EP1370773B1 - Distributeur - Google Patents

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Publication number
EP1370773B1
EP1370773B1 EP02702621A EP02702621A EP1370773B1 EP 1370773 B1 EP1370773 B1 EP 1370773B1 EP 02702621 A EP02702621 A EP 02702621A EP 02702621 A EP02702621 A EP 02702621A EP 1370773 B1 EP1370773 B1 EP 1370773B1
Authority
EP
European Patent Office
Prior art keywords
annular duct
spool
pressure
drive
control valve
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.)
Expired - Lifetime
Application number
EP02702621A
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German (de)
English (en)
Other versions
EP1370773A1 (fr
Inventor
Winfried RÜB
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.)
Bucher Hydraulics GmbH
Original Assignee
Bucher Hydraulics GmbH
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Filing date
Publication date
Application filed by Bucher Hydraulics GmbH filed Critical Bucher Hydraulics GmbH
Publication of EP1370773A1 publication Critical patent/EP1370773A1/fr
Application granted granted Critical
Publication of EP1370773B1 publication Critical patent/EP1370773B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • 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
    • 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
    • Y10T137/5109—Convertible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • 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
    • Y10T137/87209—Electric
    • 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
    • Y10T137/87217—Motor

Definitions

  • the invention relates to a directional control valve in the preamble of claim 1 mentioned type.
  • Such directional control valves are suitable, for example, for controlling hydraulic drives, move the tools or tools on implements such as harvesters and loaders.
  • the hydraulic drives can, for example, single-acting Plunger cylinders, double-acting synchronous or differential cylinders or oil engines for be one or two directions of rotation.
  • Directional valves for such applications are in great Number known in various designs.
  • a directional control valve referred to in the preamble of claim 1 is known from DEA132 25th 003 and claiming the above priority FRA12 529 635 known.
  • the Quantity of pressure medium is proportional by means of clocked solenoid to a controlled analog input signal. In this way valve are no load reporting lines available. The usability of such a directional valve is thus severely limited. at one of the embodiments have three of the ring channels of the directional control valve connection to the tank. This solution is therefore not particularly advantageous, because it is with regard to dynamic behavior of the directional valve and also on the manufacturing costs the endeavor must be to keep the number of ring channels as low as possible.
  • a directional control valve is also known from DE-A1-196 46 445, in which a valve arrangement is shown, in which two-way valves are included. Each of these directional valves is used for Control of a double-acting consumer. Each of the directional valves is each assigned to a pressure balance.
  • the common pressure balance is in as a hollow slide trained valve spool each way valve placed. By axial movement of the Valve spool in one of the working positions A and B, this pressure compensator is the one or the other of the working connections A, B can be assigned.
  • Directional valves and lifting cylinders Such types are in mobile hydraulics, such as agricultural Devices, applied.
  • the invention has for its object to provide a directional control valve, the simple Structure that allows a cost-effective production, one compared to the state of Technique has improved dynamic behavior. This also ensures that the Directional valve is suitable for different applications and by special Embodiments has a large scope of functions.
  • a differential cylinder is shown, the first Pressure chamber 2 and a second pressure chamber 3, which by a piston. 4 are separated from each other.
  • a plunger 5 is fixed, which controls the movement of the Piston 4 transmits to an unillustrated implement.
  • the differential cylinder 1 is only one possible application example. In its place, for example, too find an oil engine application.
  • the differential cylinder 1 is driven by a directional control valve 10, the is designed according to the invention.
  • the directional control valve 10 th Working ports A and B, wherein the first working port A with the first Pressure chamber 2 and the second working port B to the second pressure chamber 3 of the Differential cylinder 1 is connected.
  • the directional control valve 10 consists of a number of components and is in its construction described below.
  • a releasable Check valve 11 At each of the working ports A and B is a releasable Check valve 11, wherein the lying at the working port A is denoted by 11A, the lying at the work connection B accordingly with 11B.
  • the pilot-operated check valves 11A, 11B can also be omitted.
  • Between one Tank connection T and the working connections A and B are each a secondary pressure limiting and feed valve 12, here analogously 12A and 12B.
