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EP2280179B1 - Directional valve assembly - Google Patents

Directional valve assembly Download PDF

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Publication number
EP2280179B1
EP2280179B1 EP10006382.5A EP10006382A EP2280179B1 EP 2280179 B1 EP2280179 B1 EP 2280179B1 EP 10006382 A EP10006382 A EP 10006382A EP 2280179 B1 EP2280179 B1 EP 2280179B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
duct
working
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10006382.5A
Other languages
German (de)
French (fr)
Other versions
EP2280179A3 (en
EP2280179A2 (en
Inventor
Reiner Kunz
Andreas Albrecht
Markus Grammer
Steffen Knapper
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2280179A2 publication Critical patent/EP2280179A2/en
Publication of EP2280179A3 publication Critical patent/EP2280179A3/en
Application granted granted Critical
Publication of EP2280179B1 publication Critical patent/EP2280179B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7761—Electrically actuated valve
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated

Definitions

  • the invention relates to a directional control valve arrangement according to the preamble of patent claim 1.
  • the check valve has the task of minimizing a consumer-side load reduction due to leakage via the directional control valve.
  • a connected to the consumer channel line system may occur by the sealing check valve in foreign heating, such as sunlight or engine waste heat, an unacceptably high pressure in the pipe system and the consumer channel.
  • the impermissibly high pressure can lead to damage of the directional control valve arrangement, the line system and valves arranged thereon. To reduce and thus to avoid the unacceptably high pressure is used in the consumer channel pressure relief valve.
  • the check valve and its pilot control are opened by a plunger. This is mechanically actuated via a formed on a valve spool of the directional control valve in the up direction.
  • the consumer channel with an intermediate chamber can be connected, via the valve spool of the directional control valve, a pressure medium connection between the intermediate chamber and a tank chamber is controllable.
  • the intermediate chamber is connected via a throttled channel to the tank chamber, wherein this the gap between the valve spool and a valve spool receiving the valve housing.
  • the pressure relief valve opens, whereby pressure medium flows from the consumer channel to the intermediate chamber and from there via the throttled channel to the tank chamber.
  • the applicant's data sheet RD 66 132-01-R1 / 03.07 shows a further solution for reducing an inadmissibly high pressure in a consumer line in the case of a directional control valve arrangement.
  • a check valve is arranged in the consumer channel as in the previous document.
  • a thermo-pressure limiting valve is provided in a separate bore of a valve disc of the directional control valve arrangement. With this, a pressure medium connection between the consumer channel and a tank channel is opened at a certain impermissibly high pressure.
  • a disadvantage of the above-mentioned directional control valve arrangements is that the pressure relief valves are cost-intensive and device-technically complex components, require an adjustment of the impermissibly high pressure to be limited and have a high space requirement.
  • the invention is based on the object to provide a directional control valve arrangement, with which to create a cost-effective and space-saving pressure limitation of the clamped between a consumer and the directional control valve pressure medium.
  • a directional control valve arrangement has a directional control valve having a valve slide. About this a pressure medium connection between a pressure channel, a flow channel and a working channel can be controlled.
  • a pilot-operated, unlockable check valve is provided, which has a check valve body and a pilot body, which are mechanically alsêtbar by a displacement of the valve spool, the Auf facedung already takes place when the working channel is shut off via a control edge of the valve spool to the drainage channel.
  • the valve spool of the directional control valve is displaceable in a position in which is closed at at least over the control edge to the process shut-off working channel of the pilot body of the check valve.
  • the working channel is relieved of pressure, wherein in the pressure fluid flow path between the check valve and the control edge of the valve spool, a gap for receiving a compression volume of the working channel is provided.
  • the control of the check valve and its feedforward can be done device technology easy with an actuatable via a gate on the valve spool in the up direction ram.
  • the space for receiving the compression volume of the working channel can be space-saving partially limited by a control edge forming the control collar of the valve spool.
  • To reduce the pressure of the gap may advantageously be provided a gap leakage between the intermediate space and the flow channel over the valve spool.
  • a displacement sensor on the valve spool of the directional control valve is provided, whereby an accurate control of the control of the check valve via the valve spool and the plunger is possible.
  • an electronic arrangement for controlling the directional control valve is arranged on this.
  • a directional control valve arrangement 1 of a LS-way valve block is shown in a longitudinal sectional view according to an embodiment. This is accommodated in a housing 2 constructed in disk construction and has a pressure port P connected to a pressure port, a tank port T connected to a tank port, and two working ports A, B.
  • the directional control valve arrangement 1 further comprises an individual pressure compensator 4, controlled via a pilot valve 6 Directional valve 8 and a in the in Fig. 1 left working port A arranged check valve 10.
  • the basic structure of the directional control valve arrangement 1 is known and corresponds essentially to the valve SB 23 LS of the Applicant, which is why only the details necessary for understanding are described.
  • the pressure channel P of the directional control valve assembly 1 is connected to an input port P 'of the individual pressure compensator 4 whose output port A' is in fluid communication with an input port P "of the continuously variable directional control valve 8.
  • the directional control valve 8 has two working ports in addition to the input port P" A “and B", which are each connected via a working channel 14 and 16 to the working port A and B of the directional control valve assembly 1.
  • a tank connection T 'of the directional control valve 1 is connected via an outlet channel 18 to the tank channel T of the directional control valve arrangement 1 in pressure medium connection.
  • a valve spool 22 of the directional control valve 8 is guided in an axially displaceable manner in a valve bore 24 introduced in the housing 2.
  • a valve bore 24 introduced in the housing 2.
  • six axially spaced control chambers 26, 28, 30, 32, 34 and 36 are formed.
  • the control chamber 26 is connected to the input port P ", and the pressure medium connection between the control chamber 26 and the adjacent control chamber 28 is controllable via a metering orifice 37 of the valve spool 22.
  • the latter is connected via an intermediate channel 38 to the one shown in FIG FIG. 1 left control chamber 36 connected.
  • the working ports A “and B" of the directional control valve 8 are respectively connected to the control chamber 34 and 30 in fluid communication. Via a control edge 40 of a first control collar of the valve slide 22, the control chamber 28 with the control chamber 30 and the working port B "and via a control edge 42 of a second control collar, the control chamber 36 with the control chamber 34 and the working port A" connectable.
  • a pressure gradient and thus a volume flow at the metering orifice 37 is kept constant independent of the load.
  • the pressure compensator piston 44 is acted upon in the opening direction by a spring force of a pressure compensator spring 46 as well as via a downstream of the metering orifice 37 of the valve spool 22 of the directional control valve 8 tapped pressure, the pressure over a branched off from the intermediate channel 38 channel 47 is tapped.
  • the closing direction of the pressure compensator piston 44 is acted upon by the pressure upstream of the metering orifice 37, which is tapped via a control channel 48 from the output port A 'of the individual pressure compensator 4.
  • An Indian FIG. 1 not shown valve spool of the pilot valve 6 can be actuated via a proportional actuating magnet 50.
  • the pilot valve 6 is connected to a first and second control line 52, 54, wherein the first control line 52 with a in the Fig. 1 left control chamber 56 of the directional control valve 8 and the second control line 54 is connected to a right control chamber 58.
  • a pressure medium connection between the control line 52 and 54 and a pilot line 60 is controllable, wherein in each case one of the control lines 52, 54 with the pilot line 60 and the other with a tank line 62 or both control lines 52, 54 for pressure relief of the control chambers 56th , 58 are connected to the tank line 62.
  • the pressure of the pilot line 60 is reduced to a desired control pressure for actuating the valve spool 22 of the directional control valve 8.
  • the tank line 62 of the pilot valve 60 is further connected to a drain line 63, which is connected via an annular gap 61 between the valve spool 22 and the valve bore 24 of the directional control valve 8 to the control chamber 36.
  • the valve spool 22 of the directional control valve 8 is connected via a arranged in the control chamber 58 Zentrierfederan Aunt 64 in his in the Fig. 1 shown biased position in which the pressure medium connection of the input port P "to the control chamber 28 and the pressure medium connection between the control chambers 28, 36 and the working ports A", B "is controlled.
  • valve spool 22 of the directional control valve 8 in the Fig. 1 To move the valve spool 22 of the directional control valve 8 in the Fig. 1 to the right and thus to produce a pressure medium connection between the input port P "and the working port B", the valve spool 22 is on the left Control chamber 56 can be acted upon by the control pressure, wherein the control chamber 56 is connected via the first control line 52 and the pilot valve 6 with the pilot line 60 and the control chamber 58 is relieved via the control line 54 and the pilot valve 6 to the tank line 62. In this direction of displacement, the pressure medium connection of the working port A "via the control chamber 34 to the control chamber 32 and thus to the outlet channel 18 is opened via a control edge 65 of a control collar 66 of the valve slide 22.
  • FIG. 2 shows an enlarged section of the directional control valve assembly 1 FIG. 1 in the region of the shut-off valve 10. This is arranged in the working channel 14 to minimize a load-side load reduction due to leakage via the directional control valve 8.
  • the check valve 10 has a guided in a check valve bore 67 check valve body 68. This is in the off state with a conical seat 70 on a check valve seat 72. Via a valve spring 73, the check valve body 68 is biased onto the check valve seat 72, wherein the spring is supported on an inserted holding plate 74. This sits in the bottom region of the working port A. For the outside flow around the holding plate 74 at least two uniform recesses 76 are provided in a bore of the working port A in the area.
  • a pilot control 84 is formed for the check valve 10.
  • a ball-shaped pilot body 86 is disposed in a two-stage pilot port 88 of the check valve 10, which is biased by a spring, not shown, on a trained as a seat stage 89 of the pilot port 88 and a pilot port 90 closes.
  • a downwardly open transverse channel 91 is milled, which intersects the pilot control bore 90.
  • the check valve body 68 and the pilot body 86 can be opened via a plunger 92. This is guided approximately perpendicular to an axis of the valve spool 22 of the directional control valve 8 in the housing 2 and via a valve spool 22 between the second in the FIG. 2 left control edge 42 and the adjacent control collar 66 formed backdrop 94 in the direction of the check valve 10 slidably.
  • the link 94 has an approximately frusto-conical circumference, the diameter of which decreases in the direction of the control collar 66.
  • the plunger 92 has a radially rearwardly directed end portion 96, facing away from the valve spool 22, which is immersed in the auxiliary bore 90 of the check valve body 68 for actuation thereof.
  • the gap 100 is provided axially between the control edge 65 of the control collar 66 and the control edge 42 and is partially bounded by the valve bore 24 and the valve spool 22.
  • the diameter of the valve spool 22, between the control edge 65 and the gate 94, corresponds approximately to the minimum diameter of the gate 94th
  • the opening of the pilot control 84 is a discharge of a compression volume or a discharge volume and thus a reduction of an excessively high pressure in the working channel 14, the control chamber 34 and the gap 100 allows. Is by displacement of the valve spool 22 in the FIG. 2 to the left the pilot control 84 again closed, then the pressure in the working channel 14, the control chamber 34 and the gap 100 on the one hand via a gap leakage between the control collar 66 and the valve bore 24 to the drain channel 18 and the other via a gap leakage between the control edge 42nd associated control collar and the valve bore 24 to the intermediate channel 38, and reduced from there to the tank line 62.
  • the opening of the pilot control 84 of the check valve 10 at a controlled via the control edge 65 of the control collar 66 of the valve spool 22 fluid connection to the drain passage 18 for reducing a pressure is referred to as discharge cycle.
  • valve spool 22 in the FIG. 2 shifted to the right, wherein, as described above, the plunger 92 is moved via the guide 94 in the direction of the check valve 10.
  • pilot body 86 is opened, a pressure difference between the pressure in the working channel 14, the control chamber 34 and the gap 100 and the pressure in the working port A is reduced.
  • the displacement of the valve spool 22 of the directional control valve 8 is via a connected to this transducer 102, see FIG. 1 , detected. This is approximately coaxial with the valve spool 22 left in the FIG. 1 connected to the housing 2. Furthermore, a valve electronics 104 with a temperature sensor on the housing 2 is arranged. By Wegaufillon 102 and the valve electronics 104, the displacement and the displacement time of the valve spool 22 is precisely controlled, whereby the timing and the duration of the discharge cycles are arbitrarily adjustable.
  • a timing of the discharge of the working port A via the check valve 10 with a discharge cycle takes place, for example, as a function of a measured temperature increase in the connected to the working port A wiring harness.
  • approximately 0.16 ml of compression volume can be released at a 250 bar load pressure.
  • the length of the opening time of the pilot control 84 of the check valve 10 in the FIG. 2 in a discharge cycle is quite uncritical because no load pressure to the tank port T is reduced.
  • the relief device requires no additional space.
  • the control of the unloading cycles can take place, for example, via vehicle electronics or via the valve electronics 104.
  • FIG. 3 shows a diagram in which the compression volume and the discharge volume in cm 3 and% on the load pressure in bar in the working port A from FIG. 2 is applied.
  • An upper graph 108 in FIG. 3 shows the compression volume in cm 3 as a function of the load pressure.
  • the compression volume also increases approximately linearly. For example, at a load pressure of 350 bar, the compression volume which can be broken down via the discharge cycle is about 0.22 cm 3 .
  • a lower graph 110 in FIG. 3 which shows the compression volume in% as a function of the load pressure, is flatter than the graph 108. Due to the linear relationship between the compression volume and the load pressure, the degradation of the Compression volume over the discharge cycles at different load pressures easily and accurately controllable.
  • FIG. 4 is another diagram disclosed, wherein the load pressure in bar on the abscissa and a pressure relief is also shown in bar on the ordinate.
  • Four graphs 112, 114, 116 and 118 are shown which show the pressure relief as a function of the load pressure at respectively different tube lengths of 50, 100, 200 and 400 cm at exemplary diameters from one to the working port A in FIG. 2 connect connected pipe.
  • the pressure relief is a measure of the reduced in a discharge cycle pressure in the working port A and the connected pipe.
  • the graphs 112 to 118 increase approximately linearly with the load pressure, with a larger pipe length the slope of the respective graph 112 to 118 becomes flatter.
  • the pressure relief or the reduced pressure of a discharge cycle at a load pressure of 350 bar is about 60 bar, which is at the top graph 112 in FIG. 4 is readable.
  • the pressure relief is about 10 bar with the same load pressure, which shows the graph 118.
  • FIG. 5 represents a diagram with a load pressure and temperature curve as a function of time.
  • the abscissa forms the time in min, the left ordinate in FIG. 5 the load pressure in bar and the right ordinate a rise in temperature in one at the work connection A from FIG. 2 connected pipe with 200 cm length.
  • the increase in temperature for example due to solar radiation, should be about 4 ° C per minute, which corresponds to the approximately linear graph 120 in FIG. 5 is shown.
  • At an output load pressure of 100 bar approximately four discharge cycles are provided per minute.
  • a graph 122 that maps the load pressure as a function of time approaches asymptotically to a pressure of 210 bar. Thus, it is shown that the load pressure no longer rises despite the increase in temperature auground the discharge cycles and thus an excessive pressure in a connected to the working port A pipe is avoided.
  • a directional control valve arrangement having a valve slide having a directional control valve.
  • a pressure medium connection between a pressure connection, a tank connection and at least one working port controllable.
  • a check valve is arranged in a working channel connected to the working port.
  • the pressure in the working channel is degradable with a discharge unit, wherein the pressure medium connection between the working channel and the tank connection is blocked by the valve spool.
  • the relief unit has a gap which is formed in the pressure medium flow path between the check valve and the working channel to the tank connection shut-off control edge of the valve spool and is provided for receiving a compression volume of the working channel.
  • the gap is connectable by opening the check valve with the working channel, via the control edge of the valve spool, the connection to the tank port is blocked.

