.
  • a hard prestressing element can mean a regulation from the first regulation state 232 into the second regulation state 234 at relatively high pressures in comparison with soft prestressing elements 235, at which even low pressures are sufficient for regulation from the first regulation state 232 into the second regulation state 234 are. Accordingly, a length of the section S in Fig. 3 on the basis of the preload element 235, since in the case of a relatively hard preload element or a relatively heavily preloaded preload element, the 2-way flow control valve is in the first control state 132 over a larger area and thus follows the dynamic pressure characteristic curve "longer".
  • a further control line 211 can be branched upstream of the 2-way flow control valve 220 at a branch point 207, by means of which a further pressure signal in the open control direction is applied to the control device 230 via the connection AS3 of the control device 230 against the action of the biasing element 235 can be.
  • a switch to the second control state 234 can take place from the first control state 232. It can thereby be set, for example, that the control device 230 can only be switched to the second control state 234 from a certain minimum pressure upstream of the two-way flow control valve 220.
  • an LS control line LS2 acts on the 2-way flow control valve 220 in addition to the biasing element 222 in the up-control direction, the LS control line LS2 on the up-control side being connected to a connection AS1 on the two-way flow control valve.
  • the LS control line LS2 can additionally branch into an optional control line 228 which, at an optional second input E ′ of the control device 230, applies an LS pressure signal tapped at the LS control line LS2, which is applied in the first control state 232 the output A of the control device 230 is transmitted and the first control state 232 of the control device 230 can additionally be applied to the 2-way flow control valve 220 in the closed control direction.
  • the 2-way flow control valve 220 is essentially open-controlled by the biasing element 222.
  • the control line 228 and the additional second input E ′ of the control device 230 cannot be provided.
  • control line 228 can also be branched into a further optional control line 229 before the input E ′ in order to apply the LS pressure signal tapped via the LS control line LS2 to the control device 230 on the control side in addition to the biasing element 235.
  • control line 228 can also be branched into a further optional control line 229 before the input E ′ in order to apply the LS pressure signal tapped via the LS control line LS2 to the control device 230 on the control side in addition to the biasing element 235.
  • contrary to what is shown in Fig. 4 also be dispensed with the second input E '.
  • Fig. 5 schematically shows one to Fig. 2 alternative embodiment, in which case the hydraulic module shown here can also be integrated, for example, in a valve block or alternatively can be composed of different sub-modules.
  • a pressure-controlled 2-way flow control valve 120 is provided, which is arranged upstream of a proportional directional spool valve 110 in a supply line 105, as well as in connection with Fig. 2 was described above.
  • the illustrated embodiment is the 2-way flow control valve 120 in the illustration of FIG Fig. 5 pressure-controlled via a control device 330.
  • the control device 330 is arranged in a first control line 323, which taps a first pressure signal upstream of the 2-way flow control valve 120, which can optionally be applied or blocked by the control device 330 in the up-control direction of the 2-way flow control valve 120.
  • the control device 330 may, according to illustrative embodiments, as in FIG Fig. 5 is shown as an example, designed as a 2-way valve with two discrete switching positions.
  • first control state 332 of the control device 330 application of the first pressure signal via the first control line 323 in the open control direction to the 2-way flow control valve 120 is permitted or enabled, in particular the control device 330 is opened in the first control state 332.
  • second control state 334 of the control device 330 the first pressure signal tapped by the first control line 323 is blocked and is not applied to the 2-way flow control valve 120, in particular the control device 330 is closed in the second control state 334.
  • control device 330 can be controlled as a function of a signal 336.
  • signal 336 may represent a hydraulic control signal.
  • signal 336 may represent an electromagnetic control signal (e.g., an electrical signal for actuation an electromagnet, which can selectively set the first control state 332 or the second control state 334).
  • a pressure sensor may be disposed in the supply line 105 upstream of the 2-way flow control valve 120 and / or downstream of the 2-way flow control valve 120 and / or downstream of the proportional directional spool valve 110, so that control of the control device 330 into a desired control state of the first and second control states 332, 334 depending on the at least one tapped pressure signal.
  • Fig. 5 can, by means of the control device 330, an LS pressure signal, which is applied via an LS line LS1 in the up-control direction to the 2-way flow control valve 120 to support the biasing by the biasing element 122, in the first control state with the first pressure signal or supported by this in the up-control direction to the 2-way flow control valve 120.
