EP0051728B1 - Hydraulic motor control system - Google Patents

Hydraulic motor control system Download PDF

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Publication number
EP0051728B1
EP0051728B1 EP81107401A EP81107401A EP0051728B1 EP 0051728 B1 EP0051728 B1 EP 0051728B1 EP 81107401 A EP81107401 A EP 81107401A EP 81107401 A EP81107401 A EP 81107401A EP 0051728 B1 EP0051728 B1 EP 0051728B1
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EP
European Patent Office
Prior art keywords
valve
bore
control valve
shut
piston
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Expired
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EP81107401A
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German (de)
French (fr)
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EP0051728A1 (en
Inventor
Heinz Ing.Grad. Siegel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0051728A1 publication Critical patent/EP0051728A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve

Definitions

  • the invention is based on a control device for a hydraulic working cylinder according to the preamble of claim 1.
  • the drain control valve has a cylindrical shaft which is slidably guided in the shut-off valve body and has a longitudinal groove with a conical section, via which groove the pressure medium is throttled flows from the cylinder to the container.
  • a cylindrical extension which projects in a damping space, can be formed on the sequence control valve. The opening movement of the sequence control valve is damped, which leads to a jerk-free lowering of the load.
  • This known device is relatively simple, but should have the disadvantage that the damping of the control valve and the outflow of the pressure medium from the working cylinder are not yet optimal due to the very simple construction (DE-A-2 214 245).
  • the object of the invention is to provide a device according to the preamble of claim 1, which allows a particularly good damping of the sequence control valve and a particularly good jerk-free lowering of the consumer with a reasonable amount of construction.
  • FIG. 1 shows a hydraulic control device with a lowering brake blocking valve in longitudinal section
  • FIG. 2 shows a modification of the exemplary embodiment according to FIG. 1.
  • a pump 10 draws in pressure medium from a container 11, which is fed via a 4 / 3- way valve to a consumer 13 - here a double-acting working cylinder - directly or via a hydraulically unlockable check valve 14 serving as a lowering brake valve.
  • the working cylinder 13 has two pressure chambers 15, 16, in which a piston 17 with a piston rod 18 is guided.
  • a line 19 leads directly to the pressure chamber 15 and a line 20 leads to a bore 21 in the housing 22 of the check valve 14.
  • a line 24 branches off from the line 19 and leads to a second bore 25 in the housing 22.
  • a longitudinal bore 26 is formed, in one section of which an unlocking piston 27 is guided in a tightly sliding manner.
  • the bore 21 opens into the longitudinal bore 26.
  • a valve member 30 serving as a check valve body, which rests with a conical collar 31 on a likewise conical valve seat 32, which part of the bore section 26' is.
  • the valve member 30 has a stepped bore 33, which essentially consists of three bore sections 34 to 36 of decreasing diameter.
  • An annular groove 38 is formed on the valve member 30, from which a plurality of radial bores 39 lead into the bore section 35.
  • the radial bores 39 are connected to a transverse bore 40 in the housing 22, from which a line 41 leads to the pressure chamber 16 of the working cylinder 13.
  • the opening of the transverse bore 40 in the bore section 26 ' lies directly next to the valve seat 32.
  • the bore section 26' forms a damping space 42 and is closed by a screw plug 43.
  • One end of a compression spring 44 bears against its inner end, the other end of which plunges into a central blind bore 45 of a control valve 46.
  • the control valve 46 is guided with its rear valve part 47 tightly sliding in the bore section 34 of the valve member 30.
  • a cylindrical valve part 48 with a much smaller diameter adjoins the cylindrical valve part 47 and projects into the bore section 35.
  • the valve part 48 has a conical collar 49, with which it is pressed by the force of the spring 44 onto a valve seat 50, which is formed by the shoulder of the two bore sections 35 and 36.
  • An annular groove 52 adjoins the conical collar 49, followed by a fine control pin 53 as the third valve part.
  • the fine control pin 53 is guided with a narrow cylindrical section 53 'in the bore section 36.
  • the fine control pin 53 is followed by a fourth and last valve part, which is an impact tappet 54, which reaches close to the locking piston 27 when it reaches its one end position.
  • a short blind bore 56 with a substantially smaller diameter follows from the blind bore 45 receiving the spring 44, from which a plurality of transverse bores 57 lead to the outside.
  • a throttle notch 58 which leads up to the shoulder formed by the valve parts 47, 48. This is always at a certain distance from the shoulder formed from the bore sections 34, 35. In this area, the bore section 34 is expanded to a bore section 34 '.
  • the directional control valve can assume three switch positions 1, II and 111. If it is brought from its neutral position II into the switching position I, pressure medium flows via the line 20 to the bore 21, and the valve member 30 is lifted together with the control valve 46 against the force of the spring 44 from its valve seat 32, so that pressure medium through the bore 40 and line 41 can penetrate into the pressure chamber 16 of the working cylinder 13.
  • the control valve remains in its position, ie the conical collar 49 remains on the valve seat 50.
  • the valve member 30 thus only has the function of a check valve. By pressurizing the pressure chamber 16, the piston 17 is opposed ner load extended, pressure medium is discharged from the pressure chamber 15 via the line 19 to the container 11.
  • the directional valve 12 is brought into its switching position 111. It is important that this process must be carried out silently, smoothly and in such a way that the load does not lead ahead of the pressure medium flow now entering the lines 19. This is achieved by the check valve 14.
  • pressure medium passes through the line 24 into the longitudinal bore 26, whereupon the unlocking piston 27 moves toward the valve part.
  • the control valve 46 or its conical collar 49 is lifted off the valve seat 50 via the push-fit tappet 54.
  • the damping space 42 communicates with the bore section 35 and the radial bores 39 via the blind bore 56 and the transverse bore 57.
  • the same parts as in the previous exemplary embodiment are designated with the same numbers. It differs essentially in that when the load is lowered, i.e. when the directional control valve is in its switching position III, both valve cones stand out from their seats, the internal valve forming a pilot valve for the main control valve.
  • a damping piston 61 acts on the pilot valve 60 via the compression spring 44, i. H. it rests on the valve seat 50 under the force of this spring.
  • the hollow damping piston 61 there is a longitudinal bore 62 which is operatively connected to a longitudinal blind bore 63 formed in the pilot valve 60.
  • One or more transverse bores 64 lead outward from the bore 63.
  • a parallel bore 65 penetrates the pilot valve parallel to the blind bore 63. This communicates with a space 67 outside the pilot valve 60.
  • the throttle notch 58 is again in the same place.
  • the main control valve 70 accommodating the pilot valve 60 has a throttle bore 71 which penetrates its wall, with the exception of a fine control pin 72, which adjoins the conical collar 73. Bofin detects the directional control valve in its switching position 111, in which the load is lowered and pressure medium enters the line 19, so both the pilot valve 60 and the main control valve 70 are lifted from their seats.