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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)
  • Multiple-Way Valves (AREA)
  • Valve Housings (AREA)

Description

Die Erfindung betrifft eine Wegeventilanordnung gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a directional control valve arrangement according to the preamble of patent claim 1.

In den Druckschriften FR 2 484 029 und DE 196 27 306 A1 sind derartigen Wegeventilanordnungen offenbart.In the pamphlets FR 2 484 029 and DE 196 27 306 A1 such directional valve arrangements are disclosed.

Diese weist ein handbetätigtes Wegeventil mit in einem Verbraucherkanal angeordneten Sperr- und Druckbegrenzungsventil auf. Das Sperrventil hat die Aufgabe, eine verbraucherseitige Lastabsenkung aufgrund von Leckage über das Wegeventil zu minimieren. Bei einem an dem Verbraucherkanal angeschlossenen Leitungssystem, kann durch das dichtende Sperrventil bei Fremderwärmung, wie beispielsweise Sonnenbestrahlung oder Maschinenabwärme, ein unzulässig hoher Druck im Leitungssystem und im Verbraucherkanal auftreten. Der unzulässig hohe Druck kann zu Beschädigungen der Wegeventilanordnung, des Leitungssystems und daran angeordneten Ventilen führen. Zur Abbau und somit zur Vermeidung von dem unzulässig hohen Druck dient das im Verbraucherkanal angeordnete Druckbegrenzungsventil.This has a manually operated directional control valve arranged in a consumer channel barrier and pressure relief valve. The check valve has the task of minimizing a consumer-side load reduction due to leakage via the directional control valve. In a connected to the consumer channel line system may occur by the sealing check valve in foreign heating, such as sunlight or engine waste heat, an unacceptably high pressure in the pipe system and the consumer channel. The impermissibly high pressure can lead to damage of the directional control valve arrangement, the line system and valves arranged thereon. To reduce and thus to avoid the unacceptably high pressure is used in the consumer channel pressure relief valve.