  • biasing element for example, a mechanical spring element that mechanically biases the 2-way flow control valve 120 in the open control direction.
  • a first pressure signal which is tapped in the supply line upstream of the 2-way flow control valve 120 by means of the first control line 323 and is applied to the 2-way flow control valve 120 in the up-control direction thereof, in addition to an LS pressure signal
  • the control device 330 If the control device 330 is switched to the first control state 332, it can be compared with a second pressure signal which is tapped downstream of the 2-way flow control valve 120, for example between the 2-way flow control valve and the proportional slide valve 110, via a second control line 339 and depending on the bias by the biasing element 122, a volume flow through the 2-way flow control valve 120 and the proportional directional spool 110 can be set based on the pressure difference between the first pressure signal and the LS pressure relative to the second pressure signal.
  • the 2-way flow control valve 120 can be completely open-controlled as long as the control device 130 is in the first control state 332. If the control device 130 is in the second control state 334, the 2-way flow control valve can generate a volume flow through the 2-way flow control valve 120 and the proportional directional spool valve 110 on the basis of the pressure difference between the LS pressure (tapped via the LS line LS1) and the second pressure signal can be set. Thus, in the second control state 334 of the control device 330, a volume flow through the 2-way flow control valve 120 and the proportional directional spool valve 110 can be set in accordance with the stroke of the proportional directional spool valve 110.
  • the 2-way flow control valve 120 has no regulating effect as long as the control device 330 is in the first control state 332.
  • the volume flow through the proportional directional spool valve 110 thus essentially follows a dynamic pressure characteristic curve, ie the pressure loss across the proportional directional spool valve 110 and the 2-way flow control valve 130 is essentially proportional to the square of the volume flow rate and indirectly proportional to the control cross section in the proportional directional spool valve 110 If the control device 330 is now controlled in the second control state 334, the first pressure signal, which is applied in the first control state 332 by the first control line 323 in the closed control direction to the 2-way flow control valve 120, and thus the effect of the biasing element 122 and the LS pressure signal added, blocked.
  • a function as a pressure compensator for regulating the volume flow through the proportional directional spool 110 depending on the LS pressure and the second pressure signal are provided. Since the time at which the first pressure signal is applied by the first control line 323 in the up-control direction to the 2-way flow control valve 120 depends on the control state of the control device 330 and in particular on the control signal 336, the time from which can be set with a suitable control signal 336 the 2-way flow control valve 120 acts as a pressure compensator.
  • control signal 336 can, for example, regulate the control device 330 from the first control state 332 to the second control state 334 with a sufficiently high first pressure signal, so that, in particular, a pressure balance function of the 2-way flow control valve 120 only takes place at higher pressure differences, and thus a section the characteristic curve in accordance with section a2 in Fig. 1b is minimized or avoided as far as possible above.
  • the 2-way flow control valve 120 can be given a certain inertia, so that undesired rocking with an upstream further control valve (not shown) or an upstream control device for controlling a supply pump (not shown, for example with regard to 1a and 1b is described above), is prevented since regulation is not carried out in this case and thus the rocking is prevented by the decoupled regulating action of the 2-way flow regulating valve 120 in the second regulating state 332 of the regulating device 330.
  • the explanations are now closed Fig. 3 above also on the in Fig. 5 illustrated embodiment can be transferred accordingly.
  • Fig. 6 is now an illustrative example of the in Fig. 5 illustrated embodiment described in more detail.
  • a hydraulic module 400 with a 2-way flow control valve 420 (corresponds to the 2-way flow control valve 120) Fig. 5 ) shown upstream in a supply line 405 a proportional spool valve, not shown, is arranged.
  • a first control line is branched off at a branch point 419.
  • the first control line is connected to an input E "of a control device 430, which corresponds to the representation in FIG Fig. 6 can be designed as a 2-way valve which is biased in the open control direction by a biasing element 435, for example a mechanical spring or the like.
  • a prestress provided by the prestressing element 435 can be adjustable, for example the prestressing element 435 can be exchangeable or the prestressing exerted by the prestressing element 435 can be set as desired by an operator using a tool.
