EP1540191B1 - Hydraulically controlled valve comprising at least one hydraulic drive unit - Google Patents

Hydraulically controlled valve comprising at least one hydraulic drive unit Download PDF

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Publication number
EP1540191B1
EP1540191B1 EP04738137A EP04738137A EP1540191B1 EP 1540191 B1 EP1540191 B1 EP 1540191B1 EP 04738137 A EP04738137 A EP 04738137A EP 04738137 A EP04738137 A EP 04738137A EP 1540191 B1 EP1540191 B1 EP 1540191B1
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EP
European Patent Office
Prior art keywords
valve
control
control pressure
pressure chamber
pressure
Prior art date
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Revoked
Application number
EP04738137A
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German (de)
French (fr)
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EP1540191A1 (en
Inventor
Josef ZÜRCHER
Hansruedi Brand
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Bucher Hydraulics AG
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Bucher Hydraulics AG
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a hydraulically controlled valve with at least one hydraulic drive according to the preamble of claim 1.
  • a load-holding brake valve which is controllable by a hydraulic drive.
  • the main piston of the load-holding brake valve is actuated by a plunger of a control piston.
  • This control piston is moved against the pressure of a Auf Kunststofffeder by a control pressure.
  • load-holding brake valves are suitable, for example, for controlling double-acting hydraulic consumers which are mechanically loaded. Depending on the type of mechanical stress, such devices tend to vibrate. For example, arrangements with a very long lever arm are known, for example in cranes. For example, a shock can cause a vibration through which the volume flow of the hydraulic oil fluctuates.
  • vibrations can also be triggered in the hydraulic system itself, when the control of a movement is started and / or the movement is accelerated or decelerated. Due to such vibrations, the speed of the hydraulic consumer is no longer constant. In this way, a precise control of movements is difficult or even prevented.
  • a directional control valve which is suitable for controlling double-acting hydraulic consumers. It is disclosed here that the spool of the directional control valve is movable by at least one drive. Shown is also a solution with two hydraulic drives. In each of these drives is arranged by a control pressure against a spring movable drive piston. Through this, for example, via a piston rod of the spool of the directional control valve movable. Vibration problems can also arise in such arrangements.
  • the invention has for its object to provide a hydraulically controlled by at least one hydraulic actuator valve, which against internal or external triggered vibrations is insensitive, without the responsiveness is deteriorated.
  • Fig. 1 which is a schematic representation, 1 means a hydraulically controlled valve, which in this embodiment is a load-holding brake valve.
  • This designed as a load-holding brake valve hydraulically controlled valve 1 is shown on the right in a view that reveals no details of the internal structure, because the internal structure is not essential to the invention and in itself from WO-A1-97 / 32136 known.
  • the waiver of the representation of this internal structure is also appropriate because the not essential to the invention parts of the hydraulically controlled valve 1 may well be constructed differently than shown and described in WO-A1-97 / 32136.
  • the invention is therefore independent of a particular type of load-holding brake valve and regardless of the design of the valve 1.
  • valve 1 is hydraulically controlled by at least one hydraulic drive and that the valve 1 has a flow control device 2 through the flow of hydraulic oil from and to a consumer is controllable.
  • This flow control device 2 is controlled by a hydraulic drive 3.
  • a control plunger 4 which is part of a control piston 5, which acts on the flow control device 2.
  • the valve 1 is a load-holding brake valve, also called a lowering brake valve
  • the flow control device 2 consists, for example, of a pilot valve and a main valve.
  • the control plunger 4 acts directly on a spool.
  • the control piston 5 is shown as a view. According to the invention, it is designed as a stepped piston whose features according to the invention are described below. It should be mentioned in advance that on the left of the valve 1, a control pressure port X is provided on a housing part 6. At the control pressure port X in the housing part 6, a bore is present, which is referred to here as the control pressure primary chamber 7.
  • the control piston 5 at its the control pressure port X facing the end of a first stage 8, whose diameter D 8 only so much smaller than the inner diameter of the control pressure primary chamber 7, that he can move.
  • a control pressure Px present at the control pressure connection X and thus acting in the control pressure primary chamber 7 thus exerts a force F on the control piston 5 which corresponds to the product of the control pressure P x and the end face A 8 of the first stage 8, the end face A 8 the first stage 8 is the product of half diameter D 8 squared and ⁇ .
  • the control pressure P x thus causes a force F, with which the control piston 5 is pressed against a control spring 9. In this case, the path traveled by the control piston 5 depends on the spring rate of the control spring 9.
  • control piston 5 has a second step 10 whose diameter D 10 is greater than the diameter D 8 .
  • the diameter D 10 is slightly smaller than the inner diameter of a bore in the housing part 6. This bore in the housing part 6 is referred to as control pressure secondary chamber 11.
  • the hydraulically additionally effective area A 10 of the second stage 10 is a circular ring with the outer diameter D 10 and the inner diameter D. 8
  • Essential to the invention is that the control pressure primary chamber 7 and the control pressure secondary chamber 11 are connected by a connection 12 with a throttle point 13, which is shown schematically in FIG. It is irrelevant whether these control pressure primary chamber 7 and the control pressure secondary chamber 11 are formed by bores in a housing part 6 or whether they are realized in another way. An alternative embodiment will be shown. Essential to the invention is only that the hydraulic drive 3, the control pressure primary chamber 7 and the control pressure secondary chamber 11 has.
  • a higher control pressure P X acts only on the smaller end face A 8 .
  • the higher control pressure P X also acts on the hydraulically effective surface of the second stage 10, ie in total on an area A 10 , which results directly from the diameter D 10 . It follows that the movement of the control piston 5 is delayed, that is damped. In this way, the object of the invention is achieved in a surprisingly simple manner, because by this damping, the valve 1 against internal or external induced vibrations insensitive, without the responsiveness is deteriorated, which is when using a metering valve according to WO-A1-97 / 32136 could not be ruled out.
  • the diameter D 8 is for example 14 mm, the diameter D 10 20 mm.
  • the hydraulically effective end faces A 8 and A 10 are respectively 153.9 and 314.2 mm 2 , which gives an area ratio of 1 to 2.04. This indicates how large the amplitude of adjustable vibrations can be.
  • control pressure P X With decreasing control pressure P X , the damping is effective in an analogous manner. If the control pressure P X is reduced, the pressure in the control-pressure secondary chamber 11 can only be reduced slowly by hydraulic oil flowing via the connection 12 to the throttle point 13 from the control-pressure secondary chamber 11 into the control-pressure primary chamber 7.
  • the first stage 8 of the control piston 5 in conjunction with the associated bore in the housing part 6, which forms the control pressure primary chamber 7, are used.
  • the control pressure primary chamber 7 has an inner diameter D 7 .
  • the first stage 8 of the control piston 5 has, as already shown in Fig. 1, an outer diameter D. 8 This results in between an annular gap 14, the dimensions of which are given by the inner diameter D 7 and the outer diameter D 8 . If this annular gap 14 is used as a throttle 13, so that has a remarkable advantage.
  • annular gap 14 Since the annular gap 14 is functionally essential, the tolerances of inner diameter D 7 and outer diameter D 8 is of great importance. These tolerances are chosen so that the annular gap 14 has a gap height of advantageously about 0.01 mm to 0.04 mm. In order to achieve this, a pairing of control piston 5 and housing part 6 can optionally be carried out by selecting mutually compatible production parts.
  • FIGS. 3a to 3c show a hydraulic circuit with a consumer 20, which in the illustrated example is a double-acting cylinder with a bottom pressure chamber and a rod pressure chamber. Instead of the double-acting cylinder but also a hydraulic motor 20 can be operated as a consumer.
  • the hydraulic circuit is shown in three operating states, namely in the neutral position in FIG. 3a, in the load-lifting mode in FIG. 3b and in the load-reducing mode in FIG. 3c.
  • the existing individual elements of the hydraulic circuit are the same in all cases.
  • the hydraulic circuit is known per se and is shown here, because can be described with reference to this circuit, the inventive effect of the inventively designed hydraulically controlled valves.
  • a directional control valve 21 and a load-holding brake valve 22 are shown, which serve to control the load 20.
  • the load-holding brake valve 22 may, for example, be of the type shown in WO-A1-97 / 32136, but is equipped with a hydraulic drive 3 designed according to the invention.
  • the directional control valve 21 may, for example, be of one of the designs shown in WO-A1-02 / 075162, but is also equipped with hydraulic drives 3 'designed according to the invention.
  • the hydraulic oil can be conveyed between the tank 25 and the consumer 20 by means of a pump 24 driven by a motor 23.
  • the pump 24 are associated in a known manner, a first check valve 26 and a pressure relief valve 27.
  • the flow of the hydraulic oil is determined by the positions of the directional control valve 21 and the load-holding brake valve 22.
  • a second check valve 28 is arranged in a line to the bottom pressure chamber of the consumer 20, .
  • This separate check valve 28 can be omitted if the load-holding brake valve 22 includes such a check valve, which is in the representation of the load-holding brake valve 22 by the reference numeral 28 'is designated.
  • the directional control valve 21 is controlled in a known manner that its two drives 3 'are controlled. If none of the drives 3 'are actuated, ie acted upon by a control pressure P St , the directional control valve 21 assumes the neutral position.
  • Fig. 3b the load-lifting operation is shown. This is achieved in that the one of the drives 3 'of the directional control valve 21 is driven with a control pressure P St. The spool of the directional control valve 21 is thereby moved so that the flow of hydraulic oil from the pump 24 through the directional control valve 21 to the bottom pressure chamber of the consumer 20 and from the rod pressure chamber of the consumer 20 to the tank 25 is possible. The pump 24 thus delivers hydraulic oil from the tank 25 to the bottom side of the consumer 20, wherein the first check valve 26 and the second
  • Fig. 3c the load lowering operation is shown.
  • the pump 24 delivers hydraulic oil to the rod-pressure chamber of the consumer 20.
  • the other drive 3 'of the directional control valve 21 is acted upon by a control pressure P St.
  • P St the control pressure
  • the connection from the pump 24 to the rod pressure chamber of the consumer 20 is open and also the connection from the bottom pressure chamber of the consumer 20 to the tank 24.
  • the control pressure P X acting on the load-holding brake valve 22 is now high. It is determined by the pressure generated by the pump and the pressure loss across the directional control valve 21.
  • FIG. 4 shows an advantageous embodiment of a drive 3 which can be used in the case of a load-holding brake valve 22 (FIGS. 3 a to 3 c).
  • Fig. 4 corresponds to the Fig. 1, but also contains this advantageous embodiment. This is that between the control pressure primary chamber 7 and the control pressure secondary chamber 11, a relief check valve 30 is arranged. This allows the pressure reduction from the Steuerdruek secondary chamber 11 to the control pressure primary chamber 7 out, the pressure difference at which the relief check valve 30 opens, is determined by a spring 31.
  • This relief check valve 30 has the effect described below. If the control pressure P X is reduced, as has already been mentioned initially, the control piston 5 is moved to the left by the action of the control spring 9. This means first that the pressure in the control pressure secondary chamber 11 can not fall immediately. The pressure drop can only under the effect of compound 12 with the Throttling point 13 occur. In the load-lifting state according to FIG. 3b, however, as previously stated, the load-holding brake valve 22 has no effect. It is therefore not useful if the damping effect occurs in this operating state by the inventive design of the drive 3. By the relief check valve 30, this is achieved.
  • Fig. 5 which in itself corresponds to FIG. 4, but in which instead of the connection 12 with the throttle point 13 of the annular gap 14 is shown, it is shown as an additional advantageous embodiment that in the cylindrical surface of the first stage 8 at the Control pressure secondary chamber 11 facing a longitudinal groove 33 is inserted.
  • the effective length of the annular gap 14 is limited, the flow of hydraulic oil between the control pressure primary chamber 7 and the control pressure secondary chamber 11 facilitates and thus limits the effect of the damping.
  • the damping effect of a valve 1 with respect to the particular application can be very easily adjusted by the length of the longitudinal groove 33 is chosen differently depending on the application.
  • FIG. 6 shows a further advantageous embodiment of a drive 3 which can be used in the case of a load-holding brake valve 22 (FIGS. 3 a to 3 c).
  • the relief check valve 30 shown in FIGS. 4 and 5 is integrated directly into the drive 3. Shown are only the functionally important parts according to the invention, but not, for example, those parts that serve the power transmission to the operated Fluß complaintvornchtung 2 (Fig. 1), not the control spring 9 ( Figure 1).
  • the control piston 5 Shown is the control piston 5 with its first stage 8 and its second stage 10, which, as previously shown, the diameter D 8 and D 10 have. Also shown are the control pressure primary chamber 7 and the control pressure secondary chamber 11. Notwithstanding FIG. 5, in this exemplary embodiment the relief check valve 30 is arranged within the hydraulic drive 3. In contrast to the embodiments according to FIGS. 1, 4 and 5, the hydraulic drive 3 has no special housing part 6. Instead, the hydraulic drive 3 is arranged inside the housing of the valve 1 to be controlled (FIG. 1), this housing being designated by the reference numeral 40 in FIG. In the left open housing 40, a lid 41 is screwed. In this cover 41 is an opening which represents the control pressure port X, which, as in the previous embodiments, is connected to the control pressure primary chamber 7.
  • an aperture 42 is now arranged between the control pressure connection X and the control pressure primary chamber 7, namely within the cover 41.
  • a limitation of the flow is achieved. This has the consequence that at rapidly increasing control pressure P X, the increase in the pressure in the control pressure primary chamber 7 is delayed. Since this delay of the pressure increase means a damping, this means an advantageous additional measure with regard to the solution of the problem.
  • the damping according to the invention by the throttle point 13 (FIG. 1) or the annular gap 14 and the damping by the aperture 42 additionally acts, it is advantageous if the attenuation by the aperture 42 is significantly lower than the damping by the throttle 13 It has been found that an optimal effect then results if, for example, the annular gap 14 is dimensioned so that it corresponds to a nozzle of 0.1 mm diameter, while the diaphragm 42 a Nozzle diameter of 0.3 to 0.6 mm corresponds. With a diameter ratio of 1: 3 to 1: 6 results in an area ratio of 1: 9 to 1:36. This clearly shows that the damping through the throttle point 13 (FIG. 1) or the annular gap 14 is dominant. Through the aperture 42, a further improvement is achieved
  • the relief check valve 30 integrated in the hydraulic drive 3 is formed by a non-return plate 45 which seals against a seat surface 44 and is pressed against the seat surface 44 by the spring 31 already shown in FIGS. 4 and 5.
  • the check disc 45 has a central bore 46. Within this bore 46 is that part of the control piston 5, which forms the first stage 8.
  • the annular gap 14 is thus limited on the one hand by this bore 46 and on the other hand by the diameter D 8 of the first stage 8 of the control piston 5. With regard to the dimensioning of the annular gap 14, the rules already mentioned are applicable.
  • the function of this relief check valve 30 has been previously described. 6, the closed position is shown.
  • the relief check valve 30 opens when the control pressure P X is reduced, as has already been described in connection with FIG. 4.
  • the check disc 45 then moves against the spring 31 to the left, so lifts off from the seat 44.
  • hydraulic oil can flow directly from the control pressure secondary chamber 11 into the control pressure primary chamber 7.
  • the relief check valve 30 is parallel to the annular gap 14 between the control pressure primary chamber 7 and the control pressure secondary chamber 11. This is also in the embodiment of FIG. 6 so.
  • the construction according to FIG. 6 advantageously results in a compact construction.
  • the invention is applicable to all types of hydraulically controlled valves 1, if due to the control and / or powered by the consumer 20 Device such as a crane, or a shovel, the occurrence of vibrations can not be excluded.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Servomotors (AREA)
  • Sliding Valves (AREA)
  • Safety Valves (AREA)
  • Actuator (AREA)