Das Sperrventil und dessen Vorsteuerung werden durch einen Stößel aufgesteuert. Dieser ist mechanisch über eine an einem Ventilschieber des Wegeventils ausgebildeten Kulisse in Aufsteuerrichtung betätigbar. Über das Sperrventil und das Druckbegrenzungsventil ist der Verbraucherkanal mit einer Zwischenkammer verbindbar, wobei über den Ventilschieber des Wegeventils eine Druckmittelverbindung zwischen der Zwischenkammer und einer Tankkammer steuerbar ist. Zusätzlich ist die Zwischenkammer über einen gedrosselten Kanal mit der Tankkammer verbunden, wobei dieser der Spalt zwischen dem Ventilschieber und einem dem Ventilschieber aufnehmenden Ventilgehäuse.The check valve and its pilot control are opened by a plunger. This is mechanically actuated via a formed on a valve spool of the directional control valve in the up direction. About the check valve and the pressure relief valve, the consumer channel with an intermediate chamber can be connected, via the valve spool of the directional control valve, a pressure medium connection between the intermediate chamber and a tank chamber is controllable. In addition, the intermediate chamber is connected via a throttled channel to the tank chamber, wherein this the gap between the valve spool and a valve spool receiving the valve housing.

Bei einem unzulässig hohen Druck öffnet das Druckbegrenzungsventil, womit Druckmittel vom Verbraucherkanal zur Zwischenkammer und von dieser über den gedrosselten Kanal zur Tankkammer strömt.At an impermissibly high pressure, the pressure relief valve opens, whereby pressure medium flows from the consumer channel to the intermediate chamber and from there via the throttled channel to the tank chamber.

In dem Datenblatt RD 66 132-01-R1/03.07 der Anmelderin ist eine weitere Lösung zum Abbau eines unzulässig hohen Drucks in einer Verbraucherleitung bei einer Wegeventilanordnung gezeigt. In dieser ist wie bei der vorhergehenden Druckschrift im Verbraucherkanal ein Sperrventil angeordnet. Zur Begrenzung des unzulässig hohen Drucks ist ein Thermo- Druckbegrenzungsventil in einer eigenen Bohrung einer Ventilscheibe der Wegeventilanordnung vorgesehen. Mit diesem wird ab einem bestimmten unzulässig hohen Druck eine Druckmittelverbindung zwischen dem Verbraucherkanal und einem Tankkanal aufgesteuert.The applicant's data sheet RD 66 132-01-R1 / 03.07 shows a further solution for reducing an inadmissibly high pressure in a consumer line in the case of a directional control valve arrangement. In this, a check valve is arranged in the consumer channel as in the previous document. To limit the impermissibly high pressure, a thermo-pressure limiting valve is provided in a separate bore of a valve disc of the directional control valve arrangement. With this, a pressure medium connection between the consumer channel and a tank channel is opened at a certain impermissibly high pressure.

Nachteilig bei den oben genannten Wegeventilanordnungen ist, dass die Druckbegrenzungsventile kostenintensive und vorrichtungstechnisch aufwändig aufgebaute Bauteile sind, einer Einstellung des zu begrenzenden unzulässig hohen Drucks bedürfen und einen hohen Bauraumbedarf aufweisen.A disadvantage of the above-mentioned directional control valve arrangements is that the pressure relief valves are cost-intensive and device-technically complex components, require an adjustment of the impermissibly high pressure to be limited and have a high space requirement.

Demgegenüber liegt der Erfindung die Aufgabe zu Grunde eine Wegeventilanordnung zu schaffen, mit der eine kostengünstige und platzsparende Druckbegrenzung des zwischen einem Verbraucher und der Wegeventilanordnung eingespannten Druckmittels zu schaffen.In contrast, the invention is based on the object to provide a directional control valve arrangement, with which to create a cost-effective and space-saving pressure limitation of the clamped between a consumer and the directional control valve pressure medium.

Diese Aufgabe wird gelöst durch eine Wegeventilanordnung mit den Merkmalen des Patentanspruch 1.This object is achieved by a directional control valve arrangement having the features of patent claim 1.

Erfindungsgemäß hat eine Wegeventilanordnung ein einen Ventilschieber aufweisendes Wegeventil. Über diesen ist eine Druckmittelverbindung zwischen einem Druckkanal, einem Ablaufkanal und einem Arbeitskanal steuerbar. In dem Arbeitskanal ist ein vorgesteuertes, entsperrbares Sperrventil vorgesehen, das einen Sperrventilkörper und einen Vorsteuerkörper aufweist, die durch eine Verschiebung des Ventilschiebers mechanisch aufsteuerbar sind, wobei die Aufsteuerung schon erfolgt, wenn der Arbeitskanal über eine Steuerkante des Ventilschiebers noch zum Ablaufkanal abgesperrt ist. Es ist eine Elektronikanordnung vorhanden, von der der Ventilschieber des Wegeventils in eine Position verschiebbar ist, in der bei über die Steuerkante noch zum Ablauf abgesperrtem Arbeitskanal zumindest der Vorsteuerkörper des Sperrventils aufgesteuert ist. Dadurch ist der Arbeitskanal von Druck entlastbar, wobei im Druckmittelströmungspfad zwischen dem Sperrventil und der Steuerkante des Ventilschiebers ein Zwischenraum zum Aufnehmen eines Kompressionsvolumens des Arbeitskanals vorgesehen ist.According to the invention, a directional control valve arrangement has a directional control valve having a valve slide. About this a pressure medium connection between a pressure channel, a flow channel and a working channel can be controlled. In the working channel a pilot-operated, unlockable check valve is provided, which has a check valve body and a pilot body, which are mechanically aufsteuerbar by a displacement of the valve spool, the Aufsteuerung already takes place when the working channel is shut off via a control edge of the valve spool to the drainage channel. There is an electronic assembly available, of which the valve spool of the directional control valve is displaceable in a position in which is closed at at least over the control edge to the process shut-off working channel of the pilot body of the check valve. As a result, the working channel is relieved of pressure, wherein in the pressure fluid flow path between the check valve and the control edge of the valve spool, a gap for receiving a compression volume of the working channel is provided.

Diese Lösung hat den Vorteil, dass eine Druckentlastung des Arbeitskanals mit einem geringen vorrichtungstechnischen Aufwand umgesetzt und bauraumsparend in die Wegeventilanordnung integriert ist. Ein Druckbegrenzungsventil wie im eingangs erläuterten Stand der Technik ist nicht mehr notwendig.This solution has the advantage that a pressure relief of the working channel implemented with a low device complexity and space-saving integrated into the directional control valve assembly. A pressure relief valve as described in the prior art is no longer necessary.

Die Aufsteuerung des Sperrventils und dessen Vorsteuerung kann vorrichtungstechnisch einfach mit einem über eine Kulisse am Ventilschieber in Aufsteuerrichtung betätigbaren Stößel erfolgen.The control of the check valve and its feedforward can be done device technology easy with an actuatable via a gate on the valve spool in the up direction ram.

Der Zwischenraum zum Aufnehmen des Kompressionsvolumens des Arbeitskanals kann bauraumsparend abschnittsweise durch einen die Steuerkante ausbildenden Steuerbund des Ventilschiebers begrenzt sein.The space for receiving the compression volume of the working channel can be space-saving partially limited by a control edge forming the control collar of the valve spool.

Zum Druckabbau des Zwischenraums kann vorteilhafterweise eine Spaltleckage zwischen dem Zwischenraum und dem Ablaufkanal über dem Ventilschieber vorgesehen sein.To reduce the pressure of the gap may advantageously be provided a gap leakage between the intermediate space and the flow channel over the valve spool.

Vorzugsweise erfolgt eine Taktung einer Entlastung des Arbeitskanals zum Aufnehmen des Kompressionsvolumens im Zwischenraum, in Abhängigkeit von einer gemessenen Temperaturerhöhung, insbesondere im Arbeitskanal.Preferably, a clocking of a discharge of the working channel for receiving the compression volume in the intermediate space, in response to a measured temperature increase, in particular in the working channel.