  • These secondary pressure relief and feed valves 12A, 12B For example, they act as suction valves. They are required depending on the application when 5 outer forces attack on the plunger whose size and direction can change. They are mentioned here only for the sake of completeness, belong to the prior art of technology, so have no with the realization of the inventive concept Context.
  • Reference numeral 13 denotes a spool which performs the function of Directional valve 10 determines. This spool 13 is controllable, which later will be shown. Between the spool 13 and the unlockable Check valves 11A and 11B and the working ports A and B are each one Pressure compensator 14 is arranged, the assignment to the working ports A and B. are designated respectively 14A and 14B. So since each of the working ports A and B is associated with a separate pressure compensator 14A and 14B, they are called also as individual pressure scales. The pressure compensators 14A and 14B are here so the Pusher piston 13 downstream. This is a prior art often used principle.
  • Fig. 1 shows next to a pump port P, from which the directional control valve 10 is supplied with hydraulic oil.
  • a later-described annular channel of the directional control valve 10 is connected to the spool 13 in a known manner.
  • Shown further is a load-sensing connection LS max which belongs to the prior art in valves of such type and therefore will not be described further here.
  • Pump port P, tank port T and load sensing port LS max are present in Fig. 1 at the right and left edge of the scheme, which is intended to express that the directional control valve 10 is constructed so that a plurality of such valves 10 to a Block are rebar to control multiple consumers. For clarity, the pressures are not shown.
  • At the load-sensing connection LS max there is a pressure p LSmax .
  • the spool 13 is axially displaceable by a drive.
  • the drive should be the Spool 13 from a neutral position corresponding to a neutral position in two Move directions. It is therefore state of the art, two such drives to provide, namely a first drive 15.1, the spool 13 to the right pushes, and a second drive 15.2, which pushes the spool 13 to the left.
  • the Drives 15.1, 15.2 are electrically controllable Propartianalmagnete, which on the Slide piston 13 act.
  • the Actuators 15.1, 15.2 also be solenoid, the only two positions "ON" and Have “OFF”. They press the spool 13 against each one Control spring 16.
  • the action of the pressure compensators 14A, 14B will not be discussed here. because this is known from the prior art. Likewise are not located possibly existing pressure sensors or a differential pressure sensor, the needed to measure the pressure at the working ports A and B, which The prerequisite is that the movement of the piston 4 of the differential cylinder 1 also remains controllable with changing force directions.
  • FIG. 2 a schematic of the arrangement of pressure channels in the directional control valve 10 is shown. It is that part of the directional control valve 10, in which the not shown here Sliding piston 13 (Fig. 1) axially in a slide bore 18 is displaceable.
  • This Scheme shows the arrangement according to the invention symmetrical to a symmetry axis S. of pressure channels and their sequence according to the invention also.
  • the tank connection ring channel 19 is a tank connection channel connection 20 connected to the two end faces of the housing of the Directional valve 10 leads.
  • the channel connection 20 Dashed line because it lies in another plane. It will still be shown that it is thereby possible according to the invention; through this tank connection duct connection 20 to connect the tank connection ring channel 19 with other rooms.
  • This tank connection channel connection 20 does not necessarily have to be with other rooms be connected. There are applications in which, for example, this compound of two end-space annular channels 21, 22 do not exist with the tank connection ring channel 19 should. Therefore, the invention provides that through the tank port channel connection 20, the two end-space annular channels 21, 22 with the tank connection ring channel 19 are connectable. This will be discussed in more detail, as well as that still other connectivity options exist or may exist.
  • the directional control valve 10 in diverse To design variants that make it possible, on the basis of a universal Directional valve 10 a variety of variants for different applications too create. According to the invention, it is therefore provided that the end-space ring channels 21, 22 with other ring channels or other lines are connectable.
  • first tank connection ring channel 19 On both sides of the centrally arranged first tank connection ring channel 19 follow annular channels for the working ports A and B, namely an A-ring channel 23 on the one hand and a B-ring channel 24 on the other side.
  • pump pressure ring channels Located behind it from the center on both sides pump pressure ring channels, on one side a first pump pressure ring channel 25 and on the other side a second pump pressure annular channel 26.
  • This two pump pressure ring channels 25, 26 are according to the invention by means of a Pump pressure channel connection 27 connected to each other and are in communication with the pump port P ( Figure 1).