Abstract

A hydraulically controlled valve includes at lease one hydraulic drive unit that is provided with a control piston to which a control tappet is connected. The control tappet acts upon a flow control mechanism of the valve for controlling the flow of hydraulic oil from or to a consumer. The control piston can be moved towards a control spring by a control pressure P<SUB>X</SUB>. The control piston has a first step and a second step which have different diameters. A connection having a throttle point is provided between a primary control pressure chamber and a secondary control pressure chamber. The valve creates a throttle effect with the aid of which vibrations are dampened.

Description

Die Erfindung bezieht sich auf ein hydraulisch gesteuertes Ventil mit mindestens einem hydraulischen Antrieb gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a hydraulically controlled valve with at least one hydraulic drive according to the preamble of claim 1.

Aus WO-A1-97/32136 ist ein Lasthalte-Bremsventil bekannt, das durch eine hydraulischen Antrieb steuerbar ist. Der Hauptkolben des Lasthalte-Bremsventils wird dabei von einem Stößel eines Aufsteuerkolbens betätigt. Dieser Aufsteuerkolben wird gegen den Druck einer Aufsteuerfeder durch einen Steuerdruck bewegt. Solche Lasthalte-Bremsventile eignen sich beispielsweise zur Ansteuerung doppeltwirkender hydraulischer Verbraucher, die mechanisch belastet sind. Je nach der Art der mechanischen Belastung neigen solche Vorrichtungen zu Schwingungen. Bekannt sind beispielsweise Anordnungen mit sehr langem Hebelarm, zum Beispiel bei Kranen. Beispielsweise durch einen Stoß kann hierbei eine Schwingung entstehen, durch die der Volumenstrom des Hydrauliköls schwankt. Schwingungen können aber auch im Hydrauliksystem selbst ausgelöst werden, wenn die Steuerung einer Bewegung begonnen wird und/oder die Bewegung beschleunigt oder verzögert wird. Aufgrund solcher Schwingungen ist die Geschwindigkeit des hydraulischen Verbrauchers nicht mehr konstant. Auf diese Weise wird eine präzise Steuerung von Bewegungen erschwert oder gar verhindert.From WO-A1-97 / 32136 a load-holding brake valve is known, which is controllable by a hydraulic drive. The main piston of the load-holding brake valve is actuated by a plunger of a control piston. This control piston is moved against the pressure of a Aufsteuerfeder by a control pressure. Such load-holding brake valves are suitable, for example, for controlling double-acting hydraulic consumers which are mechanically loaded. Depending on the type of mechanical stress, such devices tend to vibrate. For example, arrangements with a very long lever arm are known, for example in cranes. For example, a shock can cause a vibration through which the volume flow of the hydraulic oil fluctuates. But vibrations can also be triggered in the hydraulic system itself, when the control of a movement is started and / or the movement is accelerated or decelerated. Due to such vibrations, the speed of the hydraulic consumer is no longer constant. In this way, a precise control of movements is difficult or even prevented.