Bevorzugterweise ist ein Wegsensor am Ventilschieber des Wegeventils vorgesehen, wodurch eine genaue Steuerung der Aufsteuerung des Sperrventils über den Ventilschieber und den Stößel möglich ist.Preferably, a displacement sensor on the valve spool of the directional control valve is provided, whereby an accurate control of the control of the check valve via the valve spool and the plunger is possible.

Mit Vorteil ist eine Elektronikanordnung zur Ansteuerung des Wegeventils an diesem angeordnet.Advantageously, an electronic arrangement for controlling the directional control valve is arranged on this.

Sonstige vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous embodiments of the invention are the subject of further subclaims.

Im Folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Figur 1 einen Längsschnitt einer Wegeventilanordnung gemäß einem Ausführungsbeispiel;
  • Figur 2 ein Sperrventil der Wegeventilanordnung in einer vergrößerten Darstellung;
  • Figur 3 ein Diagramm, bei dem das Kompressionsvolumen als Funktion eines Lastdruck gezeigt ist;
  • Figur 4 ein Diagramm, bei dem ein Druckabbau als Funktion des Lastdrucks gezeigt ist; und
  • Figur 5 ein Diagramm, bei dem der Lastdruck und einem Temperaturanstieg als Funktion einer Zeit gezeigt sind.
In the following, a preferred embodiment of the invention is explained in more detail with reference to schematic drawings. Show it:
  • FIG. 1 a longitudinal section of a directional control valve arrangement according to an embodiment;
  • FIG. 2 a check valve of the directional control valve assembly in an enlarged view;
  • FIG. 3 a diagram in which the compression volume is shown as a function of a load pressure;
  • FIG. 4 a diagram in which a pressure reduction is shown as a function of the load pressure; and
  • FIG. 5 a diagram in which the load pressure and a temperature rise as a function of time are shown.

In der Fig. 1 ist eine Wegeventilanordnung 1 eines LS-Wegeventilblocks in einer Längsschnittansicht gemäß einem Ausführungsbeispiel gezeigt. Diese ist in einem in Scheibenbauweise ausgeführten Gehäuse 2 aufgenommen und hat einen mit einem Druckanschluss verbundenen Druckkanal P, einen mit einem Tankanschluss verbundenen Tankkanal T sowie zwei Arbeitsanschlüsse A, B. Die Wegeventilanordnung 1 weist des Weiteren eine Individualdruckwaage 4, ein über ein Pilotventil 6 gesteuertes Wegeventil 8 und ein in dem in Fig. 1 linken Arbeitsanschluss A angeordnetes Sperrventil 10 auf. Der Grundaufbau der Wegeventilanordnung 1 ist bekannt und entspricht im Wesentlichen dem Ventil SB 23 LS der Anmelderin, weswegen nur die zum Verständnis notwendigen Einzelheiten beschrieben sind.In the Fig. 1 a directional control valve arrangement 1 of a LS-way valve block is shown in a longitudinal sectional view according to an embodiment. This is accommodated in a housing 2 constructed in disk construction and has a pressure port P connected to a pressure port, a tank port T connected to a tank port, and two working ports A, B. The directional control valve arrangement 1 further comprises an individual pressure compensator 4, controlled via a pilot valve 6 Directional valve 8 and a in the in Fig. 1 left working port A arranged check valve 10. The basic structure of the directional control valve arrangement 1 is known and corresponds essentially to the valve SB 23 LS of the Applicant, which is why only the details necessary for understanding are described.

Der Druckkanal P der Wegeventilanordnung 1 ist mit einem Eingangsanschluss P' der Individualdruckwaage 4 verbunden, deren Ausgangsanschluss A' über einen Zulaufkanal 12 mit einem Eingangsanschluss P" des stetig verstellbaren Wegeventils 8 in Druckmittelverbindung steht. Das Wegeventil 8 hat neben dem Eingangsanschluss P" zwei Arbeitsanschlüsse A" und B", die jeweils über einen Arbeitskanal 14 bzw. 16 mit dem Arbeitsanschluss A bzw. B der Wegeventilanordnung 1 verbunden sind. Ein Tankanschluss T' des Wegeventils 1 steht über einen Ablaufkanal 18 mit dem Tankkanal T der Wegeventilanordnung 1 in Druckmittelverbindung.The pressure channel P of the directional control valve assembly 1 is connected to an input port P 'of the individual pressure compensator 4 whose output port A' is in fluid communication with an input port P "of the continuously variable directional control valve 8. The directional control valve 8 has two working ports in addition to the input port P" A "and B", which are each connected via a working channel 14 and 16 to the working port A and B of the directional control valve assembly 1. A tank connection T 'of the directional control valve 1 is connected via an outlet channel 18 to the tank channel T of the directional control valve arrangement 1 in pressure medium connection.

Ein Ventilschieber 22 des Wegeventils 8 ist in einer in dem Gehäuse 2 eingebrachten Ventilbohrung 24 axial verschiebbar geführt. In dieser sind sechs axial voneinander beabstandete Steuerkammern 26, 28, 30, 32, 34 und 36 ausgebildet.A valve spool 22 of the directional control valve 8 is guided in an axially displaceable manner in a valve bore 24 introduced in the housing 2. In this six axially spaced control chambers 26, 28, 30, 32, 34 and 36 are formed.

Die Steuerkammer 26 ist mit dem Eingangsanschluss P" verbunden. Über eine Messblende 37 des Ventilschiebers 22 ist die Druckmittelverbindung zwischen der Steuerkammer 26 und der benachbarten Steuerkammer 28 steuerbar. Letztere ist über einen Zwischenkanal 38 mit der in der in Figur 1 linken Steuerkammer 36 verbunden. Die Arbeitsanschlüsse A" und B" des Wegeventils 8 stehen jeweils mit der Steuerkammer 34 bzw. 30 in Druckmittelverbindung. Über eine Steuerkante 40 eines ersten Steuerbunds des Ventilschiebers 22 ist die Steuerkammer 28 mit der Steuerkammer 30 bzw. dem Arbeitsanschluss B" und über eine Steuerkante 42 eines zweiten Steuerbunds ist die Steuerkammer 36 mit der Steuerkammer 34 bzw. dem Arbeitsanschluss A" verbindbar.The control chamber 26 is connected to the input port P ", and the pressure medium connection between the control chamber 26 and the adjacent control chamber 28 is controllable via a metering orifice 37 of the valve spool 22. The latter is connected via an intermediate channel 38 to the one shown in FIG FIG. 1 left control chamber 36 connected. The working ports A "and B" of the directional control valve 8 are respectively connected to the control chamber 34 and 30 in fluid communication. Via a control edge 40 of a first control collar of the valve slide 22, the control chamber 28 with the control chamber 30 and the working port B "and via a control edge 42 of a second control collar, the control chamber 36 with the control chamber 34 and the working port A" connectable.

Über einen Druckwaagenkolben 44 der Individualdruckwaage 4 wird ein Druckgefälle und somit ein Volumenstrom an der Messblende 37 lastunabhängig konstant gehalten. Der Druckwaagenkolben 44 wird in Öffnungsrichtung mit einer Federkraft einer Druckwaagenfeder 46 sowie über einen stromabwärts der Messblende 37 des Ventilschiebers 22 des Wegeventils 8 abgegriffenen Druck beaufschlagt, wobei der Druck über einen vom Zwischenkanal 38 abzweigenden Kanal 47 abgegriffen wird. In Schließrichtung wird der Druckwaagenkolben 44 vom Druck stromaufwärts der Messblende 37 beaufschlagt, der über einen Steuerkanal 48 vom Ausgangsanschluss A' der Individualdruckwaage 4 abgegriffen ist.Via a pressure compensator piston 44 of the individual pressure compensator 4, a pressure gradient and thus a volume flow at the metering orifice 37 is kept constant independent of the load. The pressure compensator piston 44 is acted upon in the opening direction by a spring force of a pressure compensator spring 46 as well as via a downstream of the metering orifice 37 of the valve spool 22 of the directional control valve 8 tapped pressure, the pressure over a branched off from the intermediate channel 38 channel 47 is tapped. In the closing direction of the pressure compensator piston 44 is acted upon by the pressure upstream of the metering orifice 37, which is tapped via a control channel 48 from the output port A 'of the individual pressure compensator 4.

