EP1729014B1 - Bloc de commande et section de bloc de commande - Google Patents

Bloc de commande et section de bloc de commande Download PDF

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Publication number
EP1729014B1
EP1729014B1 EP06009768.0A EP06009768A EP1729014B1 EP 1729014 B1 EP1729014 B1 EP 1729014B1 EP 06009768 A EP06009768 A EP 06009768A EP 1729014 B1 EP1729014 B1 EP 1729014B1
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EP
European Patent Office
Prior art keywords
control
pressure
control block
working
chamber
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
EP06009768.0A
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German (de)
English (en)
Other versions
EP1729014A2 (fr
EP1729014A3 (fr
Inventor
Niki Nieland
Armin Stellwagen
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1729014A2 publication Critical patent/EP1729014A2/fr
Publication of EP1729014A3 publication Critical patent/EP1729014A3/fr
Application granted granted Critical
Publication of EP1729014B1 publication Critical patent/EP1729014B1/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
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0878—Assembly of modular units
    • F15B13/0896—Assembly of modular units using different types or sizes of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0871—Channels for fluid

Definitions

  • the invention relates to a control block for supplying pressure medium to a plurality of consumers according to the preamble of patent claim 1 and a control block section suitable for such a control block.
  • control blocks are used to control hydraulic consumers of mobile machines.
  • a forklift can be controlled via such a control block, the steering, as well as hydraulic cylinder for raising or lowering the fork and tilting the fork-carrying mast.
  • the nominal size of the control block is designed as a function of the consumer with the greatest pressure medium requirement.
  • the pressure medium requirement of the hydraulic cylinder assembly for lifting the fork is much greater than the pressure medium requirement of other consumers (steering, mast tilt), so that the nominal size of the control block is selected in response to the maximum pressure medium requirement and the smaller consumers associated control block sections are oversized. Since the costs of the hydraulic system are not insignificantly determined by the control block, it is endeavored to carry out this with possible small nominal size. A way out of this problem might be to design the nominal size of the control block as a function of the smaller consumers and then to allocate two or more directional valve sections to compensate for the larger load, due to the additional directional valve section the investment costs for such a solution too high.
  • the document DE 44 00 760 A1 describes a multi-way valve with multiple switch positions, which can be used for various valve functions.
  • the invention has for its object to provide a control block and a suitable control block for such a control block section, with the consumer with high pressure medium demand and consumers with relatively lower pressure medium requirement with low device complexity with pressure medium can be supplied.
  • the consumer with a larger pressure medium required associated control block section is executed with two working ports, which are connected depending on the setting of a directional valve control block section either with a pressure medium source or a pressure medium sink to actuate the associated consumer.
  • the flow cross section from the directional control valve is doubled up to a common supply line to the connected consumer or consumers, so that the hydraulic resistance compared to the conventional solutions is substantially reduced and the valve section is suitable for larger flow rates than in the prior art.
  • a directional control valve via which two control chambers connected to a working connection can be connected either to a pressure connection or to a tank connection, is per se already out of the JP 2093104
  • this valve has only a single working port and moreover, it is not executed as part of a control block section. Through this single working port of the directional control valve, the pressure loss at high flow rate is large, so that a larger nominal size must be used.
  • control block section for such a control block is designed with a continuously adjustable directional valve, the valve slide has piston collars, via the control edges, the connection between the two working ports and the pressure medium source or the pressure medium sink is adjustable.
  • This construction makes it possible to make the directional valve with a small axial length and thus extremely compact, so that integration into conventional control blocks can be carried out in a simple manner.
  • the controlled via the control block consumer can have a pressure chamber or two pressure chambers, in which case each of the pressure chambers is assigned its own control block section according to the invention.
  • the control block can be designed as an LS or LUDV control block.
  • the piston collar of the valve slide is completely covered by the housing web in the central position.
  • This piston collar has a control edge, via which the connection between a control port associated with a working port and a pressure control chamber associated with the pressure port is adjustable.