Description

Die Erfindung geht aus von einer Steuervorrichtung für einen hydraulischen Arbeitszylinder nach dem Oberbegriff des Anspruchs 1. Hier weist das Ablauf-Steuerventil einen zylindrischen Schaft auf, der im Sperrventilkörper gleitend geführt ist und eine Längsnut mit konischem Abschnitt hat, über welche Nut .das Druckmittel gedrosselt vom Zylinder zum Behälter fließt. Am Ablauf-Steuerventil kann ein zylindrischer Fortsatz ausgebildet sein, der in einem Dämpfungsraum ragt. Damit erfolgt die Öffnungsbewegung des Ablauf-Steuerventils gedämpft, was zu ruckfreier Absenkung der Last führt. Diese bekannte Vorrichtung ist verhältnismäßig einfach aufgebaut, dürfte aber den Nachteil haben, daß die Dämpfung des Steuerventils und Abströmen des Druckmittels aus dem Arbeitszylinder infolge der sehr einfachen Bauweise noch nicht optimal sind (DE-A-2 214 245).The invention is based on a control device for a hydraulic working cylinder according to the preamble of claim 1. Here, the drain control valve has a cylindrical shaft which is slidably guided in the shut-off valve body and has a longitudinal groove with a conical section, via which groove the pressure medium is throttled flows from the cylinder to the container. A cylindrical extension, which projects in a damping space, can be formed on the sequence control valve. The opening movement of the sequence control valve is damped, which leads to a jerk-free lowering of the load. This known device is relatively simple, but should have the disadvantage that the damping of the control valve and the outflow of the pressure medium from the working cylinder are not yet optimal due to the very simple construction (DE-A-2 214 245).

