EP0198119B1 - Distributeur hydraulique pour commande indépendamment de la charge - Google Patents

Distributeur hydraulique pour commande indépendamment de la charge Download PDF

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Publication number
EP0198119B1
EP0198119B1 EP19850115457 EP85115457A EP0198119B1 EP 0198119 B1 EP0198119 B1 EP 0198119B1 EP 19850115457 EP19850115457 EP 19850115457 EP 85115457 A EP85115457 A EP 85115457A EP 0198119 B1 EP0198119 B1 EP 0198119B1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
valve
chamber
measuring
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
EP19850115457
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German (de)
English (en)
Other versions
EP0198119A2 (fr
EP0198119A3 (en
Inventor
Heinz Flaschar
Wolfgang Dipl.-Ing. Kötter
Gottfried Dipl.-Ing. Olbrich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0198119A2 publication Critical patent/EP0198119A2/fr
Publication of EP0198119A3 publication Critical patent/EP0198119A3/de
Application granted granted Critical
Publication of EP0198119B1 publication Critical patent/EP0198119B1/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

Definitions

  • the invention is based on a hydraulic directional valve for a load pressure-compensated control according to the preamble of claim 1.
  • Such a directional control valve is already known from DE-A-3309 998, in which a control slide forms a measuring throttle point between two measuring throttle chambers. Downstream of this measuring throttle point and still upstream from a check valve protecting an inlet chamber, the respective load pressure is tapped for a load pressure-compensated control.
  • This load pressure sensing directional valve is also designed for a closed circuit system. Above all, this directional control valve is equipped with a return lead, in which the control edge on the control spool, which relieves the hydraulic motor to the tank, opens its connection earlier before the measuring throttle point on the inflow side opens.
  • a directional control valve with return flow is only suitable for controlling hydraulic motors under braking load conditions. Such control edge overlaps are not suitable for driving load conditions.
  • such a directional control valve leads to a current-free control system, in which the volume flow set at the measuring throttle point is pressed to the motor side and leads to undesirable pressure surges which prevent smooth control, particularly when large loads are actuated.
  • a hydraulic directional control valve for a load pressure-compensated control is known from US-A-3 722 543, in particular FIG. 7, in which a control slide forms a measuring throttle point, in the area of which the respective load pressure is tapped.
  • This load pressure sensing directional valve is also designed for a closed circuit system and has an associated pressure compensating piston for each spool. While the load pressure for a common pressure compensation valve located in the connecting plate is tapped from an upstream measuring throttle chamber, the downstream measuring throttle chamber is relieved via a control connection of the control slide open to the tank in the neutral position.
  • a hydraulic directional control valve for a load pressure-compensated control and in a training for a closed system is known.
  • this directional control valve the sagging of a load due to backflow of control pressure medium via a measuring line is to be prevented, for which purpose the pressure of the adjustable pump is raised by a predetermined amount above the respective load pressure when the control slide is deflected from its neutral position into a raised position.
  • This directional control valve which has a three-chamber measuring throttle point in the center of the housing, is equipped with a return lead and is therefore only suitable for controlling hydraulic motors under braking load conditions.
  • the control pressure measuring line is continuously relieved to the tank via a throttling point.
  • control oil flow flowing to the tank the size of which depends on the size of the respective load.
  • the control oil flow in turn influences the working current flowing to the hydraulic motor, so that a load pressure-compensated control, in particular in the area of fine control, is adversely affected.
  • the directional control valve according to the invention with the characterizing features of claim 1 has the advantage that it is particularly suitable for a load pressure-compensated control in a closed circuit system under driving load conditions on the hydraulic motor. While load pressure-compensated directional control valves for a closed circuit lead to a relatively rigid system due to their rigid flow control, pressure control can be achieved with the directional control valve according to the invention, as is possible with open circuit directional control valves and is therefore softer working system can be achieved. This advantage can be achieved both over a portion of the spool stroke and over the entire stroke. Despite the inlet advance, pressure increases up to the maximum value set on the pressure relief valve are avoided. In addition, the design according to the invention can be implemented in a simple, inexpensive and space-saving manner.
  • FIG. 1 shows a hydraulic control device 10 in the form of a stacker valve which has a first directional valve 11 for a lifting function, a second directional valve 12 according to the invention for a tilting function and a third directional valve 13 for an additional function.
  • the directional control valves 11, 12, 13 are designed in a closed circuit design and are also suitable for load pressure-compensated control.
  • all directional valves 11 to 13 are connected in parallel to an inlet line 14 which starts from an inlet 15 in a connecting plate 16.