  • a second piston collar is in one embodiment with two control edges designed to adjust the connection between another working control chamber and a connected to a tank port tank control chamber or the pressure control chamber and the other working control chamber.
  • the third piston collar is also provided in this embodiment with a control edge to adjust the connection between the first working control chamber and a second tank control chamber.
  • a second piston collar is designed with a control edge over which the connection between the further working control chamber and the pressure control chamber is adjusted.
  • the third piston collar is designed with a control edge for adjusting the connection between the latter working control chamber and a further control chamber.
  • valve spool is designed with three adjacent to said piston collars piston necks.
  • the directional control valve has an LS control chamber, which can be acted upon by a passage passing through the valve spool with the load pressure in one of the working control chambers.
  • This channel opens in a preferred embodiment, on the one hand in a in a working control chamber (54, 58) movable piston collar section.
  • valve spool In an LS or LUDV control block section, it is preferred if the valve spool is designed with an LS control edge, via which one to the LS control chamber adjacent LS communication chamber in the middle position or in displacement of the valve spool in one direction with an adjacent tank control chamber is connectable.
  • FIG. 1 shows a highly simplified circuit diagram of an LS control block 1 of a forklift.
  • the basic structure of such a mobile control block 1 is known from the aforementioned data sheets RD 74 278 / 05.03 and RD 64 282 / 10.99, so that only the essential components for understanding the invention will be discussed.
  • Such an LS control block 1 has a pressure port P, a tank port T, a LS port LS and not shown control oil ports and external LS ports.
  • the tank connection T is via a tank line 2 with a tank T and the pump connection P is connected via a pump line 4 to the pressure port of a pump in the present case a variable displacement pump 6, the pump pressure is adjusted via a pump regulator 8 in response to the highest load pressure of the driven consumers so that it is always a predetermined ⁇ p above the highest load pressure.
  • This highest load pressure is picked up at the LS connection and routed to the pump regulator 8.
  • this highest load pressure is tapped via a shuttle valve cascade, not shown, from the actuated consumers and is applied to the LS connection.
  • the designed in disc design control block 1 consists essentially of an input element 10, on which the terminals P, T, LS and the other terminals (external LS terminals) are formed and a plurality of control block sections 12, 14, N and an end member 16th on which, for example, the control oil supply (stroke the front), pressure protection elements, filters and connections for supplying other control blocks with control oil (all connections not shown) may be formed.
  • Each of the directional valve or control block sections 12, 14, ... N is associated with a consumer of the forklift.
  • the section 12 is two parallel plunger cylinders 18, 20 for lifting a fork of the forklift and the section 14, for example, a tilting device 22, consisting of two parallel-connected differential cylinder for a fork-carrying mast of the forklift assigned.
  • Other sections may for example be associated with the hydraulic steering of the forklift or optional consumers.
  • the plunger cylinders 18, 20 have a higher pressure medium requirement than the other consumers (Steering, tilting device), for example, the pressure medium flow rate to the plunger cylinders is 180 1 / min, while the other consumers only need to be supplied with a lower pressure medium flow rate, for example, 50 1 / min.
  • the control section 12 described in more detail below is designed so that with a comparatively small nominal size of the control block, a sufficient supply of the plunger cylinders 18, 20 is ensured.
  • Each of the sections 12, 14, N for controlling a consumer consists in an LS control block essentially of a proportionally adjustable directional control valve 24, the pilot valves (pressure reducing valves), not shown, are assigned to control the position of a valve spool of the directional control valve 24.
  • the pressure medium volume flow over the controlled on an adjustment of the valve spool of the directional valves inlet orifice plates is kept constant independent of load at LS control blocks 1 via an upstream individual pressure compensator 26.
  • a pressure compensator piston is acted upon by a pressure compensator spring 28 and the load pressure on the associated consumer in the opening direction and by the pressure in front of the metering orifice in the closing direction.
  • the individual pressure compensator 26 is located in an inlet channel 30, which is connected on the one hand to the pressure port P to the input element 10 and on the other hand to an input port P of the directional control valve.
  • a tank connection T of the directional control valve 24 is connected via a discharge channel 32 to the tank connection T of the input element 10.
  • the directional control valve 24 of the section 12 further has two working ports A, B, which are connected via a first flow channel 34 and a second flow channel 36 with the two working ports A, B of the section 12. These two working ports A, B are connected via a branching flow line 38 with the two cylinder chambers 40, 42 of the plunger cylinder 18, 20.
