EP2280179B1 - Agencement de distributeur - Google Patents

Agencement de distributeur 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)
English (en)
Other versions
EP2280179A2 (fr
EP2280179A3 (fr
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2280179A2 publication Critical patent/EP2280179A2/fr
Publication of EP2280179A3 publication Critical patent/EP2280179A3/fr
Application granted granted Critical
Publication of EP2280179B1 publication Critical patent/EP2280179B1/fr
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)
  • Valve Housings (AREA)
  • Multiple-Way Valves (AREA)

Claims (8)

  1. Agencement de distributeur comprenant un distributeur (8) qui présente un tiroir de soupape (22) par le biais duquel une connexion de fluide sous pression entre un canal de pression (P), un canal de sortie (18) et un canal de travail (14) peut être commandée, dans le canal de travail (14) étant prévue une soupape d'arrêt (10) pilotée, pouvant être débloquée, pourvue d'un corps de soupape d'arrêt (68) et d'un corps pilote (86), lesquels, par un déplacement du tiroir de soupape (22), peuvent être commandés à s'ouvrir mécaniquement lorsque le canal de travail (14) est encore bloqué par rapport au canal de sortie (18) par le biais d'une arête de commande (65) du tiroir de soupape (22), un espace intermédiaire (100) pour recevoir un volume de compression du canal de travail (14) étant prévu dans le chemin d'écoulement de fluide sous pression entre la soupape d'arrêt (10) et l'arête de commande (65) du tiroir de soupape (22) bloquant le canal de travail (14) par rapport au canal de sortie (18), caractérisé en ce qu'un agencement électronique (104) est prévu, lequel permet de déplacer le tiroir de soupape (22) du distributeur (8) d'une position de base dans une position dans laquelle, lorsque le canal de travail (14) est encore bloqué par le biais de l'arête de commande (65) par rapport au canal de sortie (18), au moins le corps pilote de la soupape d'arrêt (10) est commandé à l'ouverture et depuis laquelle le tiroir de soupape (22) du distributeur (8) est à nouveau ramené dans la position de base.
  2. Agencement de distributeur selon la revendication 1, dans lequel le corps de soupape d'arrêt (68) et le corps de soupape pilote (86) peuvent être commandés à l'ouverture par le biais d'un poussoir (92) pouvant être actionné dans la direction de commande à l'ouverture par le biais d'une coulisse (94) au niveau du tiroir de soupape (22).
  3. Agencement de distributeur selon la revendication 1 ou 2, dans lequel l'espace intermédiaire (100) est limité en partie par un épaulement de commande (66) du tiroir de soupape (22) constituant l'arête de commande (65).
  4. Agencement de distributeur selon la revendication 2 ou 3, dans lequel la coulisse (94) est réalisée approximativement entre les arêtes de commande du tiroir de soupape (22) bloquant le canal de travail (14) par rapport au canal de sortie (18) et les arêtes de commande bloquant le canal de pression par rapport au canal de travail (14).
  5. Agencement de distributeur selon l'une quelconque des revendications précédentes, dans lequel une fuite d'interstices entre l'espace intermédiaire (100) et le canal de sortie (18) est prévue par le biais du tiroir de soupape (22).
  6. Agencement de distributeur selon l'une quelconque des revendications précédentes, dans lequel une temporisation de détente du canal de travail (14) s'effectue par le biais de l'unité de détente (10, 65, 100) en fonction d'une augmentation de température mesurée et/ou d'une pression de charge mesurée, en particulier dans le canal de travail (14).
  7. Agencement de distributeur selon l'une quelconque des revendications précédentes, dans lequel un capteur de position (102) est connecté au tiroir de soupape (22) du distributeur (8).
  8. Agencement de distributeur selon l'une quelconque des revendications précédentes, dans lequel l'agencement électronique (104) pour commander le distributeur (8) est disposé au niveau de l'agencement de distributeur (1).
EP10006382.5A 2009-07-27 2010-06-19 Agencement de distributeur Not-in-force EP2280179B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009034616A DE102009034616A1 (de) 2009-07-27 2009-07-27 Wegeventilanordnung

Publications (3)

Publication Number Publication Date
EP2280179A2 EP2280179A2 (fr) 2011-02-02
EP2280179A3 EP2280179A3 (fr) 2013-11-13
EP2280179B1 true EP2280179B1 (fr) 2016-08-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10006382.5A Not-in-force EP2280179B1 (fr) 2009-07-27 2010-06-19 Agencement de distributeur

Country Status (3)

Country Link
US (1) US8479768B2 (fr)
EP (1) EP2280179B1 (fr)
DE (1) DE102009034616A1 (fr)

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DE102019204246A1 (de) * 2019-03-27 2020-10-01 Robert Bosch Gmbh Vorsteuergerät für ein Wegeventil ohne interne Kabelverbindungen
DE102021212309A1 (de) 2021-11-02 2023-05-04 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Minimierung des Dither-Brummens an einem Ventil
DE102022204640A1 (de) 2022-05-12 2023-11-16 Robert Bosch Gesellschaft mit beschränkter Haftung Ventilanordnung für den Frontlader eines landwirtschaftlichen Traktors

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DE102013223288A1 (de) 2013-11-15 2015-05-21 Robert Bosch Gmbh Hydraulische Steueranordnung
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US10989232B2 (en) 2015-09-18 2021-04-27 Rost Innovation LLC Control valve compensation system
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US9915368B2 (en) 2015-11-06 2018-03-13 Caterpillar Inc. Electrohydraulic valve having dual-action right-angle pilot actuator
US9803661B2 (en) 2015-11-06 2017-10-31 Caterpillar Inc. Valve having right-angle proportional and directional pilot actuators
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DE102018221288A1 (de) 2018-01-04 2019-07-04 Robert Bosch Gmbh Ventilanordnung, Arbeitsmaschine und Verfahren zum Steuern einer Ventilanordnung
DE102020214024A1 (de) 2020-11-09 2022-05-12 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulische Kupplungsbuchse
DE102021213691A1 (de) 2021-12-02 2023-06-07 Robert Bosch Gesellschaft mit beschränkter Haftung Ventilanordnung mit vorgespanntem Steuerölrücklauf
DE102022201584A1 (de) 2022-02-16 2023-08-17 Robert Bosch Gesellschaft mit beschränkter Haftung Ventilbaugruppe mit automatisch kalibrierbarer Stellungsregelung

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Publication number Priority date Publication date Assignee Title
DE102019204246A1 (de) * 2019-03-27 2020-10-01 Robert Bosch Gmbh Vorsteuergerät für ein Wegeventil ohne interne Kabelverbindungen
US11754096B2 (en) 2019-03-27 2023-09-12 Robert Bosch Gmbh Pilot device for a directional valve without internal cable connections
DE102021212309A1 (de) 2021-11-02 2023-05-04 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Minimierung des Dither-Brummens an einem Ventil
DE102022204640A1 (de) 2022-05-12 2023-11-16 Robert Bosch Gesellschaft mit beschränkter Haftung Ventilanordnung für den Frontlader eines landwirtschaftlichen Traktors

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

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