  • a pressure signal can be tapped off in the first control line 423 by means of a first signal line 424 and can be applied to the control device 430 in the closed control direction of the control device 430 against the action of the biasing element 430.
  • the control device 430 can be connected on the output side (at an output A ′ of the control device 430) to a continuation 431 of the first signal line 423, which is connected to an LS line LS3 (similar to the LS lines LS1 and LS2).
  • a second signal line 429 is provided downstream of the control device 430, by means of which a pressure signal downstream of the control device 430 can be tapped in the first control line and can be applied to the control device 430 in the open control direction to support the biasing element 435.
  • the control device is regulated as a function of a pressure difference between the pressure signals which are tapped by the signal lines 424 and 429 in the first control line (relative to the pretension by the pretensioning element 435).
  • the control device 430 is controlled. This blocks transmission of the first pressure signal, which is tapped via the first control line 423, to the LS line LS3 and to the 2-way flow control valve 420.
  • the control device 430 can, depending on a pressure signal that is applied to the control device 430 via the first signal line 424, and a further pressure signal that is applied to the control device 430 via the second signal line 429, into a first control state 432 or a second control state 434 are brought, the first pressure signal in the first control state 432 by the control device 430 in the open control direction is applied to the 2-way flow control valve 420.
  • the second control state 434 application of the first pressure signal to the 2-way flow control valve 420 is blocked.
  • the 2-way flow control valve 420 can be closed in the first control state 432 of the control device, while in the second control state 434 of the control device 430 it is open-controlled, for example completely open-controlled.
  • the first pressure signal can be applied to the 2-way flow control valve 420 in the second control state 434 of the control device 430, while an application of the first pressure signal is blocked in the first control state 432 of the control device 430.
  • an LS pressure signal as shown by the arrow p_LS in Fig. 6 is shown, either from a combination of the LS pressure reported by the LS line LS3 with the first pressure signal (if the control device 430 is open-controlled) or solely from the LS pressure reported by the LS line LS3 (if the control device 430 is controlled) are applied to the 2-way flow control valve 420 in the open control direction.
  • a further control line (second control line) 452 can be branched off downstream of the 2-way flow control valve 420 at a branch point 450, by means of which a further (second) pressure signal in the closed control direction to the 2-way flow control valve 420 against the action of a biasing element 422 and the LS pressure signal, possibly combined with the first pressure signal.
  • the effect of the second pressure signal is at least partially compensated for by the first pressure signal when the control device 430 is open, so that the 2-way flow control valve 420 is opened.
  • Fig. 7 shows characteristic curves of the volume flow through the above-described proportional directional spool valve as a function of the pressure difference ⁇ p above the 2-way flow control valve and the proportional directional spool valve described above.
  • a characteristic curve with a dotted curve shows the case of a high control pressure
  • a characteristic curve with a dash-dotted curve shows the case of a low control pressure in relation to the in Fig. 3 shown characteristic curve (solid curve) means.
  • a characteristic curve or the regulating pressure is set via the adjustable preloading elements, a "harder" preloading element or a preloading element with "greater” preload meaning a "higher regulating pressure.
  • the result is a length of a standard edge, as in Fig. 7 on the basis of the double arrow labeled “ ⁇ x”, by means of which the adjustable prestressing element can be set depending on the application.
  • the structure and function of a hydraulic module with a 2-way flow control valve were described above, which according to some illustrative embodiments in proportional directional spool valves can be used with LS technology.
  • the 2-way flow control valve can be connected upstream or downstream of the individual proportional directional spools or valves.
  • a pressure drop across the proportional directional spool valve, in particular via a measuring orifice in the proportional directional spool is kept constant, and the volume flow through the proportional directional spool can also be kept constant regardless of the pump pressure or a load pressure at the consumer.
  • the 2-way flow control valve In the case of 2-way flow control valves upstream of proportional directional spool valves, the 2-way flow control valve always regulates the pressure that is present directly in front of the proportional directional spool valve (and thus in front of the measuring orifice in the proportional directional spool valve) by the same pressure difference as the consumer pressure.
  • the control device which according to illustrative embodiments based on the 2 to 7
  • the advantages described above have the following advantages: Fig. 1b Section "a2" of the characteristic curve described is bypassed.