  • On the pump pressure ring channels 25, 26 follow as Next pair of ring channels a first load-sensing ring channel 28 on the one side and a second load-sensing ring channel 29 on the other side.
  • load-sensing ring channels are known per se, but in the prior art according to DE-A1-32 25 003 unavailable. That according to the invention, these load-sensing ring channels 28, 29th are present, extends the applications of the directional control valve according to the invention in a very significant way.
  • the two load-sensing ring channels 28, 29 are connected according to the invention by a load-sensing connection line 30.
  • the load-sensing connection line 30 is like the tank port channel connection 20 to the both end faces of the housing of the directional control valve 10 out. This serves the possible To provide further advantageous alternative embodiments for different applications the directional valve 10, which will be described.
  • pilot pressure connection line 31 is shown, which is generally present is, but only needed for certain applications.
  • the pilot pressure connection line 31 is like the tank port channel connection 20 and the load sensing connection line 30 to the two end faces of the housing of Directional valve 10 out. This too serves to create variants of the Directional valve 10, namely those that are pilot pressure controlled.
  • the inventive arrangement of the annular channels 21, 28, 25, 23, 19, 24, 26, 29th and 22 in terms of symmetry and succession is achieved on the one hand that for both working connections A and B have equivalent hydraulic conditions, and on the other hand, that the number of control edges in the directional control valve 10 is minimized.
  • the directional control valve 10 of the invention as that of one of Embodiments of DE-A1-32 25 003 seven ring channels 21, 28, 25, 23, 19, 24, 26, 29, but, as mentioned, the load-sensing ring channels 28, 29 contains, at DE-A1-32 25 003 missing. This was achieved according to the invention in that According to the invention, the only tank connection ring channel 19 lies on the axis of symmetry S. and waiver on further tank connection ring channels.
  • the inventive symmetry and arrangement of the annular channels 21, 28, 25, 23, 19, 24, 26, 29 and 22 has the considerable benefit that the directional control valve 10 for very different Use cases can be used, such as different hydraulic drives such For example, single-acting plunger cylinder, double-acting synchronous or Differential cylinder or oil engines. This allows the directional control valve 10 with regard to different applications to be differently equipped, which will be shown becomes.
  • Fig. 3 the same scheme is shown, but now with both sides on the end faces of Housing of the directional valve 10 mounted drives 15.1 and 15.2. It is in both Drives 15.1 and 15.2 each have a recess 32 present in the drive 15.1 thereto serves, the tank connection ring channel 19 via the tank connection channel connection 20 with to connect the first end-space annular channel 21, and in the drive 15.2 according to the Tank connection annular channel 19 via the tank connection channel connection 20 with the second End-space annular channel 22 to connect. It has already been mentioned that this makes sense, the in the spool bore 18 axially movable spool 13 (Fig. 1) hydraulically depressurized to operate. The branches of the load-sensing connection line 30 and the Pilot pressure connection line 31 blindly to the drives 15.1 and 15.2, because they are completed by the housing of the drives 15.1 and 15.2.
  • the spool 13 has a first centrally located first annular groove 33 and two symmetrically to the center lying further annular grooves 34 which communicate with the annular channels 21, 28, 25, 23, 19, 24, 26, 29 and 22 cooperate and so the flow of hydraulic oil enable what is still described.
  • the movement of the spool 13 is effected by the drive 15.1 or 15.2 with the participation of the respective control spring 16. It is significant that the two End faces of the spool 13 are exposed to the same pressure, as already has been mentioned.
  • the drive 15.1 is shown schematically. He has one Magnetic anchor 40 which is movable by a coil, not shown. Of the Magnetic armature 40 acts upon excitation of the coil via a plunger 41 on the one end face of the spool 13. Between the end face of the spool 13 and the Drive 15.1, the control spring 16 is clamped, for example, against a Ring 42 on the housing of the drive 15.1 is supported.
  • the second drive 15.2 shown which contains the same elements as the drive 15.1.
  • the Tank connection channel connection 20 the two end-space annular channels 21, 22 with the Tank connection annular channel 19 connects in the manner as shown in Fig. 3.
  • FIG. 5 shows the spool in his Neutral position, in which the two drives 15.1, 15.2 are not activated, so that the Spool 13 is centrally centered under the action of the two control springs 16.