Eine stetige Verschiebung des Ventilschiebers 22 des Wegeventils 8 erfolgt über das elektrisch betätigbare Pilotventil 6, das beispielsweise als 4/3-Druckreduzierventil ausgeführt ist. Ein in der Figur 1 nicht dargestellter Ventilschieber des Pilotventils 6 ist über ein Proportional-Betätigungsmagneten 50 betätigbar. Das Pilotventil 6 ist an eine erste und zweite Steuerleitung 52, 54 angeschlossen, wobei die erste Steuerleitung 52 mit einem in der Fig. 1 linken Steuerraum 56 des Wegeventils 8 und die zweite Steuerleitung 54 mit einem rechten Steuerraum 58 verbunden ist. Mit dem Pilotventil 6 ist eine Druckmittelverbindung zwischen der Steuerleitung 52 und 54 und einer Pilotleitung 60 steuerbar, wobei jeweils eine der Steuerleitungen 52, 54 mit der Pilotleitung 60 und die jeweils andere mit einer Tankleitung 62 oder beide Steuerleitungen 52, 54 zur Druckentlastung der Steuerräume 56, 58 mit der Tankleitung 62 verbunden sind. Je nach Ansteuerung des Pilotventils 6 von dem Betätigungsmagneten 50 wird der Druck der Pilotleitung 60 auf einen gewünschten Steuerdruck zur Betätigung des Ventilschiebers 22 des Wegeventils 8 reduziert.A continuous displacement of the valve spool 22 of the directional control valve 8 via the electrically actuated pilot valve 6, which is designed for example as a 4/3 pressure reducing valve. An Indian FIG. 1 not shown valve spool of the pilot valve 6 can be actuated via a proportional actuating magnet 50. The pilot valve 6 is connected to a first and second control line 52, 54, wherein the first control line 52 with a in the Fig. 1 left control chamber 56 of the directional control valve 8 and the second control line 54 is connected to a right control chamber 58. With the pilot valve 6, a pressure medium connection between the control line 52 and 54 and a pilot line 60 is controllable, wherein in each case one of the control lines 52, 54 with the pilot line 60 and the other with a tank line 62 or both control lines 52, 54 for pressure relief of the control chambers 56th , 58 are connected to the tank line 62. Depending on the control of the pilot valve 6 of the actuating magnet 50, the pressure of the pilot line 60 is reduced to a desired control pressure for actuating the valve spool 22 of the directional control valve 8.

Die Tankleitung 62 des Pilotventils 60 ist des Weiteren mit einer Leckölleitung 63 verbunden, die über einen Ringspalt 61 zwischen dem Ventilschieber 22 und der Ventilbohrung 24 des Wegeventils 8 mit der Steuerkammer 36 verbunden ist.The tank line 62 of the pilot valve 60 is further connected to a drain line 63, which is connected via an annular gap 61 between the valve spool 22 and the valve bore 24 of the directional control valve 8 to the control chamber 36.

Der Ventilschieber 22 des Wegeventils 8 ist über eine im Steuerraum 58 angeordneten Zentrierfederanordnung 64 in seiner in der Fig. 1 dargestellten Grundposition vorgespannt, in der die Druckmittelverbindung des Eingangsanschlusses P" zur Steuerkammer 28 und die Druckmittelverbindung zwischen den Steuerkammern 28, 36 und den Arbeitsanschlüssen A", B" zugesteuert ist.The valve spool 22 of the directional control valve 8 is connected via a arranged in the control chamber 58 Zentrierfederanordnung 64 in his in the Fig. 1 shown biased position in which the pressure medium connection of the input port P "to the control chamber 28 and the pressure medium connection between the control chambers 28, 36 and the working ports A", B "is controlled.

Zum Verschieben des Ventilschiebers 22 des Wegeventils 8 in der Fig. 1 nach rechts und somit zur Herstellung einer Druckmittelverbindung zwischen dem Eingangsanschluss P" und dem Arbeitsanschluss B", ist der Ventilschieber 22 über den linken Steuerraum 56 mit dem Steuerdruck beaufschlagbar, wobei der Steuerraum 56 über die erste Steuerleitung 52 und über das Pilotventil 6 mit der Pilotleitung 60 verbunden ist und der Steuerraum 58 über die Steuerleitung 54 und über das Pilotventil 6 zur Tankleitung 62 entlastet ist. In dieser Verschieberichtung wird über eine Steuerkante 65 eines Steuerbunds 66 des Ventilschiebers 22 die Druckmittelverbindung des Arbeitsanschlusses A" über die Steuerkammer 34 zur Steuerkammer 32 und somit zum Ablaufkanal 18 aufgesteuert.To move the valve spool 22 of the directional control valve 8 in the Fig. 1 to the right and thus to produce a pressure medium connection between the input port P "and the working port B", the valve spool 22 is on the left Control chamber 56 can be acted upon by the control pressure, wherein the control chamber 56 is connected via the first control line 52 and the pilot valve 6 with the pilot line 60 and the control chamber 58 is relieved via the control line 54 and the pilot valve 6 to the tank line 62. In this direction of displacement, the pressure medium connection of the working port A "via the control chamber 34 to the control chamber 32 and thus to the outlet channel 18 is opened via a control edge 65 of a control collar 66 of the valve slide 22.

Zum Verschieben des Ventilschiebers 22 aus der Grundposition in der Fig. 1 nach links wird dieser über den rechten Steuerraum 58 mit dem Steuerdruck beaufschlagt, wobei dieser über die zweite Steuerleitung 54, über das Pilotventil 6 mit der Pilotleitung 60 und der linke Steuerraum 58 über die erste Steuerleitung 52, über das Pilotventil 6 mit der Tankleitung 62 verbunden ist. In dieser Verschieberichtung wird die Druckmittelverbindung zwischen dem Eingangsanschluss P" und dem Arbeitsanschluss A" und zwischen dem Arbeitsanschluss B" und dem Tankanschluss T' aufgesteuert.To move the valve spool 22 from the basic position in the Fig. 1 to the left this is acted upon via the right control chamber 58 with the control pressure, which is connected via the second control line 54, via the pilot valve 6 with the pilot line 60 and the left control chamber 58 via the first control line 52, via the pilot valve 6 to the tank line 62 is. In this displacement direction, the pressure medium connection between the input terminal P "and the working port A" and between the working port B "and the tank port T 'is opened.

Figur 2 zeigt einen vergrößerten Ausschnitt der Wegeventilanordnung 1 aus Figur 1 im Bereich des Sperrventils 10. Dieses ist zur Minimierung einer verbraucherseitigen Lastabsenkung aufgrund von Leckage über das Wegeventil 8 in dem Arbeitskanal 14 angeordnet. Das Sperrventil 10 hat einen in einer Sperrventilbohrung 67 geführten Sperrventilkörper 68. Dieser liegt im Sperrzustand mit einer kegelförmigen Sitzfläche 70 auf einem Sperrventilsitz 72 auf. Über eine Ventilfeder 73 ist der Sperrventilkörper 68 auf den Sperrventilsitz 72 vorgespannt, wobei sich die Feder an einer eingebrachten Halteplatte 74 abstützt. Diese sitzt im Bodenbereich des Arbeitsanschlusses A. Zur außenseitigen Umströmung der Halteplatte 74 sind in deren Bereich zumindest zwei gleichförmige Ausnehmungen 76 in einer Bohrung des Arbeitsanschluss A vorgesehen. FIG. 2 shows an enlarged section of the directional control valve assembly 1 FIG. 1 in the region of the shut-off valve 10. This is arranged in the working channel 14 to minimize a load-side load reduction due to leakage via the directional control valve 8. The check valve 10 has a guided in a check valve bore 67 check valve body 68. This is in the off state with a conical seat 70 on a check valve seat 72. Via a valve spring 73, the check valve body 68 is biased onto the check valve seat 72, wherein the spring is supported on an inserted holding plate 74. This sits in the bottom region of the working port A. For the outside flow around the holding plate 74 at least two uniform recesses 76 are provided in a bore of the working port A in the area.

An die kegelförmigen Sitzfläche 70 des Sperrventilkörpers 68 schließt sich vom Arbeitsanschluss A wegweisend ein Ventilkörperschaft 78 an. Dieser hat einen Kernbereich, um den drei radial abstehende rippenartige Führungsstege 80 zur Führung des Sperrventilkörpers 68 in der Sperrventilbohrung 67 angeordnet sind, wobei in der Ansicht in Figur 2 ein Führungssteg 80 ersichtlich ist. In Zwischenräumen 82 zwischen den Führungsstegen 80 fließt Druckmittel bei geöffneten Sperrventil 10.At the conical seat surface 70 of the check valve body 68 connects from the working port A pioneering a valve body stem 78 at. This has a core region around which three radially projecting rib-like guide webs 80 for guiding the check valve body 68 are arranged in the check valve bore 67, wherein in the view in FIG. 2 a guide bar 80 can be seen. In intermediate spaces 82 between the guide webs 80, pressure fluid flows when the shut-off valve 10 is open.