  • control block section 12 the pressure medium supply of the two plungers 18, 20 connected in parallel takes place via the summed pressure medium volume flows conducted via the working ports A, B of the section, the pressure medium volume flows being brought together outside the section 12.
  • control block section 12 are further hydraulic components, such as pressure relief valves with combined feed function, shuttle valves for tapping the highest load pressure, LS-pressure relief valves, the aforementioned pressure reducing valves for controlling the directional control valve 24, etc. arranged. Since these hydraulic devices contribute nothing to the understanding of the invention, their description and illustration can be dispensed with.
  • the four ports P, T, A, B are shut off (closed center) in its spring-biased (centering spring not shown) middle position.
  • the valve spool in the illustration according to FIG. 1 down (position a) are shifted, so that the pressure port P of the directional control valve 24 is connected to the two working or output ports A, B and funded by the variable displacement pump 6 pressure medium volume flow on the individual pressure compensator 28, the open-way valve 24 and the two working ports A, B of the section 12 to the cylinder chambers 40, 42 of the plunger cylinder 18, 20 flows to extend this and lift the fork of the forklift accordingly.
  • valve spool About the valve spool are doing practically two parallel flow cross-sections, each with a Zulaufmessblende 44, 46 controlled, so that the pressure medium in two substantially equal partial volume flows through the two parallel flow channels 34, 36 to the associated consumer (plunger cylinder 18, 20) flows.
  • both working ports A, B of the section 12 can be connected depending on the position of the directional control valve 24 with the pressure medium source or the pressure medium sinks by the directional control valve arrangement according to the invention, so that each parallel partial flows are conveyed in the direction of the plunger cylinders 18, 20 or run from them.
  • valve spool 48 which is guided in a valve bore 50 of the disk-block-executed control block section 12.
  • the valve bore 50 is shown in the illustration FIG. 2 left to right to a tank control chamber 52 connected to the tank connection T (the connection designations below relate to the directional control valve 24), a work control chamber 54 connected to the working connection B, a pressure control chamber 56 connected to the pressure connection P, a further work control chamber 58, a further tank control chamber 60 , and a connected to a LS connection LS control chamber 62 extended.
  • LS connection LS control chamber 62 On both sides of the LS control chamber 62, two LS connection chambers 64, 66 are formed.
  • Such a constructed valve bore 50 is also used in the aforementioned prior art according to the data sheet RD 64 278 and RD 64 282.
  • the guided within the valve bore valve slide 48 has two end-side end collars 68, 70, between which a central piston collar 72, a second piston collar 74 and a left of the piston collar 72 arranged third piston collar 76 is formed, the piston collars on four piston necks 78, 80, 82, 84 are spaced from each other.
  • the second piston collar 74 has a substantially greater axial length than the two piston collars 76, 72 which are spaced apart from the piston neck 80.
  • At the end collar which is likewise designed with a comparatively large axial length (left in FIG FIG.
  • annular groove 86 is formed, via which in the illustrated center position of the valve slide 48, the LS control chamber 62 is connected to the two adjacent LS communication chambers 64, 66.
  • the central piston collar 72 is covered in the middle position shown by a housing web 88 between the working control chamber 58 and the pressure control chamber 56, so that the pressure control chamber 56 can be performed with a relatively small axial length and thus the directional control valve 24 is relatively short.
  • the valve spool 48 is penetrated by a channel, of which in FIG. 2 only the mouth areas 90, 92 are visible.
  • the channel opens in the Center position of the directional control valve 24 on the one hand in the LS control chamber 62 and on the other hand in the piston collar 74 portion of a housing web 94 between the working control chamber 58 and the pressure control chamber 56.
  • the channel mouth 90 arranged there is thus covered by the housing web 94 in the middle position.
  • two control edges 96, 98 are formed.
  • two further control edges 98, 100 are formed and at the in FIG. 2
  • Right end face of the end collar 70 is formed a fourth control edge 102, via which in the center position, the pressure medium connection between the adjacent tank control chamber 60 and the LS connection chamber 64 is opened.
  • control edges 96, 98, 100 As in the switching symbol of the directional control valve 24 in FIG. 1 shown, in the middle position by the aforementioned control edges 96, 98, 100, the ports A, B, P and T of the directional control valve shut off.
  • the control edges are each designed with fine control notches.