Aufgabe der Erfindung ist es, eine Vorrichtung nach dem Oberbegriff des Anspruchs 1 zu schaffen, die bei vertretbarem Bauaufwand eine besonders gute Dämpfung des Ablauf-Steuerventils und ein besonders gutes ruckfreies Absenken des Verbrauchers ermöglicht.The object of the invention is to provide a device according to the preamble of claim 1, which allows a particularly good damping of the sequence control valve and a particularly good jerk-free lowering of the consumer with a reasonable amount of construction.

Diese Aufgabe wird erfindungsgemäß durch die im Kennzeichenteil des Anspruchs 1 genannten Mittel gelöst.This object is achieved by the means mentioned in the characterizing part of claim 1.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Fig. 1 eine hydraulische Steuervorrichtung mit einem Senkbrems-Sperrventil im Längsschnitt, Fig. 2 eine Abwandlung des Ausführungsbeispiels nach Fig. 1.An embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a hydraulic control device with a lowering brake blocking valve in longitudinal section, FIG. 2 shows a modification of the exemplary embodiment according to FIG. 1.

Eine Pumpe 10 saugt aus einem Behälter 11 Druckmittel an, das über ein 4/3-Wegeventil einem Verbraucher 13 - hier ein doppeltwirkender Arbeitszylinder - direkt oder über ein hydraulisch entsperrbares, als Senkbremsventil dienendes Sperrventil 14 zugeführt wird. Der Arbeitszylinder 13 hat zwei Druckräume 15, 16, in denen ein Kolben 17 mit Kolbenstange 18 geführt ist.A pump 10 draws in pressure medium from a container 11, which is fed via a 4 / 3- way valve to a consumer 13 - here a double-acting working cylinder - directly or via a hydraulically unlockable check valve 14 serving as a lowering brake valve. The working cylinder 13 has two pressure chambers 15, 16, in which a piston 17 with a piston rod 18 is guided.

Vom Wegeventil 12 führt eine Leitung 19 unmittelbar zum Druckraum 15 und eine Leitung 20 zu einer Bohrung 21 des Gehäuses 22 des Sperrventils 14. Von der Leitung 19 zweigt eine Leitung 24 ab, die zu einer zweiten Bohrung 25 des Gehäuses 22 führt.From the directional control valve 12, a line 19 leads directly to the pressure chamber 15 and a line 20 leads to a bore 21 in the housing 22 of the check valve 14. A line 24 branches off from the line 19 and leads to a second bore 25 in the housing 22.

Im Gehäuse 22 des Sperrventils 14 ist eine Längsbohrung 26 ausgebildet, in deren einem Abschnitt ein Entsperrkolben 27 dicht gleitend geführt ist. Die Bohrung 21 mündet in die Längsbohrung 26. Diese nimmt in ihrem anderen, etwas erweiterten Teil 26' ein als Sperrventilkörper dienendes Ventilglied 30 auf, das mit einem konisch ausgebildeten Bund 31 auf einem ebenfalls konisch ausgebildeten Ventilsitz 32 aufliegt, welcher Teil des Bohrungsabschnittes 26' ist.In the housing 22 of the check valve 14, a longitudinal bore 26 is formed, in one section of which an unlocking piston 27 is guided in a tightly sliding manner. The bore 21 opens into the longitudinal bore 26. This receives in its other, somewhat enlarged part 26 'a valve member 30 serving as a check valve body, which rests with a conical collar 31 on a likewise conical valve seat 32, which part of the bore section 26' is.