Aus WO-A1-02/075162 ist ein Wegeventil bekannt, das zur Ansteuerung doppeltwirkender hydraulischer Verbraucher geeignet ist. Offenbart ist hier, daß der Schieberkolben des Wegeventils durch wenigstens einen Antrieb bewegbar ist. Gezeigt ist auch eine Lösung mit zwei hydraulischen Antrieben. In jedem dieser Antriebe ist ein durch einen Steuerdruck gegen eine Feder bewegbarer Antriebskolben angeordnet. Durch diesen ist beispielsweise über eine Kolbenstange der Schieberkolben des Wegeventils bewegbar. Schwingungsprobleme können auch bei solchen Anordnungen entstehen.From WO-A1-02 / 075162 a directional control valve is known, which is suitable for controlling double-acting hydraulic consumers. It is disclosed here that the spool of the directional control valve is movable by at least one drive. Shown is also a solution with two hydraulic drives. In each of these drives is arranged by a control pressure against a spring movable drive piston. Through this, for example, via a piston rod of the spool of the directional control valve movable. Vibration problems can also arise in such arrangements.

Aus DE-A1-24 31 785 ist ein hydraulisches direkt gesteuertes Druckbegrenzungsventil in Schieberausführung bekannt. Dieses Ventil besitzt wegen der Direktsteuerung des vorhandenen Differentialkolbens keinen hydraulischen Antrieb.From DE-A1-24 31 785 a hydraulic directly controlled pressure relief valve in slide design is known. This valve has no hydraulic drive because of the direct control of the existing differential piston.

Aus US-A-2,361,881 ist ein Ventil bekannt, das als Druckbegrenzungsventil verwendet werden kann. Auch dieses Ventil besitzt keinen hydraulischen Antrieb.From US-A-2,361,881 a valve is known which can be used as a pressure relief valve. Also this valve has no hydraulic drive.

Aus DE-AS-1 254 925 ist ein federbelastetes Überdruckventil bekannt, das gleichfalls keinen hydraulischen Antrieb aufweist.From DE-AS-1 254 925 a spring-loaded pressure relief valve is known, which also has no hydraulic drive.

Der Erfindung liegt die Aufgabe zugrunde, ein durch mindestens einen hydraulischen Antrieb hydraulisch gesteuertes Ventil zu schaffen, das gegen intern oder extern ausgelöste Schwingungen unempfindlich ist, ohne daß die Ansprechempfindlichkeit verschlechtert wird.The invention has for its object to provide a hydraulically controlled by at least one hydraulic actuator valve, which against internal or external triggered vibrations is insensitive, without the responsiveness is deteriorated.

Die genannte Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen ergeben sich aus den abhängigen Ansprüchen.The above object is achieved by the features of claim 1. Advantageous developments emerge from the dependent claims.

Nachfolgend werden Ausführungsbeispiele der Erfindung anhand der Zeichnung näher erläutert.Embodiments of the invention will be explained in more detail with reference to the drawing.

Es zeigen:

Fig. 1
ein Schema der erfindungswesentlichen Details am Beispiel eines Lasthalte-Bremsventils,
Fig. 2
eine unmäßstäbliche Darstellung eines Teils eines Steuerkolbens in einer Steuerdruck-Primärkammer,
Fig. 3a bis 3c
hydraulische Schemata für die verschiedene Betriebszustände eines Verbrauchers,
Fig. 4 und 5
vorteilhafte Ausgestaltungen eines Antriebs eines Lasthalte-Bremsventils und
Fig. 6
eine alternative vorteilhafte Ausgestaltung.
Show it:
Fig. 1
a schematic of the invention essential details on the example of a load-holding brake valve,
Fig. 2
an uneven representation of a part of a control piston in a control pressure primary chamber,
Fig. 3a to 3c
hydraulic schemes for the various operating conditions of a consumer,
4 and 5
advantageous embodiments of a drive of a load-holding brake valve and
Fig. 6
an alternative advantageous embodiment.

In der Fig. 1, die eine schematische Darstellung ist, bedeutet 1 ein hydraulisch gesteuertes Ventil, das in diesem Ausführungsbeispiel ein Lasthalte-Bremsventil ist. Dieses als Lasthalte-Bremsventil gestaltete hydraulisch gesteuerte Ventil 1 ist rechts in einer Ansicht dargestellt, die keine Details des inneren Aufbaus erkennen läßt, denn der innere Aufbau ist nicht erfindungswesentlich und an sich aus WO-A1-97/32136 bekannt. Der Verzicht auf die Darstellung dieses inneren Aufbaus ist auch deshalb angebracht, weil die nicht erfindungswesentlichen Teile des hydraulisch gesteuerten Ventils 1 durchaus auch anders aufgebaut sein können als in WO-A1-97/32136 gezeigt und beschrieben. Die Erfindung ist also unabhängig von einer bestimmten Bauart des Lasthalte-Bremsventils und überhaupt unabhängig von der Bauart des Ventils 1. Wesentlich ist lediglich, daß das Ventil 1 durch mindestens einem hydraulischen Antrieb hydraulisch steuerbar ist und daß das Ventil 1 eine Flußsteuervorrichtung 2 aufweist, durch die der Fluß von Hydrauliköl von und zu einem Verbraucher steuerbar ist. Diese Flußsteuervorrichtung 2 ist von einem hydraulischen Antrieb 3 steuerbar. Zu den funktionswesentlichen Teilen dieses Antriebs 3 gehört ein Steuerstößel 4, der Teil eines Steuerkolbens 5 ist, der auf die Flußsteuervorrichtung 2 wirkt. Ist das Ventil 1 ein Lasthalte-Bremsventil, auch Senkbremsventil genannt, so besteht die Flußsteuervorrichtung 2 beispielsweise aus einem Vorsteuer- und einem Hauptventil. Bei anderer Bauart des Ventils 1 sind anders bezeichnete Teile vorhanden. Bei einem Wegeventil gemäß WO-A1-02/075162 wirkt beispielsweise der Steuerstößel 4 direkt auf einen Schieberkolben.In Fig. 1, which is a schematic representation, 1 means a hydraulically controlled valve, which in this embodiment is a load-holding brake valve. This designed as a load-holding brake valve hydraulically controlled valve 1 is shown on the right in a view that reveals no details of the internal structure, because the internal structure is not essential to the invention and in itself from WO-A1-97 / 32136 known. The waiver of the representation of this internal structure is also appropriate because the not essential to the invention parts of the hydraulically controlled valve 1 may well be constructed differently than shown and described in WO-A1-97 / 32136. The invention is therefore independent of a particular type of load-holding brake valve and regardless of the design of the valve 1. It is only essential that the valve 1 is hydraulically controlled by at least one hydraulic drive and that the valve 1 has a flow control device 2 through the flow of hydraulic oil from and to a consumer is controllable. This flow control device 2 is controlled by a hydraulic drive 3. Among the essential functional parts of this drive 3 is a control plunger 4, which is part of a control piston 5, which acts on the flow control device 2. If the valve 1 is a load-holding brake valve, also called a lowering brake valve, the flow control device 2 consists, for example, of a pilot valve and a main valve. In another type of valve 1 are different designated parts available. In a directional control valve according to WO-A1-02 / 075162, for example, the control plunger 4 acts directly on a spool.

Der Steuerkolben 5 ist als Ansicht gezeigt. Erfindungsgemäß ist er als Stufenkolben gestaltet, dessen erfindungsgemäße Merkmale nachstehend beschrieben sind. Zuvor sei erwähnt, daß links am Ventil 1 ein Steuerdruckanschluß X an einem Gehäuseteil 6 vorhanden ist. Am Steuerdruckanschluß X ist im Gehäuseteil 6 eine Bohrung vorhanden, die hier als Steuerdruck-Primärkammer 7 bezeichnet ist.The control piston 5 is shown as a view. According to the invention, it is designed as a stepped piston whose features according to the invention are described below. It should be mentioned in advance that on the left of the valve 1, a control pressure port X is provided on a housing part 6. At the control pressure port X in the housing part 6, a bore is present, which is referred to here as the control pressure primary chamber 7.