  • the two-way flow control valve is open-controlled in this area regardless of the load pressure. By suspending the control of the 2-way flow control valve in this area, energy savings are achieved. Furthermore, independence from special settings on pump controllers or on controllers in the connection block to the hydraulic module is achieved.
  • the control device described above ensures that the 2-way flow control valve is opened up to a certain set pressure difference and that there is no counteracting control on the 2-way flow control valve.
  • the behavior of the 2-way flow control valve is influenced by the biasing element up to a certain adjustable pressure difference.
  • the 2-way flow control valve is completely open-controlled in this pressure range. Only from a certain pressure difference and / or a sufficiently high pressure difference is there a regulating operation of the 2-way flow control valve by at least partially compensating for the opening effect of the prestressing element.
  • the pressure difference from which the 2-way flow control valve switches to regulating operation can be set via the control device.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (14)

  1. Module hydraulique (200; 400) comprenant une valve (220; 420) à 2 voies commandée par pression qui est disposée dans un conduit d'alimentation (205; 405) dudit module hydraulique (200; 400), ladite valve (220; 420) à 2 voies commandée par pression étant sollicitée par un premier élément de sollicitation (222; 422) dans la direction d'ouverture, un premier signal de pression, dont la prise est située en aval ou en amont de la valve (220; 420) à 2 voies commandée par pression dans le conduit d'alimentation (205; 405), est apte à être appliqué dans la direction de fermeture ou la direction d'ouverture, respectivement, à la valve (220; 430) à 2 voies commandée par pression via un premier conduit de pilotage (223; 423), dans le premier conduit de pilotage (223; 423) étant disposé un organe de régulation (230; 430) pour commander par pression la valve (220; 420) à 2 voies commandée par pression, ledit organe de régulation (230; 430) étant configuré pour bloquer, dans un premier état de régulation (232; 432), une application du premier signal de pression à la valve (220; 420) à 2 voies commandée par pression, tandis que dans un deuxième état de régulation (234; 434) le premier signal de pression est apte à être appliqué par ledit organe de régulation (230; 430) à la valve (220; 420) à 2 voies commandée par pression,
    caractérisé en ce que la valve à 2 voies commandée par pression est réalisée en forme d'une valve de régulation de débit à 2 voies commandée par pression.
  2. Module hydraulique (400) selon la revendication 1, dans lequel la prise du premier conduit de pilotage (423) est située en amont de la valve (420) de régulation de débit à 2 voies commandée par pression dans le conduit d'alimentation (405), ledit module hydraulique (400) comprenant en outre un premier conduit de signalisation (424) dont le branchement est situé en amont dudit organe de régulation (430) dans le premier conduit de pilotage (423), ledit organe de régulation étant apte à être commuté sur le premier ou le deuxième état de régulation en fonction d'un signal de pression prise par le premier conduit de signalisation (424).
  3. Module hydraulique (200) selon la revendication 1, dans lequel la prise du premier conduit de pilotage (223) est située en aval de la valve (220) de régulation de débit à 2 voies commandée par pression dans le conduit d'alimentation (205), ledit module hydraulique (200) comprenant en outre un deuxième conduit de signalisation (211) qui est raccordé audit conduit d'alimentation (205) en amont de la valve (220) de régulation de débit à 2 voies commandée par pression, ledit organe de régulation (230) étant apte à être commuté sur le deuxième état de régulation (234) en fonction d'un deuxième signal de pression prise par le deuxième conduit de signalisation (211).
  4. Module hydraulique (200; 400) selon l'une quelconque des revendications 1 à 3, dans lequel ledit organe de régulation (230; 430) comprend une valve à 2 voies commandée par pression qui est sollicitée par un deuxième élément de sollicitation (235; 435), ladite valve (230; 430) à 2 voies commandée par pression étant dans la position de fermeture lors d'un premier état de régulation (232; 432) et étant dans la position d'ouverture lors d'un deuxième état de régulation (234; 434) de sorte que le premier signal de pression est apte, avec la valve (230; 430) à 2 voies commandée par pression étant dans la position d'ouverture, à être appliqué à la valve (220; 420) de régulation de débit à 2 voies commandée par pression.