Das Ventilglied 30 weist eine Stufenbohrung 33 auf, welche im wesentlichen aus drei Bohrungsabschnitten 34 bis 36 abnehmenden Durchmessers besteht. Am Ventilglied 30 ist eine Ringnut 38 ausgebildet, von der mehrere Radialbohrungen 39 in den Bohrungsabschnitt 35 führen.The valve member 30 has a stepped bore 33, which essentially consists of three bore sections 34 to 36 of decreasing diameter. An annular groove 38 is formed on the valve member 30, from which a plurality of radial bores 39 lead into the bore section 35.

Wenn das Ventilglied 30 auf seinem Ventilsitz 32 aufliegt, stehen die Radialbohrungen 39 mit einer Querbohrung 40 im Gehäuse 22 in Verbindung, von welcher eine Leitung 41 zum Druckraum 16 des Arbeitszylinders 13 führt. Die Mündung der Querbohrung 40 in den Bohrungsabschnitt 26' liegt unmittelbar neben dem Ventilsitz 32. Der Bohrungsabschnitt 26' bildet einen Dämpfungsraum 42 und ist durch eine Verschlußschraube 43 verschlossen. An deren innerem Ende liegt das eine Ende einer Druckfeder44 an, deren anderes Ende in eine zentrale Sackbohrung 45 eines Steuerventils 46 taucht.When the valve member 30 rests on its valve seat 32, the radial bores 39 are connected to a transverse bore 40 in the housing 22, from which a line 41 leads to the pressure chamber 16 of the working cylinder 13. The opening of the transverse bore 40 in the bore section 26 'lies directly next to the valve seat 32. The bore section 26' forms a damping space 42 and is closed by a screw plug 43. One end of a compression spring 44 bears against its inner end, the other end of which plunges into a central blind bore 45 of a control valve 46.

Das Steuerventil 46 ist mit seinem hinteren Ventilteil 47 im Bohrungsabschnitt 34 des Ventilglieds 30 dicht gleitend geführt. An das zylindrische Ventilteil 47 schließt sich ein zylindrisches Ventilteil48 mit wesentlich kleinerem Durchmesser an, das in den Bohrungsabschnitt 35 hineinragt. Das Ventilteil 48 hat einen konischen Bund 49, mit dem es durch die Kraft der Feder 44 auf einen Ventilsitz 50 gedrückt wird, der durch die Schulter der beiden Bohrungsabschnitte 35 und 36 gebildet ist. An den konischen Bund 49 schließt sich eine Ringnut 52 an, auf die ein Feinsteuerzapfen 53 als dritter Ventilteil folgt. Der Feinsteuerzapfen 53 ist mit einem schmalen zylindrischen Abschnitt 53' im Bohrungsabschnitt 36 geführt. An den Feinsteuerzapfen 53 schließt sich als vierter und letzter Ventilteil ein Aufstoßstößel 54 an, der dicht bis an den Sperrkolben 27 heranreicht, wenn dieser seine eine Endlage einnimmt.The control valve 46 is guided with its rear valve part 47 tightly sliding in the bore section 34 of the valve member 30. A cylindrical valve part 48 with a much smaller diameter adjoins the cylindrical valve part 47 and projects into the bore section 35. The valve part 48 has a conical collar 49, with which it is pressed by the force of the spring 44 onto a valve seat 50, which is formed by the shoulder of the two bore sections 35 and 36. An annular groove 52 adjoins the conical collar 49, followed by a fine control pin 53 as the third valve part. The fine control pin 53 is guided with a narrow cylindrical section 53 'in the bore section 36. The fine control pin 53 is followed by a fourth and last valve part, which is an impact tappet 54, which reaches close to the locking piston 27 when it reaches its one end position.