  • FIG. 3 is the directional control valve 24 in two positions a, b adjusted, wherein in the upper position (a), the two working ports A, B of the directional valve 24 with the pressure port P and in the lower position (b) the two working ports A, B with the tank or drain port T of the directional control valve 24 are connected.
  • valve spool 48 from the in FIG. 2 shown middle position shifted to the right. This is done in which a limited by the end collar 70 control chamber 104 is acted upon by the pilot valves (pressure reducing valves), not shown, with a control pressure, so that the valve spool 48 by acting on the end face of the end collar 70 control pressure against the force of also not shown Zentrierfederanssen is moved.
  • pilot valves pressure reducing valves
  • Zentrierfederan angel By this axial displacement in dependence on the height of the control pressure, an opening cross section between the pressure control chamber 56 and the two adjacent work control chambers 58 and 54 is opened by the control edges 98, 99. That is, by the two control edges 98, 99, the two in FIG.
  • FIG. 3 Below a position (b) of the directional control valve 24 is shown, in which the pressure medium flows from the plunger cylinders 18, 20 to the tank T out.
  • the valve slide 48 from the in FIG. 2 shown center position shifted to the left, in which via the pilot control a limited by the right end collar 68 control chamber 106 is subjected to a control pressure.
  • the channel opens via the channel mouth 92 in the LS connection chamber 66, which is connected via the annular groove 86 with the LS control chamber 62.
  • the right-most holes of the channel mouth 90 is covered by the housing web 94.
  • the LS control chamber 62 may be connected in the illustrated position via the control edge 102 of the left end collar 70 and the LS connection chamber 64 with the tank control chamber 60 of the directional control valve 24, so that in the LS control chamber 62 of the section 12 the tank pressure is applied.
  • FIG. 4 an embodiment with a modified valve spool 48 is shown.
  • the structure of the valve bore 50 is substantially the same as in the above-described embodiment, so that corresponding components are provided with the same reference numerals and a repeated description to avoid repetition is omitted.
  • the two control edges 99, 100 are formed on a single, comparatively long central piston collar 108.
  • the control edge 98 is formed on a comparatively short further piston collar 110 and the control edge 96 is formed in this embodiment on the right Stirnbund 68, which is designed with a larger axial length than in the above-described embodiment.
  • the short piston collar 110 is substantially covered by a housing web 111 between the pressure control chamber 56 and the working control chamber 54.
  • the other Stirnbund 70 (left in FIG. 4 ) has the same structure as in the above-described embodiment.
  • the channel for tapping the load pressure opens at the in FIG.
  • FIG. 5 is to extend the plunger cylinder 18, 20 of the valve slide 48 by applying the right control chamber 106 with a control pressure from the in FIG. 4 shown center position to the left position (a) shifted, so that the comparatively short further piston collar 110 is completely accommodated in the pressure control chamber 56, whose axial length is greater than that of the other piston collar 110. That is, via the control edge 98, the pressure medium connection of the pressure control chamber 56 to the working control chamber 54 and the control edge 99 of the piston collar 108, the pressure control chamber 56 is opened with the other working control chamber 58 and correspondingly opened the two inlet orifices 44, 46 at the axial displacement of the valve spool 48.
  • the end collar 70 could also be designed such that in the positions of the directional valve spool 24 into which the pressure medium from the plunger cylinders 18, 20 runs, the LS control chamber 62 is connected to the tank.
  • the pressure medium flows from the two cylinder chambers 40, 42 of the plunger cylinder 18, 20 from the tank T of the hydraulic system, wherein the pressure medium flow is determined by the controlled flow cross-sections, in which in FIGS. 4 and 5 illustrated embodiment, only three piston necks 78, 112 and 114 are required, so that the production of in FIG. 4 illustrated embodiment is somewhat simpler than the embodiment described above.
  • suitable LS channels or grooves, bores would have to be provided in order to be able to be connected to the tank connection T in the middle position and, if necessary, in the drainage position (working connections A, B of the directional control valve). to connect the LS control chamber 62 or at least the LS communication chamber 64 to the tank T.
  • a single-acting consumer (plunger cylinder 18, 20) is controlled via the control block section 12.
  • the control of double-acting consumer is possible, in which case each pressure chamber of the consumer is assigned a control block section 12 with the above-described structure.
  • control block for supplying pressure medium to at least one consumer with a large pressure medium requirement and at least one smaller consumer and a control block section suitable for such a control block, via which the larger consumer can be supplied with pressure medium.
  • This control block section has two working ports, both of which are connectable to the pressure space, so that pressure fluid flows through two parallel pressure fluid flow paths toward the consumer.