Erfindungsgemäß weist der Steuerkolben 5 an seinem dem Steuerdruckanschluß X zugewandten Ende eine erste Stufe 8 auf, deren Durchmesser D8 nur so viel kleiner als der Innendurchmesser der Steuerdruck-Primärkammer 7, daß er sich bewegen läßt. Ein am Steuerdruckanschluß X vorhandener und somit in der Steuerdruck-Primärkammer 7 wirkender Steuerdruck Px übt somit auf den Steuerkolben 5 eine Kraft F aus, die dem Produkt von Steuerdruck Px und der Stirnfläche A8 der ersten Stufe 8 entspricht, wobei die Stirnfläche A8 der ersten Stufe 8 das Produkt aus halbem Durchmesser D8 im Quadrat und π ist. Der Steuerdruck Px bewirkt also eine Kraft F, mit der der Steuerkolben 5 gegen eine Steuerfeder 9 gedrückt wird. Dabei hängt der Weg, den der Steuerkolben 5 zurücklegt, von der Federrate der Steuerfeder 9 ab.According to the invention, the control piston 5 at its the control pressure port X facing the end of a first stage 8, whose diameter D 8 only so much smaller than the inner diameter of the control pressure primary chamber 7, that he can move. A control pressure Px present at the control pressure connection X and thus acting in the control pressure primary chamber 7 thus exerts a force F on the control piston 5 which corresponds to the product of the control pressure P x and the end face A 8 of the first stage 8, the end face A 8 the first stage 8 is the product of half diameter D 8 squared and π. The control pressure P x thus causes a force F, with which the control piston 5 is pressed against a control spring 9. In this case, the path traveled by the control piston 5 depends on the spring rate of the control spring 9.

Erfindungsgemäß weist der Steuerkolben 5 eine zweite Stufe 10 auf, deren Durchmesser D10 größer ist als der Durchmesser D8. Dabei ist der Durchmesser D10 geringfügig kleiner als der Innendurchmesser einer Bohrung im Gehäuseteil 6. Diese Bohrung im Gehäuseteil 6 ist als Steuerdruck-Sekundärkammer 11 bezeichnet. Die hydraulisch zusätzlich wirksame Fläche A10 dieser zweiten Stufe 10 ist ein Kreisring mit dem äußeren Durchmesser D10 und dem inneren Durchmesser D8.According to the invention, the control piston 5 has a second step 10 whose diameter D 10 is greater than the diameter D 8 . In this case, the diameter D 10 is slightly smaller than the inner diameter of a bore in the housing part 6. This bore in the housing part 6 is referred to as control pressure secondary chamber 11. The hydraulically additionally effective area A 10 of the second stage 10 is a circular ring with the outer diameter D 10 and the inner diameter D. 8

Erfindungswesentlich ist, daß die Steuerdruck-Primärkammer 7 und die Steuerdruck-Sekundärkammer 11 durch eine Verbindung 12 mit einer Drosselstelle 13 verbunden sind, was in der Fig. 1 schematisch gezeichnet ist. Unwesentlich ist, ob diese Steuerdruck-Primärkammer 7 und die Steuerdruck-Sekundärkammer 11 durch Bohrungen in einem Gehäuseteil 6 gebildet sind oder ob sie auf andere Weise realisiert sind. Ein alternatives Ausführungsbeispiel wird noch gezeigt werden. Erfindungswesentlich ist lediglich, daß der hydraulische Antrieb 3 die Steuerdruck-Primärkammer 7 und die Steuerdruck-Sekundärkammer 11 aufweist.Essential to the invention is that the control pressure primary chamber 7 and the control pressure secondary chamber 11 are connected by a connection 12 with a throttle point 13, which is shown schematically in FIG. It is irrelevant whether these control pressure primary chamber 7 and the control pressure secondary chamber 11 are formed by bores in a housing part 6 or whether they are realized in another way. An alternative embodiment will be shown. Essential to the invention is only that the hydraulic drive 3, the control pressure primary chamber 7 and the control pressure secondary chamber 11 has.

Bei der nachfolgenden Funktionsbeschreibung wird von einem Gleichgewichtszustand ausgegangen, bei dem aufgrund eines bestimmten Steuerdruckes Px der Steuerkolben 5 eine bestimmte Lage eingenommen hat. Gleichgewichtszustand heißt auch, daß der Steuerdruck Px sowohl in der Steuerdruck-Primärkammer 7 als auch in der Steuerdruck-Sekundärkammer 11 herrscht, weil über die Verbindung 12 mit der Drosselstelle 13 ein Druckausgleich stattgefunden hat. Wird nun der Steuerdruck PX erhöht, so erzeugt dieser eine größere Kraft auf die Stirnfläche A8, was zur Folge hat, daß sich der Steuerkolben 5 nach rechts gegen die Steuerfeder 9 bewegt. Der höhere Steuerdruck PX herrscht in dem Moment aber nur in der Steuerdruck-Primärkammer 7. Wegen der Drosselstelle 13 kann der Druck in der Steuerdruck-Sekundärkammer 11 nicht sogleich auch erhöht sein. Im Gegenteil: Bewirkt der höhere Steuerdruck PX in der Steuerdruck-Primärkammer 7 eine Bewegung des Steuerkolbens 5 nach rechts, so wird zunächst der Druck in der Steuerdruck-Sekundärkammer 11 fallen, was der Bewegung des Steuerkolbens 5 nach rechts entgegen wirkt. Erst dadurch, daß über die Verbindung 12 mit der Drosselstelle 13 Hydrauliköl von der Steuerdruck-Primärkammer 7 in die Steuerdruck-Sekundärkammer 11 nachfließen kann, wird dieser Druckabfall ausgeglichen und durch weiteres Nachfließen von Hydrauliköl wird schließlich erreicht, daß der Druck in der Steuerdruck-Sekundärkamzner 11 genau so groß ist wie der Steuerdruck PX, der auch in der Steuerdruck-Primärkammer 7 herrscht. Dann ist wieder der Gleichgewichtszustand erreicht, bei dem der Steuerkolben 5 eine dem höheren Steuerdruck PX entsprechende neue Lage eingenommen hat.The following description of the function assumes a state of equilibrium in which, due to a specific control pressure P x, the control piston 5 has assumed a specific position. Equilibrium state also means that the control pressure P x both in the control pressure primary chamber 7 and in the control pressure secondary chamber 11 prevails because of the connection 12 with the throttle point 13, a pressure equalization has taken place. If now the control pressure P X is increased, this generates a greater force on the end face A 8 , with the result that the control piston 5 moves to the right against the control spring 9. The higher control pressure P X prevails in the moment but only in the control pressure primary chamber 7. Because of the throttle point 13, the pressure in the control pressure secondary chamber 11 may not be increased immediately. On the contrary, causes the higher control pressure P X in the control pressure primary chamber 7, a movement of the control piston 5 to the right, so initially the pressure in the control pressure secondary chamber 11 fall, which counteracts the movement of the control piston 5 to the right. Only by the fact that via the connection 12 with the throttle body 13 hydraulic oil can flow from the control pressure primary chamber 7 in the control pressure secondary chamber 11, this pressure drop is compensated and by further Nachfließen of hydraulic oil is finally achieved that the pressure in the control pressure Sekundärkamzner 11 is exactly as large as the control pressure P X , which also prevails in the control pressure primary chamber 7. Then the equilibrium state is reached again, in which the control piston 5 has assumed a new position corresponding to the higher control pressure P X.

Im ersten Moment wirkt also ein höherer Steuerdruck PX nur auf die kleinere Stirnfläche A8. Erst nach dem Druckausgleich über Drosselstelle 13 wirkt der höhere Steuerdruck PX auch auf die hydraulisch wirksame Fläche der zweiten Stufe 10, also insgesamt auf eine Fläche A10, die sich aus dem Durchmesser D10 unmittelbar ergibt. Daraus folgt, die Bewegung des Steuerkolbens 5 verzögert, also gedämpft wird. Auf diese Weise wird die Aufgabe der Erfindung auf überraschend einfache Weise gelöst, denn durch diese Dämpfung wird das Ventil 1 gegen intern oder extern ausgelöste Schwingungen unempfindlich, ohne daß die Ansprechempfindlichkeit verschlechtert wird, was bei Anwendung eines Dosierventils gemäß WO-A1-97/32136 nicht auszuschließen wäre.In the first moment, therefore, a higher control pressure P X acts only on the smaller end face A 8 . Only after the pressure equalization via throttle point 13, the higher control pressure P X also acts on the hydraulically effective surface of the second stage 10, ie in total on an area A 10 , which results directly from the diameter D 10 . It follows that the movement of the control piston 5 is delayed, that is damped. In this way, the object of the invention is achieved in a surprisingly simple manner, because by this damping, the valve 1 against internal or external induced vibrations insensitive, without the responsiveness is deteriorated, which is when using a metering valve according to WO-A1-97 / 32136 could not be ruled out.

Der Durchmesser D8 beträgt beispielsweise 14 mm, der Durchmesser D10 20 mm. Die hydraulisch wirksamen Stirnflächen A8 und A10 betragen entsprechend 153,9 bzw. 314,2 mm2, was ein Flächenverhältnis von 1 zu 2,04 ergibt. Dies deutet an, wie groß die Amplitude von ausregelbaren Schwingungen sein kann.The diameter D 8 is for example 14 mm, the diameter D 10 20 mm. The hydraulically effective end faces A 8 and A 10 are respectively 153.9 and 314.2 mm 2 , which gives an area ratio of 1 to 2.04. This indicates how large the amplitude of adjustable vibrations can be.