An die die Feder 44 aufnehmende Sackbohrung 45 schließt sich noch eine kurze Sackbohrung 56 mit wesentlich geringerem Durchmesser an, von der mehrere Querbohrungen 57 nach außen führen. Unmittelbar an eine der Querbohrungen 57 schließt sich eine Drosselkerbe 58 an, die bis an die aus den Ventilteilen 47,48 gebildete Schulter führt. Diese hat stets einen bestimmten Abstand zu der aus den Bohrungsabschnitten 34, 35 gebildeten Schulter. In diesem Bereich ist der Bohrungsabschnitt 34 erweitert zu einem Bohrungsabschnitt 34'.A short blind bore 56 with a substantially smaller diameter follows from the blind bore 45 receiving the spring 44, from which a plurality of transverse bores 57 lead to the outside. Immediately adjacent to one of the transverse bores 57 is a throttle notch 58 which leads up to the shoulder formed by the valve parts 47, 48. This is always at a certain distance from the shoulder formed from the bore sections 34, 35. In this area, the bore section 34 is expanded to a bore section 34 '.

Das Wegeventil vermag drei Schaltstellungen 1, II und 111 einzunehmen. Wird es von seiner Neutralstellung II in die Schaltstellung I gebracht, so fließt Druckmittel über die Leitung 20 zur Bohrung 21, und das Ventilglied 30 wird samt dem Steuerventil 46 entgegen der Kraft der Feder 44 von seinem Ventilsitz 32 abgehoben, so daß Druckmittel über die Bohrung 40 und Leitung 41 in den Druckraum 16 des Arbeitszylinders 13 eindringen kann. Das Steuerventil bleibt dabei in seiner Lage, d. h. der konische Bund 49 bleibt auf dem Ventilsitz 50 liegen. Das Ventilglied 30 hat somit nur die Funktion eines Rückschlagventils. Durch die Druckmittelbeaufschlagung des Druckraums 16 wird der Kolben 17 entgegen einer Last ausgefahren, wobei Druckmittel aus dem Druckraum 15 über die Leitung 19 zum Behälter 11 abgeführt wird.The directional control valve can assume three switch positions 1, II and 111. If it is brought from its neutral position II into the switching position I, pressure medium flows via the line 20 to the bore 21, and the valve member 30 is lifted together with the control valve 46 against the force of the spring 44 from its valve seat 32, so that pressure medium through the bore 40 and line 41 can penetrate into the pressure chamber 16 of the working cylinder 13. The control valve remains in its position, ie the conical collar 49 remains on the valve seat 50. The valve member 30 thus only has the function of a check valve. By pressurizing the pressure chamber 16, the piston 17 is opposed ner load extended, pressure medium is discharged from the pressure chamber 15 via the line 19 to the container 11.