  • the tank connection ring channel 19 In this position are both the tank connection ring channel 19, the two working connection ring channels, namely, the A-ring channel 23 and the B-ring channel 24, as well as the Pump pressure ring channels 25, 26 shut off, because none of the annular grooves 33, 34 a Establishment of connection between the ring channels. It can be used by and for Differential cylinder 1 no hydraulic oil flow. Consequently, the differential cylinder is 1 quiet.
  • FIG. 6 the representation of FIG. 5 is repeated, but here in a position of Spool 13, in which by excitation of the first drive 15.1 of Sliding piston 13 is shifted to the right.
  • the right of the control springs 16 is below the Effect of the drive 15.1 compressed.
  • this position of the spool 13th Now there is the left of the two annular grooves 34 connection from the A-ring channel 23 to Tank connection annular channel 19 and at the same time on the right of the two annular grooves 34th From the pump pressure ring channel 26 to the B-ring channel 24. It follows that in this Control of the first drive 15.1 hydraulic oil from the pump line P (Fig. 1) via the pump pressure annular channel 26 to the B-ring channel 24 and from there via the Working port B (Fig.
  • the activation of the second drive 15.2 leads to the function "lifting" which, which is not shown separately in a figure, hydraulic oil from the pump port P via the pump pressure ring channel 25 to the A-ring channel 23 and further over the Working port A can flow into the first pressure chamber 2 of the differential cylinder 1, while simultaneously from the second pressure chamber 3 of the differential cylinder.
  • Hydraulic oil via the working port B, the B-ring channel 24 to the tank connection ring channel 19 and from there to the tank connection T can flow.
  • Fig. 7 is a schematic sectional view of a spool 13 with two inside pressure compensator 14 (Fig. 1) shown, as they are in principle from the prior Technics are known.
  • Each of these pressure compensators 14 has a pressure compensating piston 50 on, which is axially displaceable within an axial bore 51 of the spool 13.
  • the position of the pressure balance piston 50 is determined in a known manner by the adjacent pressures and a pressure regulator spring 52, the one hand on Pressure compensator piston 50 and on the other hand supported on a cap 53.
  • These Closure caps 53 are screwed into the spool 13 on both sides and form at the same time the end faces of the spool 13th
  • FIG. 8 shows a hydraulic diagram of a further exemplary embodiment.
  • the drive of the spool 13 in contrast to FIG. 1 is not by two magnetic drives 15.1, 15.2, but by a single hydraulic drive 60th Parts with the same reference numbers correspond to the elements shown in FIG.
  • first quick-switching valve 61A and a second quick-switching valve 61B act as controllable hydraulic resistors, the size of the respective resistor being determined by the clock ratio of the drive, for example by means of pulse-width-modulated signals, ie by the ratio "OPEN to CLOSE” or "OPEN to (OPEN + CLOSED)".
  • a pressure p St is controllable, which is arbitrarily adjustable or variable within the limits of the pressure prevailing at the tank port T and the pilot pressure port P Pilot .
  • This variable pressure p St is used to control the spool 13 because it is supplied to the drive 60 for the spool 13.
  • the spool 13 is also influenced by a drive 60 associated control spring 16 which corresponds functionally to the control spring 16 of the first embodiment (Fig. 1).
  • the directional control valve 10 in this advantageous embodiment is therefore a vor Kunststoffbares directional control valve.
  • Fig. 8 shows next to turn the pump port P, from which the directional control valve 10 is supplied with hydraulic oil.
  • the tank connection annular channel 19 (FIG. 2) of the directional control valve 10 is connected to the control piston 13, analogously to the previous exemplary embodiment.
  • the load-sensing connection LS max Shown further is the load-sensing connection LS max , which, as already mentioned in valves of such kind belongs to the prior art and will therefore not be described further here.
  • Pump port P, tank port T, load sensing port LS max and pilot pressure port P Pilot are also present in Fig. 8 at the right and left edge of the scheme, which in turn is intended to express that the directional control valve 10 is constructed so that a plurality of such valves 10 can be connected to a block in order to control several consumers.