Bei abnehmendem Steuerdruck PX ist die Dämpfung in analoger Weise wirksam. Wird der Steuerdruck PX verringert, so kann sich der Druck in der Steuerdruck-Sekundärkammer 11 nur dadurch langsam verringern, daß Hydrauliköl über die Verbindung 12 mit der Drosselstelle 13 von der Steuerdruck-Sekundärkammer 11 in die Steuerdruck-Primärkammer 7 abfließt.With decreasing control pressure P X , the damping is effective in an analogous manner. If the control pressure P X is reduced, the pressure in the control-pressure secondary chamber 11 can only be reduced slowly by hydraulic oil flowing via the connection 12 to the throttle point 13 from the control-pressure secondary chamber 11 into the control-pressure primary chamber 7.

Die in WO-A1-97/32136 beschriebenen Maßnahmen zur Verhinderung der Anregung von Schwingungen, beispielsweise die Anwendung einer Düse und eines mittels einer Verstellspindel einstellbaren Dosierventils, sind somit entbehrlich. Insoweit ist die erfindungsgemäße Lösung außerordentlich einfach. Damit entfällt auch im Hinblick auf die jeweilige Anwendung das Erfordernis, die Größe der Düse zu wählen und einzubauen. Zeitraubende Einstellarbeiten des Dosierventils entfallen ebenfalls.The measures described in WO-A1-97 / 32136 for preventing the excitation of vibrations, for example the use of a nozzle and a metering valve which can be adjusted by means of an adjusting spindle, are thus dispensable. In that regard, the solution according to the invention is extremely simple. This eliminates the need to choose and install the size of the nozzle with regard to the respective application. Time-consuming adjustments of the metering valve are also eliminated.

In vorteilhafter Weise kann als Verbindung 12 mit der Drosselstelle 13 die erste Stufe 8 des Steuerkolbens 5 in Verbindung mit der zugehörigen Bohrung im Gehäuseteil 6, die die Steuerdruck-Primärkammer 7 bildet, genutzt werden. Dies ist in der Fig. 2 gezeigt, wobei diese Darstellung im Hinblick auf die Klarheit unmaßstäblich ist. Die Steuerdruck-Primärkammer 7 hat einen Innendurchmesser D7. Die erste Stufe 8 des Steuerkolbens 5 hat, wie schon in Fig. 1 gezeigt, einen Außendurchmesser D8. Somit ergibt sich dazwischen ein Ringspalt 14, dessen Maße durch den Innendurchmesser D7 und den Außendurchmesser D8 gegeben sind. Wenn dieser Ringspalt 14 als Drosselstelle 13 benutzt wird, so hat das einen bemerkenswerten Vorteil. Während sich eine als Drosselstelle 13 benutze Düse durch Schwebstoffablagerungen im Laufe der Zeit verändern kann, so daß sich die Drosselwirkung verändert, wird der Ringspalt 14 durch die Bewegung des Steuerkolbens 5 während der Betriebs des Ventils 1 (Fig. 1) immer wieder von allfälligen Schwebstoffablagerungen gereinigt. Somit bleibt die Drosselwirkung besser konstant.Advantageously, as a connection 12 with the throttle body 13, the first stage 8 of the control piston 5 in conjunction with the associated bore in the housing part 6, which forms the control pressure primary chamber 7, are used. This is shown in Fig. 2, which is not to scale in the light of clarity. The control pressure primary chamber 7 has an inner diameter D 7 . The first stage 8 of the control piston 5 has, as already shown in Fig. 1, an outer diameter D. 8 This results in between an annular gap 14, the dimensions of which are given by the inner diameter D 7 and the outer diameter D 8 . If this annular gap 14 is used as a throttle 13, so that has a remarkable advantage. While a nozzle used as a restrictor 13 may change over time due to particulate deposits, so that the throttling action changes, the annular gap 14 is repeatedly affected by any suspending matter due to the movement of the control piston 5 during operation of the valve 1 (FIG cleaned. Thus, the throttle effect remains better constant.

Da der Ringspalt 14 funktionswesentlich ist, kommt den Toleranzen von Innendurchmesser D7 und Außendurchmesser D8 große Bedeutung zu. Diese Toleranzen werden so gewählt, daß der Ringspalt 14 eine Spalthöhe von vorteilhaft etwa 0,01 mm bis 0,04 mm aufweist. Um dies zu erreichen kann gegebenenfalls eine Paarung von Aufsteuerkolben 5 und Gehäuseteil 6 durch Auswahl von zueinander passenden Fertigungsteilen erfolgen.Since the annular gap 14 is functionally essential, the tolerances of inner diameter D 7 and outer diameter D 8 is of great importance. These tolerances are chosen so that the annular gap 14 has a gap height of advantageously about 0.01 mm to 0.04 mm. In order to achieve this, a pairing of control piston 5 and housing part 6 can optionally be carried out by selecting mutually compatible production parts.

In den Fig. 3a bis 3c ist eine hydraulische Schaltung mit einem Verbraucher 20 gezeigt, der im dargestellten Beispiel ein doppeltwirkender Zylinder mit einem Boden-Druckraum und einem Stangen-Druckraum ist. Anstelle des doppelt wirkenden Zylinders kann aber auch ein Hydromotor als Verbraucher 20 betrieben werden. Die hydraulische Schaltung ist in drei Betriebszuständen gezeigt, nämlich in der Fig. 3a in der Neutralstellung, in der Fig. 3b im lasthebenden Betrieb und in der Fig. 3c im lastsenkenden Betrieb. Die vorhanden Einzelelemente der hydraulischen Schaltung sind in allen Fällen gleich. Die hydraulische Schaltung ist an sich bekannt und wird hier gezeigt, weil sich anhand dieser Schaltung die erfindungsgemäße Wirkung der erfindungsgemäß ausgestalteten hydraulisch gesteuerten Ventile beschreiben läßt.FIGS. 3a to 3c show a hydraulic circuit with a consumer 20, which in the illustrated example is a double-acting cylinder with a bottom pressure chamber and a rod pressure chamber. Instead of the double-acting cylinder but also a hydraulic motor 20 can be operated as a consumer. The hydraulic circuit is shown in three operating states, namely in the neutral position in FIG. 3a, in the load-lifting mode in FIG. 3b and in the load-reducing mode in FIG. 3c. The existing individual elements of the hydraulic circuit are the same in all cases. The hydraulic circuit is known per se and is shown here, because can be described with reference to this circuit, the inventive effect of the inventively designed hydraulically controlled valves.

In allen drei Fig. 3a bis 3c sind ein Wegeventil 21 und ein Lasthaltebremsventil 22 gezeigt, die der Steuerung des Verbrauchers 20 dienen. Das Lasthaltebremsventil 22 kann beispielsweise von der in WO-A1-97/32136 gezeigten Bauart sein, ist aber mit einem erfindungsgemäß ausgestalteten hydraulischen Antrieb 3 ausgestattet. Das Wegeventil 21 kann beispielsweise von einer der in WO-A1-02/075162 gezeigten Bauarten sein, ist aber ebenfalls mit erfindungsgemäß ausgestalteten hydraulischen Antrieben 3' ausgestattet.In all three Figs. 3a to 3c, a directional control valve 21 and a load-holding brake valve 22 are shown, which serve to control the load 20. The load-holding brake valve 22 may, for example, be of the type shown in WO-A1-97 / 32136, but is equipped with a hydraulic drive 3 designed according to the invention. The directional control valve 21 may, for example, be of one of the designs shown in WO-A1-02 / 075162, but is also equipped with hydraulic drives 3 'designed according to the invention.

Das Hydrauliköl ist mittels einer von einem Motor 23 angetriebenen Pumpe 24 zwischen dem Tank 25 und dem Verbraucher 20 förderbar. Der Pumpe 24 sind in bekannter Weise ein erstes Rückschlagventil 26 und ein Druckbegrenzungsventil 27 zugeordnet. Der Fluß des Hydraulilöls wird dabei bestimmt durch die Stellungen des Wegeventils 21 und des Lasthaltebremsventils 22. In einer Leitung zum Boden-Druckraum des Verbrauchers 20 ist ein zweites Rückschlagventil 28 angeordnet. Dieses separate Rückschlagventil 28 kann dann entfallen, wenn das Lasthalte-Bremsventil 22 ein solches Rückschlagventil beinhaltet, was in der Darstellung des Lasthalte-Bremsventils 22 mit der Bezugszahl 28' bezeichnet ist.The hydraulic oil can be conveyed between the tank 25 and the consumer 20 by means of a pump 24 driven by a motor 23. The pump 24 are associated in a known manner, a first check valve 26 and a pressure relief valve 27. The flow of the hydraulic oil is determined by the positions of the directional control valve 21 and the load-holding brake valve 22. In a line to the bottom pressure chamber of the consumer 20, a second check valve 28 is arranged. This separate check valve 28 can be omitted if the load-holding brake valve 22 includes such a check valve, which is in the representation of the load-holding brake valve 22 by the reference numeral 28 'is designated.