Zum Senken der Last wird das Wegevontil 12 in seine Schaltstellung 111 gebracht. Wichtig ist dabei, daß dieser Vorgang geräuschlos, ruckfrei und so erfolgen muß, daß die Last dem nun in die Leitungen 19 gelangenden Druckmittelstrom nicht vorauseilt. Dies wird durch das Sperrventil 14 erreicht. Durch Druckbeaufschlagung der Leitung 19 gelangt über die Leitung 24 Druckmittel in Längsbohrung 26, worauf sich der Entsperrkolben 27 zum Ventilteil hin bewegt. Über den Aufstoßstößel 54 wird das Steuerventil 46 bzw. dessen konischer Bund 49 vom Ventilsitz 50 abgehoben. Bei Beginn des Absenkens steht der Dämpfungsraum 42 über die Sackbohrung 56 und die Querbohrung 57 mit dem Bohrungsabschnitt 35 und den Radialbohrungen 39 in Verbindung. Wird das Steuerventil 46 entgegen der Kraft der Feder 44 verschoben, dann werden auch die Querbohrungen 57 verschlossen, da sie aus dem Bereich der Erweiterung 34' gelangt sind und durch Eintauchen in den Bohrungsabschnitt 34 verschlossen werden. Druckmittel kann nun aus dem Dämpfungsraum 42 nur noch über die Drosselkerbe 58 in den Bohrungsabschnitt 35 abströmen, wodurch die Öffnungsbewegung des Steuerventils 46 gedämpft wird. Druckmittel kann aus dem Druckraum 16 des Arbeitszylinders aber erst dann abfließen, wenn der zylindrische Abschnitt 53' über den Ventilsitz 50 hinausgelangt ist. Es fließt dann mehr oder weniger stark gedrosselt zum Behälter ab, wobei ein Schwingen des Steuerventils 46 durch die Drosselkerbe 58 sicher verhindert wird, so daß der Senkvorgang stetig erfolgt. Bei diesem Vorgang hebt sich das Ventilglied 30 nicht von seinem Ventilsitz 32 ab.To lower the load, the directional valve 12 is brought into its switching position 111. It is important that this process must be carried out silently, smoothly and in such a way that the load does not lead ahead of the pressure medium flow now entering the lines 19. This is achieved by the check valve 14. By pressurizing the line 19, pressure medium passes through the line 24 into the longitudinal bore 26, whereupon the unlocking piston 27 moves toward the valve part. The control valve 46 or its conical collar 49 is lifted off the valve seat 50 via the push-fit tappet 54. At the beginning of the lowering, the damping space 42 communicates with the bore section 35 and the radial bores 39 via the blind bore 56 and the transverse bore 57. If the control valve 46 is moved against the force of the spring 44, then the transverse bores 57 are also closed, since they have come from the area of the extension 34 ′ and are closed by being immersed in the bore section 34. Pressure medium can now only flow out of the damping space 42 via the throttle notch 58 into the bore section 35, as a result of which the opening movement of the control valve 46 is damped. However, pressure medium can only flow out of the pressure chamber 16 of the working cylinder when the cylindrical section 53 'has reached beyond the valve seat 50. It then flows more or less throttled to the container, whereby the control valve 46 is reliably prevented by the throttle notch 58, so that the lowering process takes place continuously. In this process, the valve member 30 does not rise from its valve seat 32.

Ein Verstopfen der Drosselstelle 58 ist so gut wie nicht möglich, da sie ja stets wieder aus dem Bohrungsabschnitt 34 austaucht und dabei gereinigt wird.Clogging of the throttle point 58 is practically impossible since it always emerges from the bore section 34 and is cleaned in the process.