  • all directional valves 11 to 13 are connected to a return line 17, which leads to an outlet 18 in the connection plate 16.
  • a pressure compensation valve 19 is connected between the inlet 15 and the outlet 18, which valve 22 has shuttle valves 22 via a control line system 21 can be controlled with the maximum load pressure of one of the directional control valves 11 to 13.
  • a pilot-controlling pressure relief valve 23 in the control line system 21 works together with the pressure compensation valve 19.
  • the second directional control valve 12 according to FIG. 1 is shown in a constructive form in longitudinal section in FIG.
  • the second directional valve 12 has a housing 24 which receives a control slide 26 in a continuous longitudinal bore 25.
  • the longitudinal bore 25 penetrates a series of chambers which, in a manner known per se, seen from right to left as the first (27) and second measuring throttle chamber 28, as the first return chamber 29, as the first motor chamber 31, as the inlet chamber 32, as the second motor chamber 33 and as a second return chamber 34 are formed.
  • the first measuring throttle chamber 27 is connected to the inlet line 14.
  • a transverse channel 35 leads from the second measuring throttle chamber 28 to the inlet chamber 32.
  • a control pressure tap opening 37 connected to the control line system 21 and a check valve 38 securing the inlet chamber 32 are arranged one behind the other in the flow direction.
  • First control recesses 41 which form parts of a so-called measuring throttle point 42, are arranged on a control collar 39 lying in the drawn neutral position of the control slide 26 between the two measuring throttle chambers 27, 28.
  • Bypass throttles 45 are formed on a second control collar 43 adjoining the first control collar 39 and a subsequent third control collar 44, which are used to control the connection between the second measuring throttle chamber 28 and the first return chamber 29. Furthermore, the third Control collar 44 also has an outlet-side, first throttle recess 46. To control the connections between the inlet chamber 32 and the two motor chambers 31 and 33, two control notches 48 are arranged on a fourth control collar 47 of the control slide 26. A piston section 51 on the control slide 26 facing a double-acting return device 49 has on its control edge a second, throttle recess 52 on the outlet side.
  • control slide 26 first opens the pressure medium connection in the measuring throttle point 42 when deflecting from its drawn neutral position in working positions with its first control recesses 41 and only then open the discharge throttle recesses 52 and 46 on the discharge to the tank. This ensures that, under driving load conditions, the load is guided in the directional control valve 12 by throttling on the outlet side. This fact must also exist in the case of an unfavorable tolerance position of the control edges for the start of the inflow or outflow, in particular it must also be ensured in the fine control area.
  • the first motor chamber 31 is connected via a first shut-off valve 53 to a first motor connection 54 and further to a cylinder space 55 of a tilt cylinder 56.
  • a piston rod chamber 57 on the tilt cylinder 56 has a connection to the second motor chamber 33 via a second motor connection 58 and a second shut-off valve 59.
  • Both check valves 53, 59 are designed as pilot-operated valves and can be unlocked hydraulically by an unlocking piston 61 lying coaxially to them.
  • the piston rod must extend in the tilt cylinder 56.
  • the stroke direction according to arrow s and the force on the piston rod of the tilt cylinder 56 according to arrow F thus point in the same direction; at the tilt cylinder 56 there are driving load conditions.
  • the control slide 26 is pressed somewhat into the housing 24.
  • the first control recesses 41 open the measuring throttle point 42, so that, due to the load-compensating control device 10, an oil flow coming from the pressure medium source flows via the inlet line 14 and the opened measuring throttle point 42 into the second measuring throttle chamber 28.
  • the pressure in the second measuring throttle chamber 28 can build up via the transverse channel 35, the check valve 38, the control notch 48, which is likewise opened, also in the first motor chamber 31 and further via the check valve 53 and the first motor connection 54 in the cylinder space of the tilt cylinder 56.
  • the pressure in the transverse channel 35 acts via the control pressure tap opening 37 and the control line system 21 also on the end of the pressure compensation valve 19 loaded by a spring.
  • the second measuring throttle chamber 28 to the second return chamber is via the bypass throttle 45 which is currently active 29 relieved.
  • the entire oil flow metered via the measuring throttle point 42 flows out via the open bypass throttle 45 to the second return chamber 29; the cross-section of the bypass throttle 45, which is in each case controlled, thus allows the pressure in the second measuring throttle chamber 28 and accordingly the pump pressure to be determined.
  • the first control recesses 41 and the bypass throttles 45 are correspondingly coordinated with one another and also work together in opposite directions. If the control slide 26 is pushed further towards the forward tilt position, the second throttle recess 52 finally opens the connection from the second motor chamber 32 to the second return chamber 34. When the throttle 52 on the outlet side is activated, a partial oil flow can now flow via the tilt cylinder 56.