Im Kernbereich des Ventilkörperschafts 78 ist eine Vorsteuerung 84 für das Sperrventil 10 ausgebildet. Die Sperrrichtung der Vorsteuerung entspricht der des Sperrventils 10. Ein kugelförmiger Vorsteuerkörper 86 ist in einer zweistufigen Vorsteuerbohrung 88 des Sperrventils 10 angeordnet, wobei dieser über eine nicht dargestellte Feder auf einer als Sitz ausgebildeten Stufe 89 der Vorsteuerbohrung 88 vorgespannt ist und eine Vorsteuerbohrung 90 verschließt. An einer Unterseite des Ventilkörperschafts 78 ist ein nach unten offener Querkanal 91 eingefräst, der die Vorsteuerbohrung 90 schneidet.In the core region of the valve body shaft 78, a pilot control 84 is formed for the check valve 10. A ball-shaped pilot body 86 is disposed in a two-stage pilot port 88 of the check valve 10, which is biased by a spring, not shown, on a trained as a seat stage 89 of the pilot port 88 and a pilot port 90 closes. On an underside of the valve body shaft 78, a downwardly open transverse channel 91 is milled, which intersects the pilot control bore 90.

Der Sperrventilkörper 68 und der Vorsteuerkörper 86 sind über einen Stößel 92 aufsteuerbar. Dieser ist etwa senkrecht zu einer Achse des Ventilschiebers 22 des Wegeventils 8 im Gehäuse 2 geführt und über eine am Ventilschieber 22 zwischen dem zweiten in der Figur 2 linken Steuerkante 42 und der benachbarten Steuerbund 66 ausgebildeten Kulisse 94 in Aufsteuerrichtung des Sperrventils 10 verschiebbar. Die Kulisse 94 weist einen etwa kegelstumpfförmigen Umfang auf, dessen Durchmesser in Richtung zum Steuerbund 66 abnimmt. Der Stößel 92 hat einen vom Ventilschieber 22 wegweisenden radial zurückgestuften Endabschnitt 96, der in die Hilfsbohrung 90 des Sperrventilkörpers 68 zu dessen Betätigung eingetaucht ist.The check valve body 68 and the pilot body 86 can be opened via a plunger 92. This is guided approximately perpendicular to an axis of the valve spool 22 of the directional control valve 8 in the housing 2 and via a valve spool 22 between the second in the FIG. 2 left control edge 42 and the adjacent control collar 66 formed backdrop 94 in the direction of the check valve 10 slidably. The link 94 has an approximately frusto-conical circumference, the diameter of which decreases in the direction of the control collar 66. The plunger 92 has a radially rearwardly directed end portion 96, facing away from the valve spool 22, which is immersed in the auxiliary bore 90 of the check valve body 68 for actuation thereof.

In der in Figur 2 gezeigten Grundstellung des Ventilschiebers 22 des Wegeventils 8 liegt der Stößel 92 mit einer vom Sperrventil 10 wegweisenden Stirnfläche 98 im Bereich des minimalen Durchmessers der Kulisse 94 an dieser an. Bei einer Verschiebung des Ventilschiebers 22 in der Figur 1 nach rechts, gleitet der Stößel 92 mit der Stirnfläche 98 entlang der Kulisse 94 und wird dabei in Richtung des Sperrventils 10 verschoben, wobei mit dem Endabschnitt 96 des Stößels 92 der Vorsteuerkörper 86 der Vorsteuerung 84 in Öffnungsrichtung bewegt wird. Das Öffnen der Vorsteuerung 84 erfolgt vor dem Aufsteuern der Druckmittelverbindung zwischen dem Arbeitskanal 14 und dem Ablaufkanal 18 über die Steuerkante 65 des Steuerbunds 66. Dies ermöglicht das Abbauen beispielsweise eines im eingangs im Stand der Technik erläuterten unzulässig hohen Drucks im Arbeitsanschluss A bzw. daran angeschlossenen Leitungsstrangs in einen Zwischenraum 100 der Wegeventilanordnung 1, ohne das ein Lastdruck im Arbeitsanschluss A oder im Leitungsstrang abfällt.In the in FIG. 2 shown basic position of the valve spool 22 of the directional control valve 8 is the plunger 92 with a direction away from the check valve 10 end face 98 in the region of the minimum diameter of the link 94 at this. With a displacement of the valve spool 22 in the FIG. 1 to the right, the plunger 92 slides with the end face 98 along the guide 94 and is thereby displaced in the direction of the check valve 10, wherein the end portion 96 of the plunger 92 of the pilot body 86 of the feedforward control 84 is moved in the opening direction. The opening of the feedforward control 84 takes place before opening the pressure medium connection between the working channel 14 and the drainage channel 18 via the control edge 65 of the control collar 66. This allows the dismantling of, for example, an inadmissible high pressure explained in the background in the working connection A or connected thereto Wiring harness in a gap 100 of the directional control valve assembly 1, without a load pressure in the working port A or in the wiring harness drops.

Der Zwischenraum 100 ist axial zwischen der Steuerkante 65 des Steuerbunds 66 und der Steuerkante 42 vorgesehen und wird abschnittsweise von der Ventilbohrung 24 und dem Ventilschieber 22 begrenzt. Der Durchmesser des Ventilschiebers 22, zwischen der Steuerkante 65 und der Kulisse 94, entspricht etwa dem minimalen Durchmesser der Kulisse 94.The gap 100 is provided axially between the control edge 65 of the control collar 66 and the control edge 42 and is partially bounded by the valve bore 24 and the valve spool 22. The diameter of the valve spool 22, between the control edge 65 and the gate 94, corresponds approximately to the minimum diameter of the gate 94th

Durch die vorbeschriebene Öffnung der Vorsteuerung 84 ist ein Abströmen eines Kompressionsvolumens bzw. eines Entlastungsvolumen und somit ein Abbau eines unzulässig hohen Drucks in den Arbeitskanal 14, die Steuerkammer 34 und den Zwischenraum 100 ermöglicht. Wird durch Verschiebung des Ventilschiebers 22 in der Figur 2 nach links die Vorsteuerung 84 wieder geschlossen, dann wird der Druck im Arbeitskanal 14, der Steuerkammer 34 und dem Zwischenraum 100 zum Einen über eine Spaltleckage zwischen dem Steuerbund 66 und der Ventilbohrung 24 zum Ablaufkanal 18 und zum Anderen über eine Spaltleckage zwischen dem der Steuerkante 42 zugeordneten Steuerbund und der Ventilbohrung 24 zum Zwischenkanal 38, und von dort zur Tankleitung 62 abgebaut. Das Öffnen der Vorsteuerung 84 des Sperrventils 10 bei einer über die Steuerkante 65 des Steuerbunds 66 des Ventilschiebers 22 zugesteuerten Druckmittelverbindung zum Ablaufkanal 18 zum Abbau eines Drucks wird als Entlastungszyklus bezeichnet.By the above-described opening of the pilot control 84 is a discharge of a compression volume or a discharge volume and thus a reduction of an excessively high pressure in the working channel 14, the control chamber 34 and the gap 100 allows. Is by displacement of the valve spool 22 in the FIG. 2 to the left the pilot control 84 again closed, then the pressure in the working channel 14, the control chamber 34 and the gap 100 on the one hand via a gap leakage between the control collar 66 and the valve bore 24 to the drain channel 18 and the other via a gap leakage between the control edge 42nd associated control collar and the valve bore 24 to the intermediate channel 38, and reduced from there to the tank line 62. The opening of the pilot control 84 of the check valve 10 at a controlled via the control edge 65 of the control collar 66 of the valve spool 22 fluid connection to the drain passage 18 for reducing a pressure is referred to as discharge cycle.