  5. Module hydraulique (200) selon la revendication 4 en combinaison avec la revendication 3, dans lequel le deuxième signal de pression est apte à être appliqué à la valve (230) à 2 voies commandée par pression dans la direction d'ouverture par ledit deuxième conduit de pilotage (211).
  6. Module hydraulique (200; 400) selon l'une quelconque des revendications 1 à 5, comprenant en outre un troisième conduit de pilotage (LS2; LS3) qui est raccordé audit conduit d'alimentation (205; 405) en aval de la valve (220; 420) de régulation de débit à 2 voies commandée par pression, un troisième signal de pression étant apte à être appliqué de la valve (220; 420) de régulation de débit à 2 voies commandée par pression dans la direction d'ouverture par ledit troisième conduit de pilotage (LS2; LS3).
  7. Module hydraulique (200) selon la revendication 6 en combinaison avec la revendication 2, comprenant en outre un quatrième conduit de pilotage (228) qui est raccordé audit troisième conduit de pilotage (LS2), ledit troisième signal de pression étant apte à être appliqué audit organe de régulation (230) par ledit quatrième conduit de pilotage (228) et ledit organe de régulation étant apte à être commuté sur le premier état de régulation (232) en fonction dudit ledit troisième signal de pression.
  8. Module hydraulique (200) selon la revendication 6 ou 7 en combinaison avec la revendication 2, dans lequel le troisième signal de pression est apte à être appliqué à la valve (220) de régulation de débit à 2 voies commandée par pression dans la direction de fermeture lors d'un premier état de régulation (232) dudit organe de régulation (230).
  9. Module hydraulique (100) selon l'une quelconque des revendications 1 à 8, comprenant en outre un distributeur à tiroir à commande proportionnelle (110) qui est disposé dans le conduit d'alimentation (105) en aval de la valve (120) de régulation de débit à 2 voies commandée par pression.
  10. Module hydraulique (100) selon la revendication 9 en combinaison avec une quelconque des revendications 6 à 8, dans lequel la prise du premier signal de pression est située en amont du distributeur à tiroir à commande proportionnelle (110) et la prise du troisième signal de pression est située en aval du distributeur à tiroir à commande proportionnelle (110).
  11. Module hydraulique (200) selon l'une quelconque des revendications 1 à 10, dans lequel ladite valve (220) de régulation de débit à 2 voies commandée par pression et ledit organe de régulation (230) sont intégrés dans un bloc de valves.
  12. Module hydraulique (200) selon l'une quelconque des revendications 1 à 11, dans lequel ledit organe de régulation (230) comprend seulement le premier et le deuxième état de régulation (232, 234) dans la forme de deux positions de commutation discrètes.
  13. Module hydraulique (200) selon l'une quelconque des revendications 1 à 12, dans lequel ledit organe de régulation (230) comprend un élément de sollicitation ajustable (235) par lequel ledit organe de régulation (230) est sollicité vers le premier état de régulation (232).
  14. Système de modules hydrauliques, comprenant au moins deux modules hydrauliques, seulement un desdits au moins deux modules hydrauliques étant réalisé selon le module hydraulique (200) de l'une quelconque des revendications 1 à 13.
EP16174633.4A 2016-06-15 2016-06-15 Module hydraulique avec soupape de régulation 2-voies contrôlé par pression Active EP3258116B1 (fr)

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CN113152575B (zh) * 2021-05-19 2022-11-25 徐州徐工挖掘机械有限公司 一种基于液压桥路的集合先导正流量控制系统

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SE500119C2 (sv) * 1993-01-14 1994-04-18 Voac Hydraulics Boraas Ab Förfarande för styrning av en hydraulmotor, jämte hydraulventil härför
DE4311191C2 (de) * 1993-04-05 1995-02-02 Deere & Co Hydrauliksystem zur Versorgung offener oder geschlossener Hydraulikfunktionen
SE510508C2 (sv) * 1993-06-11 1999-05-31 Voac Hydraulics Boraas Ab Anordning för styrning av en hydraulisk motor
DE202005001417U1 (de) * 2005-01-28 2006-06-08 Hawe Hydraulik Gmbh & Co. Kg Hydraulische Steuervorrichtung
DE502005000989D1 (de) * 2005-08-11 2007-08-16 Hawe Hydraulik Gmbh & Co Kg Elektrohydraulische Vorrichtung

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