  • the pilot-operated shut-off valve 59 has been opened gently by the unlocking piston 61, on its end side facing the first engine chamber 31 the intermediate pressure accumulated in the second measuring throttle chamber 28 works. If the control slide 26 is pressed further towards the forward tilt position, the bypass throttle 45 closes its associated tank connection completely from a certain stroke and the entire oil flow metered via the measuring throttle point 42 flows to the tilt cylinder 56. The adjustable bypass throttle 45 is thus switched off , as can also be seen from the circuit symbol of the directional control valve 12 in FIG. 1.
  • FIG. 3 shows the course of the pressure p over the slide stroke s
  • FIG. 4 shows the current Q flowing through the measuring throttle point 42 as a function of the slide stroke s.
  • p1 indicates the maximum pressure value set on the pressure relief valve 23.
  • the solid characteristic curve 62 illustrates the course of the pump pressure in the event that no bypass throttles 45 are provided, as a result of which the pump pressure in the area of the inlet lead 63 rises to the maximum value p1, and only drops to a pressure level p2 again after the inlet lead has been overridden that occurs with normal load pressure compensated control.
  • the dashed curve 64 shows the course of the pump pressure in the directional control valve 12 according to the invention with existing bypass throttles 45. It can be seen from the curve 64 that relatively long pressure peaks with an appealing pressure relief valve are avoided and the pump pressure increases with increasing stroke s without sudden changes starting from Pressure zero rises relatively evenly up to pressure level p2.
  • the associated current profile is shown in FIG. 4, the pressure medium flow via the measuring throttle point 42 constantly increasing as a function of the stroke of the control slide 26 to a maximum current Q1.
  • the control edge inlet advance in the directional control valve 12 is no longer necessary when tilting back due to the load conditions, but is intended to enable a soft opening of the check valves 53, 59 and thus a smooth control.
  • the control slide 26 is pulled out of the drawn neutral position according to FIG. 2 from the housing 24.
  • the first control recesses 41 in the measuring throttle point 42 and the bypass throttles 45 cooperate in a corresponding manner for pressure control.
  • the bypass throttle 45 can also be switched off after a predetermined stroke, as can be seen in FIG. 1 from the switching symbol of the directional valve 12.
  • the course of the pump pressure when tilting back with the directional control valve 12 is shown in more detail in FIG. 5, the pressures p1 and p2 being given in a corresponding manner as in FIG. 3.
  • the solid characteristic curve 65 in turn shows the pressure curve of the pump pressure in the event that there are no bypass throttles. This results in a sudden, strong pressure increase in the area of the inlet advance, the size of which strongly depends on the actuation speed of the control slide in the directional control valve.
  • the dashed curve 66 shows the course of the pump pressure in the control device 12 according to the invention with existing bypass throttles 45. In spite of the inlet advance, a much flatter pressure rise and a lower pressure increase is achieved before the pump pressure drops to the load pressure level p2. The function of reclining is therefore considerably softer according to characteristic curve 66.
  • the directional control valve 12 can thus be used in a control device for a closed circuit and with load pressure compensation Mode of operation, even under driving load conditions, achieve properties that can only be achieved with control devices for open circuits and with pressure control. Instead of a rigid system with primary flow control, a soft system with pressure control is achieved. This is particularly favored in the directional control valve 12 in that the measuring throttle point 42, the bypass throttles 45 and also the control pressure tap opening 37 are all upstream of the check valve 38. The function of the bypass throttles 45 can be effective over part or over the entire stroke of the control slide 26.
  • FIG. 6 shows as a second embodiment of a directional control valve according to the invention a partial longitudinal section through a fourth directional control valve 70.
  • the fourth directional control valve 70 differs from the second directional control valve 12 according to FIG. 2 as follows, the same reference numerals being used for the same components.
  • the bypass throttles 45 on the control slide 71 are omitted.
  • the control slide 71 takes a secondary pressure relief valve 72 in its place, which secures the first motor chamber 31. With the help of the secondary pressure relief valve 72, the problem of pressure reduction can be solved in the control edge area of the inlet lead. A course of the pump pressure can thereby be achieved, as is shown in FIG. 3 with the dash-dotted characteristic curve 73.
  • FIG. 7 shows part of a fifth directional control valve 75 according to the invention, in which the function of secondary pressure relief valves is integrated in the unlocking piston 76.
  • the print function is effective for both motor connections 54 and 58.
  • the relief of the secondary pressure relief valves takes place here to a return channel 78 between the motor chambers 31 and 33.
  • control spool can only be equipped with an advance lead in one direction of movement and a return lead in the other direction. It is also possible to achieve the inlet advance using the check valves.
  • the subject of the invention can also be applied to directional valves with a hollow slide, in which case the return chamber no longer has to lie directly next to the second measuring throttle chamber 28, as shown in FIG. 2.