Zum Ermöglichen eines Abströmens von Druckmittel von einem Verbraucher über den Arbeitsanschluss A und das Sperrventil 10 wird der Ventilschieber 22 in der Figur 2 nach rechts verschoben, wobei, wie oben beschrieben, der Stößel 92 über die Kulisse 94 in Richtung des Sperrventils 10 bewegt wird. Nachdem der Vorsteuerkörper 86 geöffnet ist, wird eine Druckdifferenz zwischen dem Druck im Arbeitskanal 14, der Steuerkammer 34 und dem Zwischenraum 100 und dem Druck im Arbeitsanschluss A verringert. Bei weiterer Verschiebung des Ventilschiebers 22 ist der Endabschnitt 96 vollständig in die Hilfsbohrung 90 des Sperrventils 10 eingetaucht und der Stößel 92 schiebt den im Wesentlichen druckausgeglichenen Sperrventilkörper 68 in Öffnungsrichtung, wobei die Druckmittelverbindung von dem Arbeitskanal 14, der Steuerkammer 34 und dem Zwischenraum 100 zur Ablaufleitung 18 über den Steuerbund 66 des Ventilschiebers 22 aufgesteuert wird.To allow a flow of pressure medium from a consumer via the working port A and the check valve 10, the valve spool 22 in the FIG. 2 shifted to the right, wherein, as described above, the plunger 92 is moved via the guide 94 in the direction of the check valve 10. After the pilot body 86 is opened, a pressure difference between the pressure in the working channel 14, the control chamber 34 and the gap 100 and the pressure in the working port A is reduced. Upon further displacement of the valve spool 22, the end portion 96 is fully immersed in the auxiliary bore 90 of the check valve 10 and the plunger 92 pushes the substantially pressure-balanced check valve body 68 in the opening direction, the pressure medium connection from the working channel 14, the control chamber 34 and the gap 100 to the drain line 18 is turned on via the control collar 66 of the valve spool 22.

Der Verschiebeweg des Ventilschiebers 22 des Wegeventils 8 wird über einen mit diesem verbundenen Wegaufnehmer 102, siehe Figur 1, erfasst. Dieser ist etwa koaxial zum Ventilschieber 22 links in der Figur 1 mit dem Gehäuse 2 verbunden. Des Weiteren ist eine Ventilelektronik 104 mit einem Temperatursensor am Gehäuse 2 angeordnet. Durch den Wegaufnehmer 102 und der Ventilelektronik 104 ist der Verschiebeweg und die Verschiebedauer des Ventilschiebers 22 genau steuerbar, womit die Taktung und die Dauer der Entlastungszyklen beliebig einstellbar sind.The displacement of the valve spool 22 of the directional control valve 8 is via a connected to this transducer 102, see FIG. 1 , detected. This is approximately coaxial with the valve spool 22 left in the FIG. 1 connected to the housing 2. Furthermore, a valve electronics 104 with a temperature sensor on the housing 2 is arranged. By Wegaufnehmer 102 and the valve electronics 104, the displacement and the displacement time of the valve spool 22 is precisely controlled, whereby the timing and the duration of the discharge cycles are arbitrarily adjustable.

Eine Taktung der Entlastung des Arbeitsanschlusses A über das Sperrventil 10 mit einem Entlastungszyklus erfolgt beispielsweise in Abhängigkeit von einer gemessenen Temperaturerhöhung in dem an den Arbeitsanschluss A angeschlossenen Leitungsstrang. Bei einem Entlastungszyklus können bei einem Lastdruck von 250 bar etwa 0,16 ml an Kompressionsvolumen abgebaut werden.A timing of the discharge of the working port A via the check valve 10 with a discharge cycle takes place, for example, as a function of a measured temperature increase in the connected to the working port A wiring harness. During a discharge cycle, approximately 0.16 ml of compression volume can be released at a 250 bar load pressure.

Die Länge der Öffnungszeit der Vorsteuerung 84 des Sperrventils 10 in der Figur 2 bei einem Entlastungszyklus ist recht unkritisch, da kein Lastdruck zum Tankanschluss T abgebaut wird.The length of the opening time of the pilot control 84 of the check valve 10 in the FIG. 2 in a discharge cycle is quite uncritical because no load pressure to the tank port T is reduced.

Die Entlastungseinrichtung erfordert keinen zusätzlichen Bauraum.The relief device requires no additional space.

Die Steuerung der Entlastungszyklen kann beispielsweise über eine Fahrzeugelektronik oder über die Ventilelektronik 104 erfolgen.The control of the unloading cycles can take place, for example, via vehicle electronics or via the valve electronics 104.

Figur 3 zeigt ein Diagramm, bei dem das Kompressionsvolumen bzw. das Entlastungsvolumen in cm3 und % über den Lastdruck in bar im Arbeitsanschluss A aus Figur 2 aufgetragen ist. Ein oberer Graph 108 in Figur 3 zeigt dabei das Kompressionsvolumen in cm3 als Funktion des Lastdrucks. Bei steigendem Lastdruck steigt auch das Kompressionsvolumen etwa linear an. Beispielsweise bei einem Lastdruck von 350 bar beträgt das über den Entlastungszyklus abbaubare Kompressionsvolumen etwa 0,22 cm3. Ein unterer Graph 110 in Figur 3, der das Kompressionsvolumen in % als Funktion des Lastdrucks zeigt, verläuft flacher als der Graph 108. Durch den linearen Zusammenhang zwischen dem Kompressionsvolumen und dem Lastdruck, ist der Abbau des Kompressionsvolumens über die Entlastungszyklen bei unterschiedlichen Lastdrücken einfach und genau steuerbar. FIG. 3 shows a diagram in which the compression volume and the discharge volume in cm 3 and% on the load pressure in bar in the working port A from FIG. 2 is applied. An upper graph 108 in FIG FIG. 3 shows the compression volume in cm 3 as a function of the load pressure. As the load pressure increases, the compression volume also increases approximately linearly. For example, at a load pressure of 350 bar, the compression volume which can be broken down via the discharge cycle is about 0.22 cm 3 . A lower graph 110 in FIG FIG. 3 , which shows the compression volume in% as a function of the load pressure, is flatter than the graph 108. Due to the linear relationship between the compression volume and the load pressure, the degradation of the Compression volume over the discharge cycles at different load pressures easily and accurately controllable.

In Figur 4 ist ein weiteres Diagramm offenbart, wobei der Lastdruck in bar auf der Abszisse und eine Druckentlastung ebenfalls in bar auf der Ordinate abgebildet ist. Es sind vier Graphen 112, 114, 116 und 118 gezeigt, die die Druckentlastung als Funktion des Lastdrucks bei jeweils unterschiedlichen Rohrlängen von 50, 100, 200 bzw. 400 cm an beispielhaften Durchmessern von einem an den Arbeitanschluss A in Figur 2 angeschlossen Rohr abbilden. Die Druckentlastung ist dabei ein Maß für den bei einem Entlastungszyklus abgebauten Druck in dem Arbeitsanschluss A und dem daran angeschlossenem Rohr.In FIG. 4 is another diagram disclosed, wherein the load pressure in bar on the abscissa and a pressure relief is also shown in bar on the ordinate. Four graphs 112, 114, 116 and 118 are shown which show the pressure relief as a function of the load pressure at respectively different tube lengths of 50, 100, 200 and 400 cm at exemplary diameters from one to the working port A in FIG FIG. 2 connect connected pipe. The pressure relief is a measure of the reduced in a discharge cycle pressure in the working port A and the connected pipe.

Die Graphen 112 bis 118 steigen etwa linear mit dem Lastdruck an, wobei bei größerer Rohrlänge die Steigung des jeweiligen Graphen 112 bis 118 flacher wird. Beispielsweise bei einer Rohrlänge von 50 cm, beträgt die Druckentlastung bzw. der abgebaute Druck eines Entlastungszyklus bei einem Lastdruck von 350 bar etwa 60 bar, was am obersten Graphen 112 in Figur 4 ablesbar ist. Bei einer Rohrlänge von 400 cm beträgt die Druckentlastung etwa 10 bar bei gleichem Lastdruck, was der Graph 118 zeigt.The graphs 112 to 118 increase approximately linearly with the load pressure, with a larger pipe length the slope of the respective graph 112 to 118 becomes flatter. For example, with a tube length of 50 cm, the pressure relief or the reduced pressure of a discharge cycle at a load pressure of 350 bar is about 60 bar, which is at the top graph 112 in FIG. 4 is readable. With a pipe length of 400 cm, the pressure relief is about 10 bar with the same load pressure, which shows the graph 118.