Das Wegeventil 21 wird in bekannter Weise dadurch gesteuert, daß dessen beide Antriebe 3' ansteuerbar sind. Ist keiner der Antriebe 3' angesteuert, d.h. mit einem Steuerdruck PSt beaufschlagt, so nimmt das Wegeventil 21 die Neutralstellung ein.The directional control valve 21 is controlled in a known manner that its two drives 3 'are controlled. If none of the drives 3 'are actuated, ie acted upon by a control pressure P St , the directional control valve 21 assumes the neutral position.

In der in der Fig. 3a gezeigten Neutralstellung des Wegeventils 21 ist im Wegeventil 21 die Verbindung zwischen der Pumpe 24, dem Boden-Druckraum des Verbrauchers 20, dem Stangen-Druckraum des Verbrauchers und dem Rückfluß zum Tank 25 offen. Dies gilt nicht generell und ist beispielsweise beim Wegeventil gemäß WO-A1-02/075162 anders. Darauf kommt es aber im Hinblick auf die Erfindung nicht an. Für die vorliegende Schaltung ist im Hinblick auf korrekte Steuerung des Verbrauchers 20 nur bedeutsam, daß in der Neutralstellung das Lasthaltebremsventil 22 geschlossen ist, so daß der Verbraucher 20 in seiner Stellung verbleibt. Daß das Lasthaltebremsventil 22 geschlossen bleibt, ergibt sich unmittelbar daraus, daß der Steuerdruck PX (Fig. 1) etwa dem Druck im Stangen-Druckraum des Verbrauchers 20 entspricht, der seinerseits etwa dem atmosphärischen Druck entspricht, weil die Verbindung zum Tank 25 offen ist.In the neutral position of the directional control valve 21 shown in Fig. 3a is in the directional control valve 21, the connection between the pump 24, the bottom pressure chamber of the consumer 20, the rod pressure chamber of the consumer and the reflux to the tank 25 open. This does not apply generally and is different for example in the directional control valve according to WO-A1-02 / 075162. However, this is not important with regard to the invention. For the present circuit, with regard to correct control of the load 20, it is only significant that in the neutral position the load-holding brake valve 22 is closed so that the load 20 remains in its position. The fact that the load-holding brake valve 22 remains closed results directly from the fact that the control pressure P X (FIG. 1) corresponds approximately to the pressure in the rod pressure chamber of the consumer 20, which in turn corresponds approximately to the atmospheric pressure because the connection to the tank 25 is open ,

In der Fig. 3b ist der lasthebende Betrieb gezeigt. Erreicht wird dies dadurch, daß der eine der Antriebe 3' des Wegeventils 21 mit einem Steuerdruck PSt angesteuert wird. Der Schieberkolben des Wegeventils 21 wird dadurch so bewegt, daß der Fluß von Hydrauliköl von der Pumpe 24 durch das Wegeventil 21 zum Boden-Druckraum des Verbrauchers 20 sowie vom Stangen-Druckraum des Verbrauchers 20 zum Tank 25 möglich ist. Die Pumpe 24 fördert also Hydrauliköl aus dem Tank 25 zur Bodenseite des Verbrauchers 20, wobei das erste Rückschlagventil 26 sowie das zweiteIn Fig. 3b, the load-lifting operation is shown. This is achieved in that the one of the drives 3 'of the directional control valve 21 is driven with a control pressure P St. The spool of the directional control valve 21 is thereby moved so that the flow of hydraulic oil from the pump 24 through the directional control valve 21 to the bottom pressure chamber of the consumer 20 and from the rod pressure chamber of the consumer 20 to the tank 25 is possible. The pump 24 thus delivers hydraulic oil from the tank 25 to the bottom side of the consumer 20, wherein the first check valve 26 and the second

Rückschlagventil 28 bzw. das Rückschlagventil 28' durch den Pumpendruck automatisch aufgesteuert werden. Dadurch, daß Hydrauliköl zum Boden-Druckraum des Verbrauchers 20 gefördert wird, wird gleichzeitig Hydrauliköl aus dem Stangen-Druckraum des Verbrauchers 20 verdrängt, das über das Wegeventil 21 zum Tank 25 abfließt. Das Lasthaltebremsventil 22 ist funktionslos. Dies steht damit im Zusammenhang, daß der wirksame Steuerdruck PX sehr klein ist, denn das Hydrauliköl fließt von der Stangenseite des Verbrauchers 20 zum drucklosen Tank 25 ab, wie dies bei der Neutralstellung erläutert worden ist. Damit bleibt auch die schwingungsdämpfende Wirkung des Antriebs 3 des Lasthaltebremsventils 22 wirkungslos.Check valve 28 and the check valve 28 'are automatically controlled by the pump pressure. Characterized in that hydraulic oil is conveyed to the bottom pressure chamber of the consumer 20, hydraulic oil is simultaneously displaced from the rod-pressure chamber of the consumer 20, which flows through the directional control valve 21 to the tank 25. The load-holding brake valve 22 is inoperative. This is related to the fact that the effective control pressure P X is very small, because the hydraulic oil flows from the rod side of the consumer 20 to the unpressurized tank 25, as has been explained in the neutral position. Thus, the vibration damping effect of the drive 3 of the load-holding brake valve 22 is ineffective.

Sind die Antriebe 3' des Wegeventils 21 erfindungsgemäß gestaltet, so entfalten diese die beschriebene dämpfende Wirkung, was dann vorteilhaft ist, wenn der Steuerdruck PSt, wie vielfach üblich, aus dem Lastdruck am Verbraucher 20 oder aus dem Pumpendruck abgeleitet ist. Schwankungen dieses Last- bzw. Pumpendrucks werden also im Antrieb 3' des Wegeventils gedämpft. Die vorteilhafte Wirkung der Dämpfung tritt auch dann auf, wenn im lasthebenden Betrieb der Verbraucher 20 bzw. die von ihm angetriebene Vorrichtung, beispielsweise gegen ein Hindernis läuft, wodurch der Lastdruck sich momentan ändert.Are the drives 3 'of the directional control valve 21 designed according to the invention, they unfold the described damping effect, which is advantageous if the control pressure P St , as often customary, is derived from the load pressure at the load 20 or from the pump pressure. Variations in this load or pump pressure are thus damped in the drive 3 'of the directional control valve. The advantageous effect of damping occurs even when in load-lifting operation, the consumer 20 or the device driven by it, for example, runs against an obstacle, whereby the load pressure changes momentarily.

In der Fig. 3c ist der lastsenkende Betrieb gezeigt. Hierbei fördert die Pumpe 24 Hydrauliköl zum Stangen-Druckraum des Verbrauchers 20. Erreicht wird dies dadurch, daß nun der andere Antrieb 3' des Wegeventils 21 mit einem Steuerdruck PSt beaufschlagt wird. Dadurch ist im Wegeventil 21 die Verbindung von der Pumpe 24 zum Stangen-Druckraum des Verbrauchers 20 offen und außerdem die Verbindung vom Boden-Druckraum des Verbrauchers 20 zum Tank 24. Der am Lasthalte-Bremsventil 22 wirksame Steuerdruck PX ist nun hoch. Er ist bestimmt durch den von der Pumpe erzeugten Druck und den Druckverlust über dem Wegeventil 21.In Fig. 3c, the load lowering operation is shown. Here, the pump 24 delivers hydraulic oil to the rod-pressure chamber of the consumer 20. This is achieved in that now the other drive 3 'of the directional control valve 21 is acted upon by a control pressure P St. As a result, in the directional control valve 21, the connection from the pump 24 to the rod pressure chamber of the consumer 20 is open and also the connection from the bottom pressure chamber of the consumer 20 to the tank 24. The control pressure P X acting on the load-holding brake valve 22 is now high. It is determined by the pressure generated by the pump and the pressure loss across the directional control valve 21.

Weil Hydrauliköl zum Stangen-Druckraum des Verbrauchers 20 strömt, muß nun Hydrauliköl vom Boden-Druckraum des Verbrauchers 20 zum Tank 24 abfließen. Das zweite Rückschlagventil 28, das parallel zum Lasthalte-Bremsventil 22 angeordnet ist, bzw. das Rückschlagventil 28' ist jedoch in diesem Lastfall geschlossen. Hydrauliköl kann also nur dann aus dem Boden-Druckraum des Verbrauchers 20 abfließen, wenn das Lasthalte-Bremsventil 22 geöffnet wird. Dies geschieht durch den Steuerdruck PX, der sich aufgrund der proportionalen Verstellung des Wegeventils 21 durch den Steuerdruck PSt einstellt. Damit wird in bekannter Weise erreicht, daß aus dem Boden-Druckraum des Verbrauchers 20 das Hydrauliköl abfließen kann. Diese aus dem Verbraucher 20 abfließende Menge ist größer als die gleichzeitig in den Stangen-Druckraum einfließende Menge, weil die Querschnitte auf der Stangenseite und auf der Bodenseite unterschiedlich groß sind.Since hydraulic oil flows to the rod pressure chamber of the consumer 20, hydraulic oil must now flow from the bottom pressure chamber of the consumer 20 to the tank 24. However, the second check valve 28, which is arranged parallel to the load-holding brake valve 22, or the check valve 28 'is closed in this load case. Hydraulic oil can therefore only flow out of the bottom pressure chamber of the consumer 20 when the load-holding brake valve 22 is opened. This is done by the control pressure P X , which is adjusted by the control pressure P St due to the proportional adjustment of the directional control valve 21. This is achieved in a known manner that from the bottom pressure chamber of the consumer 20, the hydraulic oil can flow. This effluent from the consumer 20 amount is greater than the same time in the rod pressure chamber inflowing amount, because the cross sections on the rod side and on the bottom side are different in size.