  • the individual directional control valves 10 are of the same basic design according to the general inventive concept of different embodiment, such as one according to FIG. 1, another according to FIG. 8. For the sake of clarity, the pressures are not located. There is a pilot pressure p pilot at the pilot pressure connection P Pilot , a pressure p LSmax at the load-sensing connection LS max and a control pressure p St in the connection line 62.
  • the drive 60 is a drive with a differential cylinder, as will be shown later.
  • the pilot pressure p pilot acts on the one hand, the pilot pressure p pilot , on the other hand, the control pressure p St.
  • the control pressure p St By changing the control pressure p St as a result of the control of the quick-acting valves 61 A, 61 B, the piston of the drive 60 can be moved and this movement is transmitted to the spool 13.
  • FIG. 9 shows a schematic sectional drawing of the directional control valve 10 with the drive 60 attached thereto.
  • the drive 60 consists essentially of a drive piston 70 which is directly connected on the one hand via a piston rod 71 with the spool 13, for example by a screw.
  • the rigid connection of drive piston 70 and spool 13 allows the drive 60 can move the spool 13 from the central neutral position in both directions, so that with a single drive 60 is to get along.
  • a control pressure chamber 72 connects, while on the spool 13 facing side of the drive piston 70, the piston rod 71 enclosing a pilot pressure chamber 73 is arranged.
  • the control pressure p St which can be influenced by the high-speed switching valves 61A, 61B, prevails, while the pilot pressure P pilot prevails in the pilot pressure chamber 73.
  • the tank connection channel connection 20 here connects the tank connection ring channel 19 with the first end room annular channel 21.
  • the possibility provided in the directional control valve 10 that the tank connection ring channel 19 is connected through the tank connection channel connection 20 with the second end-space annular channel 22 is not used here.
  • the spool 13 is hydraulically actuated in a hydraulic drive 60 by acting on the one end face of the spool 13, a hydraulic pressure, so this connection must not exist. Instead, the tank port-channel connection 20 leads into the drive 60 and indeed to the quick-change valve 61B, also already shown in FIG. 8 can be seen, because there is shown that the quick-change valve 61B has a connection to the tank port T.
  • the piston rod 71 is surrounded by the control spring 16 already shown in FIG. 8.
  • This control spring 16 is supported on the one hand via a first ring 75 against the piston 70th or a stage 76 from. On the other hand, it supports itself via a second ring 77 a part of the end face of the spool 13 from. So she is a tied pen.
  • This ring 77 is an opening 78 through which the pilot pressure chamber 73 with the second end-space annular channel 22 is in communication.
  • the movement of the Drive piston 70 and thus of the spool 13 is thus influenced by the Pressures in the control pressure chamber 72 and in the pilot pressure chamber 73 and by the Control spring 16.
  • the control spring 16 stops this the spool 13 in the neutral position shown in FIG. 9, the adequate to the neutral position in the first embodiment (Fig. 5).
  • the control pressure chamber 72 is provided with an insert 81 completed.
  • the plate 80 may have a similar or the same shape as the Insert 81.
  • the already mentioned recess 32 is arranged so that it connects the first end-space annular channel 21 with the tank connection annular channel 20.
  • the drive 60 is a copy in which the effective cross section of the piston 70 in the control pressure chamber 72 is twice as large as the effective cross section in the pilot pressure chamber 73. If the two quick-change valves 61A, 61B so controlled that the pressure in the control pressure chamber 72, which corresponds to the pressure in the connecting line 62, is half the pressure in the pilot pressure chamber 73, which corresponds to the pressure at the pilot pressure port P Pilot , acts on the two sides of the piston 70 of the drive 60, the same force , so that the piston 70 and thus the spool 13 is stationary and is held by the control spring 16 in the neutral position.
  • the drive 60 moves the spool 13 to the right against the force of the control spring 16. If the pressure p St in the connecting line 62 and thus increased in the control pressure chamber 72, which in turn is achieved by appropriate control of the quick-acting valves 61A, 61B, the drive 60 moves the spool 13 to the left.
  • the spool 13 between stops in the in the Fig. 9 shown center position fixed.
  • the attacks are on the one hand around the first ring 75, which is supported against the piston 70 and the stage 76, and on the other hand to the second ring 77, which is located on a part of the end face of the Sliding piston 13 is supported.