Figur 5 stellt ein Diagramm mit einen Lastdruck- und Temperaturverlauf als Funktion der Zeit dar. Die Abszisse bildet dabei die Zeit in min, die linke Ordinate in Figur 5 den Lastdruck in bar und die rechte Ordinate einen Temperaturanstieg in einem am Arbeitanschluss A aus Figur 2 angeschlossenem Rohr mit 200 cm Länge. Der Temperaturanstieg, beispielsweise aufgrund von Sonneneinstrahlung, soll etwa 4°C pro min betragen, was mit dem etwa linearen Graphen 120 in der Figur 5 gezeigt ist. Bei einem Ausgangslastdruck von 100 bar sind pro min etwa vier Entlastungszyklen vorgesehen. Ein Graph 122, der den Lastdruck als Funktion der Zeit abbildet, nähert sich asymptotisch etwa einem Druck von 210 bar an. Somit ist gezeigt, dass der Lastdruck trotz Temperaturanstieg augrund der Entlastungszyklen nicht mehr steigt und somit ein zu hoher Druck in einem an dem Arbeitsanschluss A angeschlossenem Rohr vermieden ist. FIG. 5 represents a diagram with a load pressure and temperature curve as a function of time. The abscissa forms the time in min, the left ordinate in FIG. 5 the load pressure in bar and the right ordinate a rise in temperature in one at the work connection A from FIG. 2 connected pipe with 200 cm length. The increase in temperature, for example due to solar radiation, should be about 4 ° C per minute, which corresponds to the approximately linear graph 120 in FIG FIG. 5 is shown. At an output load pressure of 100 bar, approximately four discharge cycles are provided per minute. A graph 122 that maps the load pressure as a function of time approaches asymptotically to a pressure of 210 bar. Thus, it is shown that the load pressure no longer rises despite the increase in temperature augrund the discharge cycles and thus an excessive pressure in a connected to the working port A pipe is avoided.

Offenbart ist eine Wegeventilanordnung mit einem einen Ventilschieber aufweisenden Wegeventil. Über dieses ist eine Druckmittelverbindung zwischen einem Druckanschluss, einem Tankanschluss und zumindest einem Arbeitsanschluss steuerbar. In einem mit dem Arbeitsanschluss verbundenen Arbeitskanal ist ein Sperrventil angeordnet. Der Druck im Arbeitskanal ist mit einer Entlastungseinheit abbaubar, wobei die Druckmittelverbindung zwischen dem Arbeitskanal und dem Tankanschluss durch den Ventilschieber gesperrt ist. Die Entlastungseinheit hat einen Zwischenraum, der im Druckmittelströmungspfad zwischen dem Sperrventil und einer den Arbeitskanal zum Tankanschluss absperrenden Steuerkante des Ventilschiebers ausgebildet ist und zum Aufnehmen eines Kompressionsvolumens des Arbeitskanals vorgesehen ist. Der Zwischenraum ist durch Aufsteuern des Sperrventils mit dem Arbeitskanal verbindbar, wobei über die Steuerkante des Ventilschiebers die Verbindung zum Tankanschluss gesperrt ist.Disclosed is a directional control valve arrangement having a valve slide having a directional control valve. About this is a pressure medium connection between a pressure connection, a tank connection and at least one working port controllable. In a working channel connected to the working port a check valve is arranged. The pressure in the working channel is degradable with a discharge unit, wherein the pressure medium connection between the working channel and the tank connection is blocked by the valve spool. The relief unit has a gap which is formed in the pressure medium flow path between the check valve and the working channel to the tank connection shut-off control edge of the valve spool and is provided for receiving a compression volume of the working channel. The gap is connectable by opening the check valve with the working channel, via the control edge of the valve spool, the connection to the tank port is blocked.

Claims (8)

  1. Directional valve arrangement having a directional valve (8) which has a valve slide (22), via which a pressure medium connection between a pressure duct (P), an outlet duct (18) and a working duct (14) can be controlled, a pilot-controlled, unlockable shut-off valve (10) having a shut-off valve body (68) and a pilot control body (86) being provided in the working duct (14), which bodies can be opened mechanically by way of a displacement of the valve slide (22) in the case of a working duct (14) which is still shut off to the outlet duct (18) via a control edge (65) of the valve slide (22), an intermediate space (100) for receiving a compression volume of the working duct (14) being present in the pressure medium flow path between the shut-off valve (10) and that control edge (65) of the valve slide (22) which shuts off the working duct (14) to the outlet duct (18), characterized in that there is an electronic arrangement (104), by which the valve slide (22) of the directional valve (8) can be displaced from a basic position into a position, in which, in the case of a working duct (14) which is still shut off to the outlet duct (18) via the control edge (65), at least the pilot control body of the shut-off valve (10) is opened, and from which position the valve slide (22) of the directional valve (8) is reset into the basic position again.
  2. Directional valve arrangement according to Patent Claim 1, it being possible for the shut-off valve body (68) and the pilot control body (86) to be opened via a tappet (92) which can be actuated in the opening direction via a slotted guide (94) on the valve slide (22).
  3. Directional valve arrangement according to Patent Claim 1 or 2, the intermediate space (100) being delimited in sections by way of a control collar (66) of the valve slide (22), which control collar (66) forms the control edge (65).
  4. Directional valve arrangement according to Patent Claim 2 or 3, the slotted guide (94) being configured approximately between the control edges of the valve slide (22) which shut off the working duct (14) to the outlet duct (18) and the control edges of the valve slide (22) which shut off the pressure duct to the working duct (14).
  5. Directional valve arrangement according to one of the preceding patent claims, a gap leakage being provided between the intermediate space (100) and the outlet duct (18) via the valve slide (22).
  6. Directional valve arrangement according to one of the preceding patent claims, there being cycling of a relief of the working duct (14) via the relief unit (10, 65, 100) in a manner which is dependent on a measured temperature increase and/or a measured load pressure, in particular in the working duct (14).
  7. Directional valve arrangement according to one of the preceding patent claims, a displacement sensor (102) being connected to the valve slide (22) of the directional valve (8).
  8. Directional valve arrangement according to one of the preceding patent claims, the electronic arrangement (104) for actuating the directional valve (8) being arranged on the directional valve arrangement (1).
EP10006382.5A 2009-07-27 2010-06-19 Directional valve assembly Not-in-force EP2280179B1 (en)

Applications Claiming Priority (1)

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DE102009034616A DE102009034616A1 (en) 2009-07-27 2009-07-27 Way valve arrangement

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EP2280179A2 EP2280179A2 (en) 2011-02-02
EP2280179A3 EP2280179A3 (en) 2013-11-13
EP2280179B1 true EP2280179B1 (en) 2016-08-10

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EP10006382.5A Not-in-force EP2280179B1 (en) 2009-07-27 2010-06-19 Directional valve assembly

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EP (1) EP2280179B1 (en)
DE (1) DE102009034616A1 (en)

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DE102019204246A1 (en) * 2019-03-27 2020-10-01 Robert Bosch Gmbh Pilot control device for a directional valve without internal cable connections
DE102021212309A1 (en) 2021-11-02 2023-05-04 Robert Bosch Gesellschaft mit beschränkter Haftung Method of minimizing dither hum on a valve
DE102022204640A1 (en) 2022-05-12 2023-11-16 Robert Bosch Gesellschaft mit beschränkter Haftung Valve assembly for the front loader of an agricultural tractor
US12044323B2 (en) 2021-12-02 2024-07-23 Robert Bosch Gmbh Valve assembly with preloaded control oil return
DE102023204654A1 (en) 2023-05-17 2024-11-21 Robert Bosch Gesellschaft mit beschränkter Haftung valve assembly for operating a lifting mechanism

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Publication number Priority date Publication date Assignee Title
DE102019204246A1 (en) * 2019-03-27 2020-10-01 Robert Bosch Gmbh Pilot control device for a directional valve without internal cable connections
US11754096B2 (en) 2019-03-27 2023-09-12 Robert Bosch Gmbh Pilot device for a directional valve without internal cable connections
DE102021212309A1 (en) 2021-11-02 2023-05-04 Robert Bosch Gesellschaft mit beschränkter Haftung Method of minimizing dither hum on a valve
US12152610B2 (en) 2021-11-02 2024-11-26 Robert Bosch Gmbh Method for minimizing the dither hum on a valve
US12044323B2 (en) 2021-12-02 2024-07-23 Robert Bosch Gmbh Valve assembly with preloaded control oil return
DE102022204640A1 (en) 2022-05-12 2023-11-16 Robert Bosch Gesellschaft mit beschränkter Haftung Valve assembly for the front loader of an agricultural tractor
DE102023204654A1 (en) 2023-05-17 2024-11-21 Robert Bosch Gesellschaft mit beschränkter Haftung valve assembly for operating a lifting mechanism

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US20110017321A1 (en) 2011-01-27
DE102009034616A1 (en) 2011-02-03
EP2280179A3 (en) 2013-11-13
US8479768B2 (en) 2013-07-09
EP2280179A2 (en) 2011-02-02

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