In diesem Betriebzustand kommt nun die erfindungsgemäße Wirkung der Gestaltung des Antriebs 3 des Lasthalte-Bremsventils 22 zur Geltung. Wird der Steuerdruck PSt sehr schnell erhöht, so erhöht sich auch der Steuerdruck PX sehr schnell. Die schnelle Erhöhung des Steuerdruck PSt könnte Schwingungen am Verbraucher 20 auslösen, doch wird diese Schwingung durch die erfinderungsgemäße Gestaltung des Antriebs 3 des Lasthalte-Bremsventils 22 stark gedämpft.In this operating state, the effect according to the invention of the design of the drive 3 of the load-holding brake valve 22 now comes into its own. If the control pressure P St is increased very rapidly, the control pressure P X also increases very rapidly. The rapid increase of the control pressure P St could trigger vibrations at the load 20, but this vibration is greatly attenuated by the inventive design of the drive 3 of the load-holding brake valve 22.

Sind auch die Antriebe 3' des Wegeventils 21 erfindungsgemäß gestaltet, so wirkt dieser dämpfend hinsichtlich der Wirkung des Steuerdrucks PSt auf das Wegeventil 21, was zur Folge hat, daß auch dadurch die Neigung zu Schwingungen am Verbraucher 20 eliminiert wird. Schwingungen am Verbraucher 20 durch schnelle Erhöhung des Steuerdrucks PSt können so gar nicht erst entstehen. Schwingungen, die durch wechselnde Last am Verbraucher 20 angeregt werden, werden aber gleichzeitig durch den Antrieb 3 des Lasthalte-Bremsventils 22 gedämpft.Are the drives 3 'of the directional control valve 21 designed according to the invention, so this acts dampening with respect to the effect of the control pressure P St on the directional control valve 21, with the result that also by the tendency to oscillations on the consumer 20 is eliminated. Vibrations at the consumer 20 due to rapid increase of the control pressure P St can not arise in the first place. Vibrations, which are excited by changing load on the consumer 20, but are simultaneously damped by the drive 3 of the load-holding brake valve 22.

Dieses Beispiel zeigt, daß die erfindungsgemäße Gestaltung des Antriebs 3 beim Lasthalte-Bremsventil 22 Schwingungen beim lastsenkenden Betrieb verhindern kann. Wird die erfindungsgemäße Gestaltung, die an sich zunächst nur für die Anwendung bei einem Lasthalte-Bremsventil 22 gedacht war, auch bei den hydraulischen Antrieben 3' des Wegeventils 21 angewendet, ergibt sich auch dadurch eine wirksame Dämpfung. Es ist also vorteilhaft, auch die Antriebe 3' des Wegeventils 21 nach der Lehre der Erfindung zu gestalten.This example shows that the inventive design of the drive 3 in the load-holding brake valve 22 can prevent vibrations during load-lowering operation. If the design according to the invention, which was initially intended only for use with a load-holding brake valve 22, is also used in the hydraulic drives 3 'of the directional control valve 21, this also results in effective damping. It is therefore advantageous to design the drives 3 'of the directional valve 21 according to the teaching of the invention.

In der Fig. 4 ist eine vorteilhafte Ausgestaltung eines Antriebs 3 gezeigt, die bei einem Lasthalte-Bremsventil 22 (Fig. 3a bis 3c) zur Anwendung kommen kann. Die Fig. 4 entspricht an sich der Fig. 1, enthält aber darüber hinaus diese vorteilhafte Ausgestaltung. Diese besteht darin, daß zwischen der Steuerdruck-Primärkammer 7 und der Steuerdruck-Sekundärkammer 11 ein Entlastungs-Rückschlagventil 30 angeordnet ist. Dieses ermöglicht den Druckabbau von der Steuerdruek-Sekundärkammer 11 zur Steuerdruck-Primärkammer 7 hin, wobei die Druckdifferenz, bei der das Entlastungs-Rückschlagventil 30 öffnet, durch eine Feder 31 bestimmt ist.FIG. 4 shows an advantageous embodiment of a drive 3 which can be used in the case of a load-holding brake valve 22 (FIGS. 3 a to 3 c). Fig. 4 corresponds to the Fig. 1, but also contains this advantageous embodiment. This is that between the control pressure primary chamber 7 and the control pressure secondary chamber 11, a relief check valve 30 is arranged. This allows the pressure reduction from the Steuerdruek secondary chamber 11 to the control pressure primary chamber 7 out, the pressure difference at which the relief check valve 30 opens, is determined by a spring 31.

Dieses Entlastungs-Rückschlagventil 30 hat die nachfolgend beschriebene Wirkung. Wird der Steuerdruck PX verringert, wie dies anfänglich schon erwähnt wurde, so wird durch die Wirkung der Steuesfeder 9 der Steuerkolben 5 nach links bewegt. Das bedeutet zunächst, daß der Druck in der Steuerdruck-Sekundärkammer 11 nicht sogleich fallen kann. Der Druckabfall kann erst unter der Wirkung der Verbindung 12 mit der Drosselstelle 13 eintreten. Im lasthebenden Zustand gemäß Fig. 3b hat aber, wie zuvor ausgeführt, das Lasthalte-Bremsventil 22 keine Wirkung. Es ist deshalb gar nicht sinnvoll, wenn in diesem Betriebszustand der dämpfende Wirkung durch die erfindungsgemäße Ausgestaltung des Antriebs 3 eintritt. Durch das Entlastungs-Rückschlagventil 30 wird dies erreicht.This relief check valve 30 has the effect described below. If the control pressure P X is reduced, as has already been mentioned initially, the control piston 5 is moved to the left by the action of the control spring 9. This means first that the pressure in the control pressure secondary chamber 11 can not fall immediately. The pressure drop can only under the effect of compound 12 with the Throttling point 13 occur. In the load-lifting state according to FIG. 3b, however, as previously stated, the load-holding brake valve 22 has no effect. It is therefore not useful if the damping effect occurs in this operating state by the inventive design of the drive 3. By the relief check valve 30, this is achieved.

In der Fig. 5, die an sich der Fig. 4 entspricht, bei der aber anstelle der Verbindung 12 mit der Drosselstelle 13 der Ringspalt 14 gezeigt ist, ist als zusätzliche vorteilhafte Ausgestaltung gezeigt, daß in der zylindrischen Mantelfläche der ersten Stufe 8 am der Steuerdruck-Sekundärkammer 11 zugewandten Ende eine Längsnut 33 eingestochen ist. Durch diese Maßnahme wird die wirksame Länge des Ringspalts 14 begrenzt, der Fluß des Hydrauliköls zwischen der zur Steuerdruck-Primärkammer 7 und der Steuerdruck-Sekundärkammer 11 erleichtert und somit die Wirkung der Dämpfung begrenzt. Auf diese Weise läßt sich die Dämpfungswirkung eines Ventils 1 im Hinblick auf die jeweilige Anwendung sehr einfach anpassen, indem die Länge der Längsnut 33 je nach Anwendung unterschiedlich gewählt wird.In Fig. 5, which in itself corresponds to FIG. 4, but in which instead of the connection 12 with the throttle point 13 of the annular gap 14 is shown, it is shown as an additional advantageous embodiment that in the cylindrical surface of the first stage 8 at the Control pressure secondary chamber 11 facing a longitudinal groove 33 is inserted. By this measure, the effective length of the annular gap 14 is limited, the flow of hydraulic oil between the control pressure primary chamber 7 and the control pressure secondary chamber 11 facilitates and thus limits the effect of the damping. In this way, the damping effect of a valve 1 with respect to the particular application can be very easily adjusted by the length of the longitudinal groove 33 is chosen differently depending on the application.

In der Fig. 6 ist eine weitere vorteilhafte Ausgestaltung eines Antriebs 3 gezeigt, die bei einem Lasthalte-Bremsventil 22 (Fig. 3a bis 3c) zur Anwendung kommen kann. Hier ist das in der Fig. 4 und 5 gezeigte Entlastungs-Rückschlagventil 30 unmittelbar in den Antrieb 3 integriert. Dargestellt sind nur die erfindungsgemäßen funktionswichtigen Teile, nicht hingegen beispielsweise jene Teile, die der Kraftübertragung auf die zu betätigende Flußsteuervornchtung 2 (Fig. 1) dienen, ebenso nicht die Steuerfeder 9 (Fig 1).FIG. 6 shows a further advantageous embodiment of a drive 3 which can be used in the case of a load-holding brake valve 22 (FIGS. 3 a to 3 c). Here, the relief check valve 30 shown in FIGS. 4 and 5 is integrated directly into the drive 3. Shown are only the functionally important parts according to the invention, but not, for example, those parts that serve the power transmission to the operated Flußsteuervornchtung 2 (Fig. 1), not the control spring 9 (Figure 1).