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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 (8)

  1. Distributeur hydraulique (12) pour une commande (10) indépendamment de la charge, avec un carter (24) dans l'alésage longitudinal (25) duquel est disposé un tiroir de commande (26) qui comporte un premier évidement de commande (41) afin de constituer au moins un point d'étranglement de mesure (42), qui est branché sur le courant de fluide sous pression s'écoulant de la pompe vers le moteur (56), tandis que ce point d'étranglement de mesure (42) comporte une première chambre d'étranglement de mesure (27) reliée à une canalisation d'amenée (14) ainsi qu'une seconde chambre d'étranglement de mesure (28) placée en aval, chambres dont la communication réciproque est commandée par le premier évidement de commande (41), et avec une chambre d'amenée (32) qui est susceptible d'être reliée au choix avec un des deux raccordements de moteur (54, 58) dans deux positions de fonctionnement du tiroir de commande (26), tandis que l'autre raccordement de moteur est susceptible d'être déchargé par l'intermédiaire d'un évidement d'étranglement (52) vers le retour (18), et cette chambre d'amenée (32) est en communication avec la seconde chambre d'étranglement de mesure (28), et avec une chambre de retour (29) qui, dans la position neutre du tiroir de commande (26) est en communication avec la seconde chambre d'étranglement de mesure (28) et qui est susceptible d'être bloquée dans les positions de fonctionnement par des arêtes de commande correspondantes du tiroir de commande (26), et avec un orifice de prélèvement (37) de la pression de commande pour la commande indépendamment de la charge placée au voisinage du point d'étranglement de mesure (42) en aval de celui-ci, distributeur hydraulique caractérisé en ce que le tiroir de commande (26; 71) est réalisé avec une avance à l'amenés, pour laquelle le point d'étranglement de mesure (42) côté amenée, s'ouvre avant que s'ouvre l'évidement d'étranglement (52) correspondant côté évacuation sur le tiroir de commande (26; 71), et en ce que la décharge de l'orifice de prélèvement (37) de la pression de commande vers le réservoir (18) est susceptible d'être effectuée par l'intermédiaire de moyens de commande de la pression (45; 72; 77) susceptibles d'être activés par le tiroir de commande (26; 71).
  2. Distributeur selon la revendication 1, caractérisé en ce que les moyens de commande de la pression sont réalisés sous la forme d'étranglements à deux dérivations (45) qui, pour permettre la liaison avec étranglement entre la seconde chambre d'étranglement de mesure (28) et la chambre de retour (29) notamment adjacente, sur un trajet de déplacement prédéfini du tiroir de commande (26), sont disposés sur les épaulements de commande (43, 44) de façon qu'ils fonctionnent en sens inverse par rapport aux évidements de commande (41) du point d'étranglement de mesure (42).
  3. Distributeur selon la revendication 2, caractérisé en ce que les étranglements à deux dérivations (45) sont opérationnels dans la zone de commande de l'avance à l'amenée et notamment sont encore partiellement ouverts.
  4. Distributeur selon une des revendications 1 à 3, caractérisé en ce que l'orifice de prélèvement (37) de la pression de commande est placé en amont de la chambre d'amenée (32).
  5. Distributeur selon une ou plusieurs des revendications 2 à 4, caractérisé en ce que le point d'étranglement de mesure (42), les étranglements à deux dérivations (45) et les orifices de prélèvement (37) de la pression de commande, sons placés en amont d'une soupape anti-retour (38) protégeant la chambre d'amenée (32).
  6. Distributeur selon la revendication 1, caractérisé en ce que les moyens de commande de la pression, sont réalisés sous la forme d'une soupape de limitation de la pression secondaire (72) qui protège une chambre de travail associée (31) (figure 6).
  7. Distributeur selon la revendication 6, caractérisé en ce que la soupape de limitation de la pression secondaire (72) est disposée dans le tiroir de commande (71).
  8. Distributeur selon la revendication 6, avec une soupape d'arrêt branchée entre deux raccordements de moteur et deux chambres de travail, avec un piston de déverrouillage (76) associé, distributeur caractérisé en ce que le piston de déverrouillage (76) reçoit au moins une soupape de limitation de la pression secondaire (77) (figure 7).
EP19850115457 1985-02-19 1985-12-05 Distributeur hydraulique pour commande indépendamment de la charge Expired - Lifetime EP0198119B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853505623 DE3505623A1 (de) 1985-02-19 1985-02-19 Hydraulisches wegeventil fuer eine lastdruckkompensierte steuerung
DE3505623 1985-02-19