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

Claims (12)

  1. Bloc de commande pour l'alimentation en fluide sous pression d'au moins un consommateur (18, 20) ayant un grand besoin en fluide sous pression et d'au moins un plus petit consommateur (22), au moins une section de bloc de commande (12, 14, N) avec une soupape de distribution respective (24) à réglage en continu étant associée à chaque consommateur (18, 20 ; 22), par le biais de laquelle soupape de distribution un espace de pression (42, 44) du consommateur (18, 20) peut être connecté à une source de fluide sous pression (B) ou à un collecteur de fluide sous pression (T), caractérisé en ce que la section de bloc de commande (12) associée au plus gros consommateur (18, 20) présente une soupape de distribution hydraulique (24) à réglage en continu avec deux raccords de travail (A, B), qui sont tous deux connectés à l'espace de pression (40, 42), et la section de bloc de commande (12) présentant un raccord de pression (P) et un raccord de sortie (T), les deux raccords de travail (A, B) pouvant être connectés en commun au raccord de pression (P) ou au raccord de sortie (T) par le biais d'un tiroir de soupape (48) de la soupape de distribution (24) de la section de bloc de commande (12) associée au plus gros consommateur (18, 20).
  2. Bloc de commande selon la revendication 1, dans lequel le plus gros consommateur présente deux espaces de pression auxquels est à chaque fois associée une section de bloc de commande propre (12).
  3. Bloc de commande selon la revendication 1 ou 2, celui-ci étant réalisé sous forme de bloc de commande LS ou LUDV.
  4. Section de bloc de commande pour un bloc de commande selon l'une quelconque des revendications précédentes, comprenant un raccord de pression (P), un raccord de sortie (T) et deux raccords de travail (A, B), et une soupape de distribution hydraulique (24) à réglage en continu, par le biais du tiroir de soupape (48) de laquelle les deux raccords de travail (A, B) peuvent être connectés en commun au raccord de pression (P) ou au raccord de sortie (T).
  5. Section de bloc de commande selon la revendication 4, dans laquelle un tiroir de soupape (48) de la soupape de distribution (24) présente trois épaulements de piston (72, 74, 76), par le biais des arêtes de commande (96, 98, 99, 100) desquels la connexion entre les deux raccords de travail (A, B) et le raccord de pression (P) ainsi que le raccord de sortie (T) peut être commandée à l'ouverture ou à la fermeture, un épaulement de piston (72, 110), par le biais duquel la connexion entre le raccord de pression et au moins un raccord de travail (A, B) peut être commandée à l'ouverture ou à la fermeture, étant essentiellement complètement recouvert dans une position centrale par une nervure de boîtier (88, 111) entre une chambre de commande de travail (58, 54) associée au raccord de travail (A) et une chambre de commande de pression (56) associée au raccord de pression (P).
  6. Section de bloc de commande selon la revendication 5, dans laquelle l'épaulement de piston (72, 110) est recouvert par la nervure de boîtier (88, 111) et présente une arête de commande (99, 98) par le biais de laquelle la connexion entre la chambre de commande de travail (54, 58) et la chambre de commande de pression (56) peut être commandée à l'ouverture ou à la fermeture.