  • the rings 75 and 77 together with the biased control spring 16 a quasi-rigid part, which is shown in the here Neutral position with only a few tenths of a millimeter play between the attacks can move through the spool 13 on the one hand and the piston 70 and the Level 76 are given on the other hand.
  • the spool 13 blocks the Connection from pump port P to working ports A and B. This position the spool 13 is the "neutral" position.
  • the directional control valve 10 with the same symmetrical arrangement of the annular channels 21, 28, 25, 23, 19, 24, 26, 29 and 22 both for the equipment with magnetic drives 15.1 and 15.2 (Fig. 5 and 6) as well as for the equipment with a single hydraulic drive 60 used can be.
  • the only necessary variation on the arrangement of the annular channels 21, 28, 25, 23, 19, 24, 26, 29 and 22 is that in one case through the tank port channel connection 20 a connection from the second end-space annular channel 22 to Tank connection ring channel 19 is, in the other case but not. This is the production different variants of directional valves 10 for different applications very economically.
  • FIG. 10 shows a schematic of a further exemplary embodiment. This corresponds largely to that of Fig. 5, but has the following two essential Differences on the spool 13 (Fig. 5) is here divided into two individual Pusher piston, namely a first spool 13.1 and a second Spool 13.2.
  • the second difference from Fig. 3 is that the the Slider piston 13.1, 13.2 associated drives 15.1 and 15.2 (Fig. 5) on the Slide piston 13.1, 13.2 not oppressive act, but pulling. Because of this Significant difference are the drives in FIG. 10 with the reference numbers 15.1 ' or 15.2 '.
  • the neutral position is shown, in which both Drives 15.1 'and 15.2' are not energized.
  • a further embodiment is shown, which largely corresponds to the 10 and 11 corresponds, but instead of the magnetic drives 15.1 'and 15.2' hydraulic drives 60.1 and 60.2, which already shown in FIG. 9 Drive 60 correspond.
  • the split one Spool 13 is present, which is divided into the spool 13.1 and 13.2. Functionally, this embodiment corresponds to that of FIGS. 10 and 11, only with the Difference that in the example of FIG. 12, the movement of the two spool 13.1 and 13.2 is effected by driving the quick-switching valves 61A, 61B, as before is described.
  • Fig. 12 the split one Spool 13 is present, which is divided into the spool 13.1 and 13.2.
  • this embodiment corresponds to that of FIGS. 10 and 11, only with the Difference that in the example of FIG. 12, the movement of the two spool 13.1 and 13.2 is effected by driving the quick-switching valves 61A, 61B, as before is described.
  • the spool 13.2 shown on the right is through by corresponding activation of the quick-acting valves 61A, 61B shifted to the right, whereby the control spring 16 contained in the drive 60.2 is compressed, ie whose spring force determines the position of the spool 13.2.
  • the quick-change valves 61A, 61B both Actuators 60.1, 60.2 in a very advantageous manner to achieve the floating position, without that it requires additional resources.
  • FIG. 13 corresponds in principle to Fig. 8, but has instead of the single Spool 13 with the hydraulic actuator 60 that actuates these two separate spool 13.1 and 13.2 with the associated drives 60.1 and 60.2 on.
  • the quick-change valves 61 are present in double number, namely on the one hand, the quick-change valves 61.1A and 61.1B, the drive 60.1 are assigned, and the quick-change valves 61.2A and 61.2B, the drive to 60.2 belong.
  • FIG. 8 In which the control pressure p St for controlling the drive 60 prevails, two connecting lines 62.1 and 62.2 are shown in FIG. In the connecting line 62.1 prevails a control pressure p St1 , which causes the control of the drive 60.1. Analogously, there is a control pressure p St2 in the connecting line 62.2 , which causes the control of the drive 60.2.
  • FIG. 13 Another hydraulic scheme is shown in FIG. This corresponds largely the Fig. 13, but instead of the differential cylinder 1 are two from each other independent hydraulic consumers, namely a first consumer 100A and a second consumer 100B available.
  • the first consumer 100A is at first Working port A of the directional control valve 10 connected to the second consumer 100B the second working port B.