Publications (3)

Publication Number Publication Date
EP0198119A2 EP0198119A2 (fr) 1986-10-22
EP0198119A3 EP0198119A3 (en) 1989-04-26
EP0198119B1 true EP0198119B1 (fr) 1991-08-07

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EP19850115457 Expired - Lifetime EP0198119B1 (fr) 1985-02-19 1985-12-05 Distributeur hydraulique pour commande indépendamment de la charge

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EP (1) EP0198119B1 (fr)
DE (2) DE3505623A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003091576A1 (fr) * 2002-04-26 2003-11-06 Bosch Rexroth Ag Ensemble distributeur ls

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3640640C2 (de) * 1986-11-28 1999-07-22 Linde Ag Hydrostatisches Antriebssystem mit einem Verbraucher mit zwei Anschlüssen
DE3833999A1 (de) * 1988-10-06 1990-04-12 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE4223389C2 (de) * 1992-07-16 2001-01-04 Mannesmann Rexroth Ag Steueranordnung für mindestens einen hydraulischen Verbraucher
DE4234034A1 (de) * 1992-10-09 1994-04-14 Rexroth Mannesmann Gmbh Wegeventil zur Ansteuerung eines hydraulischen Verbrauchers insbesondere eines mobilen Arbeitsgerätes
DE4234035A1 (de) * 1992-10-09 1994-04-14 Rexroth Mannesmann Gmbh Wegeventil zur Ansteuerung eines hydraulischen Verbrauchers insbesondere eines mobilen Arbeitsgerätes
FR2815385B1 (fr) * 2000-10-13 2003-01-17 Mannesmann Rexroth Sa Circuit hydraulique autorisant un deplacement d'un recepteur a vitesse tres lente et distributeur hydraulique agence a cet effet
DE102015122915A1 (de) * 2015-12-29 2017-06-29 Xcmg European Research Center Gmbh Hydraulische Steuerung
IT201900015363A1 (it) * 2019-09-02 2021-03-02 Cnh Ind Italia Spa Valvola direzionale per un veicolo da lavoro e relativa disposizione idraulica

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3722543A (en) * 1971-11-02 1973-03-27 Hydraulic Industries Pressure compensated control valve
DE2723279A1 (de) * 1976-05-26 1977-12-08 Cessna Aircraft Co Hydraulisches steuerventil

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3602104A (en) * 1969-07-08 1971-08-31 Eaton Yale & Towne Pressure-compensated flow control
US4145958A (en) * 1977-12-02 1979-03-27 Borg-Warner Corporation Fluid control system with automatically actuated motor port lock-out valves
DE2804045A1 (de) * 1978-01-31 1979-08-09 Bosch Gmbh Robert Steuervorrichtung fuer einen hydraulisch betriebenen verbraucher
DE3309998C2 (de) * 1983-03-19 1996-06-13 Bosch Gmbh Robert Hydraulische Einrichtung zur Auswahl und Weiterleitung eines Drucksignals in einem Blockwegeventil

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3722543A (en) * 1971-11-02 1973-03-27 Hydraulic Industries Pressure compensated control valve
DE2723279A1 (de) * 1976-05-26 1977-12-08 Cessna Aircraft Co Hydraulisches steuerventil

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003091576A1 (fr) * 2002-04-26 2003-11-06 Bosch Rexroth Ag Ensemble distributeur ls

Also Published As

Publication number Publication date
DE3583743D1 (de) 1991-09-12
DE3505623A1 (de) 1986-08-21
EP0198119A2 (fr) 1986-10-22
EP0198119A3 (en) 1989-04-26

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