  7. Section de bloc de commande selon la revendication 5 ou 6, comprenant un deuxième épaulement de piston (74) avec deux arêtes de commande (96, 98), par le biais desquelles une connexion entre une chambre de commande de travail (54) et une chambre de commande de réservoir (52) connectée au raccord de réservoir (T) ou la chambre de commande de pression (56) et la chambre de commande de travail (54) peut être commandée à l'ouverture ou à la fermeture, le troisième épaulement de piston (76) présentant une arête de commande (100) pour la commande à l'ouverture ou à la fermeture de la connexion entre la première chambre de commande de travail (58) et une deuxième chambre de commande de réservoir adjacente (60).
  8. Section de bloc de commande selon la revendication 5 ou 6, comprenant un épaulement de piston supplémentaire (108) qui présente deux arêtes de commande (99, 100), dont l'une commande à l'ouverture ou à la fermeture la connexion entre la chambre de commande de pression (56) et la chambre de commande de travail (58) et l'autre commande à l'ouverture ou à la fermeture la connexion entre la chambre de commande de travail (58) et une chambre de commande de réservoir (60) connectée au raccord de réservoir, le troisième épaulement de piston (68) étant réalisé avec une arête de commande (96) par le biais de laquelle la connexion entre la chambre de commande de travail (54) et une autre chambre de commande de réservoir (52) peut être ajustée.
  9. Section de bloc de commande selon la revendication 8, dans laquelle le tiroir de soupape (48) est réalisé avec trois cols de piston (78, 112, 114).
  10. Section de bloc de commande selon l'une quelconque des revendications 4 à 9, comprenant une chambre de commande LS (62) qui peut être sollicitée par le biais d'un canal (90, 92) traversant le tiroir de soupape (48) avec la pression de charge dans l'une des chambres de commande de travail (54, 58).
  11. Section de bloc de commande selon la revendication 10, dans laquelle le canal débouche d'une part dans une rainure annulaire (86) du tiroir de soupape (48) et d'autre part au niveau de la périphérie extérieure d'une portion d'épaulement de piston (74, 108) déplaçable dans une chambre de commande de travail (54, 58).
  12. Section de bloc de commande selon la revendication 10 ou 11, comprenant une arête de commande LS (102) réalisée sur un épaulement frontal (70), par le biais de laquelle arête de commande LS une chambre de connexion LS (64) adjacente à la chambre de commande LS (62) peut être connectée à la chambre de commande de réservoir adjacente (60).
EP06009768.0A 2005-06-02 2006-05-11 Bloc de commande et section de bloc de commande Not-in-force EP1729014B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510025441 DE102005025441A1 (de) 2005-06-02 2005-06-02 Steuerblock und Steuerblocksektion

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EP1729014A2 EP1729014A2 (fr) 2006-12-06
EP1729014A3 EP1729014A3 (fr) 2008-03-12
EP1729014B1 true EP1729014B1 (fr) 2013-11-06

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DE (1) DE102005025441A1 (fr)

Cited By (1)

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CN107850226A (zh) * 2015-07-30 2018-03-27 迈特沃克股份有限公司 具有增加流量的电磁阀系统

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Publication number Priority date Publication date Assignee Title
SE533719C2 (sv) * 2009-04-24 2010-12-14 Nordhydraulic Ab Manöverventil
EP2770216B1 (fr) * 2013-02-20 2016-04-06 FESTO AG & Co. KG Agencement de vannes

Citations (1)

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CN107850226A (zh) * 2015-07-30 2018-03-27 迈特沃克股份有限公司 具有增加流量的电磁阀系统
CN107850226B (zh) * 2015-07-30 2019-07-26 迈特沃克股份有限公司 具有增加流量的电磁阀系统

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