  • split Spool 13 the two spool 13.1 and 13.2 independently are controllable, it is therefore possible with a directional control valve 10 in the in Fig. 12 shown type two hydraulic consumers 100A, 100B independently operate.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Servomotors (AREA)
  • Magnetically Actuated Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Temperature-Responsive Valves (AREA)

Claims (8)

  1. Distributeur (10) pour commander la pression et le débit d'huile hydraulique de et vers des raccords de travail (A, B) d'au moins un consommateur (1 ; 100A, 100B), dans lequel la pression et le débit peuvent être commandés au moyen d'un piston de tiroir (13) pouvant être déplacé dans un alésage de tiroir (18) par au moins un entraínement (15 ; 15.1, 15.2 ; 15.1', 15.2' ; 60 ; 60.1, 60.2) et de canaux annulaires (19, 21, 22, 23, 24, 25, 26, 28, 29) en interaction avec celui-ci, un canal annulaire de raccord de réservoir (19) étant disposé au centre de symétrie sur un axe de symétrie (S) et d'autres canaux annulaires (21, 22, 23, 24, 25, 26, 28, 29) étant disposés symétriquement de chaque côté, caractérisé par le fait
    que de chaque côté du canal annulaire de raccord de réservoir (19) sont disposés l'un derrière l'autre en s'éloignant de l'axe de symétrie (S)
    - d'un côté de l'axe de symétrie (S) un canal annulaire A (23) associé au raccord de travail (A), un premier canal annulaire de pression de pompe (25), un premier canal annulaire de détection de charge (28) et un premier canal annulaire de chambre d'extrémité (21), et
    - de l'autre côté de l'axe de symétrie (S) un canal annulaire B (24) associé à l'autre raccord de travail (B), un deuxième canal annulaire de pression de pompe (26), un deuxième canal annulaire de détection de charge (29) et un deuxième canal annulaire de chambre d'extrémité (22), et
    que le premier canal annulaire de chambre d'extrémité (21) et le deuxième canal annulaire de chambre d'extrémité (22) peuvent être mis en communication avec d'autres canaux annulaires (19 ; 28, 29) ou d'autres conduits (20 ; 27 ; 30 ; 31),
    que le premier canal annulaire de pression de pompe (25) est en communication avec le deuxième canal annulaire de pression de pompe (26) par l'intermédiaire d'un canal de liaison de pression de pompe (27) et
    que le premier canal annulaire de détection de charge (28) est en communication avec le deuxième canal annulaire de détection de charge (29) par l'intermédiaire d'un conduit de liaison de détection de charge (30).
  2. Distributeur selon la revendication 1, caractérisé par le fait que le canal annulaire de raccord de réservoir (19) est en communication avec le premier canal annulaire de chambre d'extrémité (21) et le deuxième canal annulaire de chambre d'extrémité (22) par l'intermédiaire du canal de liaison de raccord de réservoir (20) et que l'entraínement (15) est constitué d'un premier entraínement magnétique pouvant être commandé électriquement (15.1) et d'un deuxième entraínement magnétique pouvant être commandé électriquement (15.2) qui sont disposés de chaque côté du piston de tiroir (13) et agissent sur ses faces frontales contre des ressorts de commande (16).
  3. Distributeur selon la revendication 1, caractérisé par le fait que le premier canal annulaire de chambre d'extrémité (21) et le deuxième canal annulaire de chambre d'extrémité (22) sont en communication avec le conduit de liaison de détection de charge (30) et que l'entraínement (15) est constitué d'un premier entraínement magnétique pouvant être commandé électriquement (15.1) et d'un deuxième entraínement magnétique pouvant être commandé électriquement (15.2) qui sont disposés de chaque côté du piston de tiroir (13) et agissent sur ses faces frontales contre des ressorts de commande (16).
  4. Distributeur selon la revendication 1, caractérisé par le fait que le premier canal annulaire de chambre d'extrémité (21) et le deuxième canal annulaire de chambre d'extrémité (22) sont en communication avec le premier canal annulaire de pression de pompe (25) et avec le deuxième canal annulaire de pression de pompe (26) par l'intermédiaire du canal de liaison de pression de pompe (27) et que l'entraínement (15) est constitué d'un premier entraínement magnétique pouvant être commandé électriquement (15.1) et d'un deuxième entraínement magnétique pouvant être commandé électriquement (15.2) qui sont disposés de chaque côté du piston de tiroir (13) et agissent sur ses faces frontales contre des ressorts de commande (16).