Beim Ausführungsbeispiel nach der Fig. 2 sind gleiche Teile wie beim vorhergehenden Ausführungsbeispiel mit denselben Ziffern bezeichnet. Es unterscheidet sich im wesentlichen dadurch, daß beim Senken der Last, also dann, wenn das Wegeventil in seiner Schaltstellung III steht, sich beide Ventilkegel von ihren Sitzen abheben, wobei das innenliegende Ventil ein Vorsteuerventil für das Hauptsteuerventil bildet. Auf das Vorsteuerventil 60 wirkt über die Druckfeder 44 ein Dämpfungskolben 61 ein, d. h. es legt sich unter der Kraft dieser Feder auf den Ventilsitz 50. Im hohl ausgebildeten Dämpfungskolben 61 befindet sich eine Längsbohrung 62, die mit einer im Vorsteuerventil 60 ausgebildeten, längs verlaufenden Sackbohrung 63 in Wirkverbindung steht. Von der Bohrung 63 führen wieder eine oder mehrere Querbohrungen 64 nach außen. Parallel zur Sackbohrung 63 ist das Vorsteuerventil von einer Längsbohrung 65 durchdrungen. Diese steht mit einem Raum 67 außerhalb des Vorsteuerventils 60 in Verbindung. Die Drosselkerbe 58 befindet sich wiederum an derselben Stelle. Das das Vorsteuerventil 60 aufnehmende Hauptstouerventil 70 weist eine seine Wandung durchdringende Drosselbohrung 71 auf, außor dem noch einen Feinsteuerzapfen 72, welchor sich an den konischen Bund 73 anschließt. Bofin det sich das Wegeventil in seiner Schaltstellung 111, in welcher die Last gesenkt wird und Druckmittel in die Leitung 19 gelangt, so heben sich sowohl das Vorsteuerventil 60 wie auch das Hauptsteuerventil 70 von ihren Sitzen ab. Beim Öffnen des Hauptsteuerventils 70 fließt Druckmittel aus dem Raum 67 über den Spalt zwischen dem Dämpfungskolben 61 und dem Hauptsteuerventil 70 über die Längsbohrung 65 ab; das Hauptsteuerventil 70 wird durch Wirken des in der Leitung 41 herrschenden Lastdrucks gedämpft geöffnet. Beim Öffnen des Vorsteuerventils 60 fließt das im Dämpfungsraum 42 enthaltene Druckmittel über die Bohrungen 62, 63 und 64 sowie die Drosselkerbe 58 ab. Dies ist derselbe Vorgang wie zuvor.In the exemplary embodiment according to FIG. 2, the same parts as in the previous exemplary embodiment are designated with the same numbers. It differs essentially in that when the load is lowered, i.e. when the directional control valve is in its switching position III, both valve cones stand out from their seats, the internal valve forming a pilot valve for the main control valve. A damping piston 61 acts on the pilot valve 60 via the compression spring 44, i. H. it rests on the valve seat 50 under the force of this spring. In the hollow damping piston 61 there is a longitudinal bore 62 which is operatively connected to a longitudinal blind bore 63 formed in the pilot valve 60. One or more transverse bores 64 lead outward from the bore 63. A parallel bore 65 penetrates the pilot valve parallel to the blind bore 63. This communicates with a space 67 outside the pilot valve 60. The throttle notch 58 is again in the same place. The main control valve 70 accommodating the pilot valve 60 has a throttle bore 71 which penetrates its wall, with the exception of a fine control pin 72, which adjoins the conical collar 73. Bofin detects the directional control valve in its switching position 111, in which the load is lowered and pressure medium enters the line 19, so both the pilot valve 60 and the main control valve 70 are lifted from their seats. When the main control valve 70 is opened, pressure medium flows out of the space 67 via the gap between the damping piston 61 and the main control valve 70 via the longitudinal bore 65; the main control valve 70 is opened damped by the action of the load pressure prevailing in the line 41. When opening the pilot valve 60, the pressure medium contained in the damping chamber 42 flows out through the bores 62, 63 and 64 and the throttle notch 58. This is the same process as before.

Claims (4)