  5. Distributeur selon l'une des revendications 2 à 4, caractérisé par le fait que les liaisons avec le premier canal annulaire de chambre d'extrémité (21) et le deuxième canal annulaire de chambre d'extrémité (22) sont réalisées au moyen d'évidements ou de cavités (32) dans les faces frontales des entraínements magnétiques pouvant être commandés électriquement (15.1, 15.2).
  6. Distributeur selon la revendication 1, caractérisé par le fait que le canal annulaire de raccord de réservoir (19) est en communication avec le premier canal annulaire de chambre d'extrémité (21) par l'intermédiaire du canal de liaison de raccord de réservoir (20), que le deuxième canal annulaire de chambre d'extrémité (22) est en communication avec un conduit de pression pilote (31) et que l'entraínement (60) est un entraínement hydraulique muni d'un piston différentiel.
  7. Distributeur selon les revendications 2 et 5, caractérisé par le fait que le piston de tiroir (13) est divisé en un premier piston de tiroir (13.1) et un deuxième piston de tiroir (13.2) qui sont reliés chacun à un entraínement magnétique pouvant être commandé électriquement (15.1', 15.2') de façon que les entraínements magnétiques (15.1', 15.2') agissent sur les pistons de tiroir (13.1, 13.2) par traction.
  8. Distributeur selon les revendications 1 et 6, caractérisé par le fait que le piston de tiroir (13) est divisé en un premier piston de tiroir (13.1) et un deuxième piston de tiroir (13.2) qui sont reliés chacun de façon rigide à un piston d'entraínement (70) de l'entraínement pouvant être commandé hydrauliquement (60.1, 60.2).
EP02702621A 2001-03-21 2002-03-04 Distributeur Expired - Lifetime EP1370773B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH5222001 2001-03-21
CH522012001 2001-03-21
PCT/IB2002/000661 WO2002075162A1 (fr) 2001-03-21 2002-03-04 Distributeur

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EP1370773B1 true EP1370773B1 (fr) 2005-06-22

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EP (1) EP1370773B1 (fr)
AT (1) ATE298395T1 (fr)
DE (1) DE50203452D1 (fr)
WO (1) WO2002075162A1 (fr)

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DE102007054134A1 (de) 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
WO2009062572A1 (fr) 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Vanne hydraulique
DE102008006879A1 (de) 2008-01-31 2009-08-06 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
WO2012065692A1 (fr) 2010-11-17 2012-05-24 Hydac Filtertechnik Gmbh Dispositif à soupape hydraulique

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DE102005029821A1 (de) * 2005-04-04 2006-10-05 Bosch Rexroth Ag Wegeventil und damit ausgeführte LS-Steueranordnung
DE102005022891A1 (de) 2005-04-05 2006-10-12 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung und Steuerblock
EP2036679B1 (fr) * 2007-09-11 2012-07-11 Uryu Seisaku Ltd. Dispositif de réglage de couple d'impact d'une clé dynamométrique hydraulique
US8021873B2 (en) * 2008-07-16 2011-09-20 Boston Microfluidics Portable, point-of-care, user-initiated fluidic assay methods and systems
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WO2009062572A1 (fr) 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Vanne hydraulique
WO2009062564A1 (fr) 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Mécanisme hydraulique à soupape
DE102007054137A1 (de) 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
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US8479769B2 (en) 2007-11-14 2013-07-09 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102008006879A1 (de) 2008-01-31 2009-08-06 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
WO2012065692A1 (fr) 2010-11-17 2012-05-24 Hydac Filtertechnik Gmbh Dispositif à soupape hydraulique
DE102010051690A1 (de) 2010-11-17 2012-05-24 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung

Also Published As

Publication number Publication date
ATE298395T1 (de) 2005-07-15
DE50203452D1 (de) 2005-07-28
US7100639B2 (en) 2006-09-05
US20040079425A1 (en) 2004-04-29
EP1370773A1 (fr) 2003-12-17
WO2002075162A1 (fr) 2002-09-26

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