1. Control device for a hydraulic working cylinder (13), having a directional control valve (12), arranged downstream from a pressure medium source (10), and a countertorque shut-off valve (14) arranged between the directional control valve (12) and the working cylinder, which countertorque shut-off valve (14) has an unlocking piston (27) which is mounted in a sliding manner in a housing (22) and interacts with a relief control valve (46 and 60) arranged in a shut-off valve body (30 and 70), which relief control valve (46 and 60), at a tapered shoulder (49) of its closure part (48) and by the force of a spring (44), sits against a valve seat (50) formed in the shut-off valve body (30 and 70), and the shut-off valve body likewise sits against a valve seat (32) formed in the housing (22), with the relief control valve (46 and 60) having a control pin (53 and 53') which is separated from the closure part (48) by an annular groove (52), slides in a discharge bore (36) surrounded by the valve seat (50) of the shut-off valve body (30 and 70) and has a cylindrical guide section (53') guided in the relief bore (36) and a fine control pin (53), and with a pistonlike part (47) being formed on the relief control valve (46 and 60), which piston-like part (47), when the relief control valve is lifted from its seat (50), displaces pressure medium out of a damping space (42) via a throttle (58), and pressure medium is discharged out of the working cylinder (13) via the relief control valve (46 and 60) only when the cylindrical guide section (53') of the control pin emerges out of the discharge bore (36), characterised in that the fine control pin (53) has a tapered design, that the piston-like (47) of the relief control valve (46 and 60) is guided in a sliding manner in a bore (34) of the shut-off valve body (30 and 70) and that the throttle portion (58) is formed on the piston-like part (47) and interacts with the bore (34) of the shut-off valve body (30 and 70) in such a way that pressure medium is discharged out of the damping space (42) first of all essentially without being throttled and, after a slight displacement of the relief control valve (46 and 60), is discharged while being throttled.
2. Device according to Claim 1, characterised in that the relief control valve (46 and 60) is designed as a stepped piston, with the piston-like part (47), the closure part (48) and the control pin (53 and 53') having decreasing diameters and with the stepped piston being arranged in a stepped bore (33) of the shut-off valve body (30 and 70) in such a way that a pressure space (34' and 35) is formed between the closure part (48) and the shut-off valve body (30 and 70), which pressure space (34' and 35) is connected to the working cylinder side (16) via at least one opening (39) in the shut-off valve body (30 and 70).
3. Device according to Claim 2, characterised in that a channel (56, 57; 63, 64), which is connected to the damping space (42), is formed in the piston-like part (47), which channel (56, 57; 63, 64), in the closed position of the relief control valve (46 and 60), opens out into the pressure space (34' and 35) via at least one radial transverse bore (57 and 64) and, in the open position of the relief control valve, with the radial transverse bore sealed, opens out into the pressure space (34' and 35) via the throttle (58).
4. Device according to Claim 2 or 3, characterised in that the opening is designed as a throttle bore (71).
EP81107401A 1980-11-08 1981-09-18 Hydraulic motor control system Expired EP0051728B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3042277 1980-11-08
DE19803042277 DE3042277A1 (en) 1980-11-08 1980-11-08 CONTROL DEVICE FOR A HYDRAULIC WORKING CYLINDER

Publications (2)

Publication Number Publication Date
EP0051728A1 EP0051728A1 (en) 1982-05-19
EP0051728B1 true EP0051728B1 (en) 1985-06-19

Family

ID=6116353

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81107401A Expired EP0051728B1 (en) 1980-11-08 1981-09-18 Hydraulic motor control system

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EP (1) EP0051728B1 (en)
JP (1) JPS57107402A (en)
DE (2) DE3042277A1 (en)

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US4466336A (en) * 1982-02-08 1984-08-21 Lakeland Hydraulics, Inc. Control valve for hydraulic motor apparatus
JPS60104899A (en) * 1983-11-09 1985-06-10 Aisin Seiki Co Ltd Low temperature vessel connected to refrigerator
DE4032078C2 (en) * 1990-10-10 1997-08-07 Bosch Gmbh Robert Control device for a hydraulic working cylinder
AT402334B (en) * 1991-03-20 1997-04-25 Hoerbiger Gmbh HYDRAULIC CYLINDER / PISTON ARRANGEMENT
DE4140604A1 (en) * 1991-12-10 1993-06-17 Bosch Gmbh Robert CONTROL DEVICE FOR THE VOLUME FLOW OF A HYDRAULIC WORKING AGENT
DE19754242A1 (en) * 1997-12-06 1999-06-10 Bosch Gmbh Robert Hydraulic check valve in seat valve design
CN103899596B (en) * 2014-03-31 2016-11-02 雷永志 A kind of hydraulic lock of band guide's check valve
CN105221755B (en) * 2014-07-02 2019-04-05 浙江师范大学 A kind of cone valve type direct acting big flow water valve with damping piston

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Also Published As

Publication number Publication date
DE3171037D1 (en) 1985-07-25
DE3042277A1 (en) 1982-06-03
JPS57107402A (en) 1982-07-03
EP0051728A1 (en) 1982-05-19

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