Gezeigt ist der Steuerkolben 5 mit seiner ersten Stufe 8 und seiner zweiten Stufe 10, die, wie zuvor gezeigt, die Durchmesser D8 bzw. D10 aufweisen. Dargestellt sind auch die Steuerdruck-Primärkammer 7 und die Steuerdruck-Sekundärkammer 11. Abweichend von der Fig. 5 ist bei diesem Ausführungsbeispiel das Entlastungs-Rückschlagventil 30 innerhalb des hydraulischen Antriebs 3 angeordnet. Dabei weist im Gegensatz zu den Ausführungen gemäß den Figuren 1, 4 und 5 der hydraulische Antrieb 3 kein besonderes Gehäuseteil 6 auf. Vielmehr wird der hydraulische Antrieb 3 innerhalb des Gehäuses des zu steuernden Ventils 1 (Fig. 1) angeordnet, wobei dieses Gehäuse in der Fig. 6 mit der Bezugszahl 40 bezeichnet ist. In das nach links offene Gehäuse 40 ist ein Deckel 41 einschraubbar. In diesem Deckel 41 befindet sich eine Öffnung, die den Steuerdruckanschluß X darstellt, der, wie auch bei den vorherigen Ausführungsbeispielen, mit der Steuerdruck-Primärkammer 7 verbunden ist.Shown is the control piston 5 with its first stage 8 and its second stage 10, which, as previously shown, the diameter D 8 and D 10 have. Also shown are the control pressure primary chamber 7 and the control pressure secondary chamber 11. Notwithstanding FIG. 5, in this exemplary embodiment the relief check valve 30 is arranged within the hydraulic drive 3. In contrast to the embodiments according to FIGS. 1, 4 and 5, the hydraulic drive 3 has no special housing part 6. Instead, the hydraulic drive 3 is arranged inside the housing of the valve 1 to be controlled (FIG. 1), this housing being designated by the reference numeral 40 in FIG. In the left open housing 40, a lid 41 is screwed. In this cover 41 is an opening which represents the control pressure port X, which, as in the previous embodiments, is connected to the control pressure primary chamber 7.

Vorteilhaft ist hier nun zwischen dem Steuerdruckanschluß X und der Steuerdruck-Primärkammer 7 eine Blende 42 angeordnet, nämlich innerhalb des Deckels 41. Durch diese Blende 42 wird eine Begrenzung des Durchflusses erreicht. Dies hat zur Folge, daß bei schnell ansteigendem Steuerdruck PX der Anstieg des Druckes in der Steuerdruck-Primärkammer 7 verzögert wird. Da diese Verzögerung des Druckanstiegs eine Dämpfung bedeutet, bedeutet dies eine vorteilhafte zusätzliche Maßnahme im Hinblick auf die Lösung der Aufgabe.Advantageously, an aperture 42 is now arranged between the control pressure connection X and the control pressure primary chamber 7, namely within the cover 41. Through this aperture 42, a limitation of the flow is achieved. This has the consequence that at rapidly increasing control pressure P X, the increase in the pressure in the control pressure primary chamber 7 is delayed. Since this delay of the pressure increase means a damping, this means an advantageous additional measure with regard to the solution of the problem.

Da die erfindungsgemäße Dämpfung durch die Drosselstelle 13 (Fig. 1) bzw. den Ringspalt 14 erfolgt und die Dämpfung durch die Blende 42 zusätzlich wirkt, ist es vorteilhaft, wenn die Dämpfung durch die Blende 42 deutlich geringer ist als die Dämpfung durch die Drosselstelle 13 (Fig. 1) bzw. den Ringspalt 14. Es hat sich herausgestellt, daß sich eine optimale Wirkung dann ergibt, wenn beispielsweise der Ringspalt 14 so bemessen ist, daß er einer Düse von 0,1 mm Durchmesser entspricht, während die Blende 42 einem Düsendurchmesser von 0,3 bis 0,6 mm entspricht. Bei einem Durchmesserverhältnis von 1:3 bis 1:6 ergibt sich ein Flächenverhältnis von 1:9 bis 1:36. Dies zeigt deutlich, daß die Dämpfung durch die Drosselstelle 13 (Fig. 1) bzw. den Ringspalt 14 dominierend ist. Durch die Blende 42 wird eine weitere Verbesserung erreichtSince the damping according to the invention by the throttle point 13 (FIG. 1) or the annular gap 14 and the damping by the aperture 42 additionally acts, it is advantageous if the attenuation by the aperture 42 is significantly lower than the damping by the throttle 13 It has been found that an optimal effect then results if, for example, the annular gap 14 is dimensioned so that it corresponds to a nozzle of 0.1 mm diameter, while the diaphragm 42 a Nozzle diameter of 0.3 to 0.6 mm corresponds. With a diameter ratio of 1: 3 to 1: 6 results in an area ratio of 1: 9 to 1:36. This clearly shows that the damping through the throttle point 13 (FIG. 1) or the annular gap 14 is dominant. Through the aperture 42, a further improvement is achieved

Das in den hydraulischen Antrieb 3 integrierte Entlastungs-Rückschlagventil 30 wird gebildet durch eine gegen eine Sitzfläche 44 dichtende Rückschlagscheibe 45, wobei diese durch die schon in Fig. 4 und 5 gezeigte Feder 31 gegen die Sitzfläche 44 gedrückt wird. Die Rückschlagscheibe 45 weist eine zentrale Bohrung 46 auf. Innerhalb dieser Bohrung 46 befindet sich jener Teil des Steuerkolbens 5, der die erste Stufe 8 bildet. Der Ringspalt 14 wird somit einerseits begrenzt durch diese Bohrung 46 und andererseits durch den Durchmesser D8 der ersten Stufe 8 des Steuerkolbens 5. Hinsichtlich der Dimensionierung des Ringspalts 14 sind die schon erwähnten Regeln anwendbar. Die Funktion dieses Entlastungs-Rückschlagventils 30 ist zuvor schon beschrieben worden. In der Fig. 6 ist die Schließstellung gezeigt. Das Entlastungs-Rückschlagventil 30 öffnet, wenn der Steuerdruck PX verringert wird, wie dies schon im Zusammenhang mit der Fig. 4 beschrieben worden ist. Die Rückschlagscheibe 45 bewegt sich dann gegen die Feder 31 nach links, hebt also von der Sitzfläche 44 ab. Damit kann Hydrauliköl direkt aus der Steuerdruck-Sekundärkammer 11 in die Steuerdruck-Primärkammer 7 fließen.The relief check valve 30 integrated in the hydraulic drive 3 is formed by a non-return plate 45 which seals against a seat surface 44 and is pressed against the seat surface 44 by the spring 31 already shown in FIGS. 4 and 5. The check disc 45 has a central bore 46. Within this bore 46 is that part of the control piston 5, which forms the first stage 8. The annular gap 14 is thus limited on the one hand by this bore 46 and on the other hand by the diameter D 8 of the first stage 8 of the control piston 5. With regard to the dimensioning of the annular gap 14, the rules already mentioned are applicable. The function of this relief check valve 30 has been previously described. 6, the closed position is shown. The relief check valve 30 opens when the control pressure P X is reduced, as has already been described in connection with FIG. 4. The check disc 45 then moves against the spring 31 to the left, so lifts off from the seat 44. Thus, hydraulic oil can flow directly from the control pressure secondary chamber 11 into the control pressure primary chamber 7.

Wie in der Fig. 5 gezeigt, liegt das Entlastungs-Rückschlagventil 30 parallel zum Ringspalt 14 zwischen der Steuerdruck-Primärkammer 7 und der Steuerdruck-Sekundärkammer 11. Das ist auch beim Ausführungsbeispiel der Fig. 6 so. Die Konstruktion gemäß Fig. 6 ergibt vorteilhaft eine kompakte Bauweise.As shown in Fig. 5, the relief check valve 30 is parallel to the annular gap 14 between the control pressure primary chamber 7 and the control pressure secondary chamber 11. This is also in the embodiment of FIG. 6 so. The construction according to FIG. 6 advantageously results in a compact construction.

Die Erfindung ist bei allen Bauarten von hydraulisch gesteuerten Ventilen 1 anwendbar, wenn aufgrund der Ansteuerung und/oder der vom Verbraucher 20 betriebenen Einrichtung wie etwa Kran, oder Schaufellader das Entstehen von Schwingungen nicht auszuschließen ist.The invention is applicable to all types of hydraulically controlled valves 1, if due to the control and / or powered by the consumer 20 Device such as a crane, or a shovel, the occurrence of vibrations can not be excluded.

Claims (10)

  1. Hydraulically controlled valve (1) with at least one hydraulic drive (3, 3') provided with a control piston (5), to which a control plunger (4) is connected, which acts on a flow-control device (2) of the valve (1), by means of which the flow of hydraulic oil from and/or to a consumer (20) can be controlled, where the control piston (5) can be moved by a control pressure PX present in a control pressure connection (X) against a the force of a control spring (9), characterized in that
    - the control piston (5) is a stepped piston,
    - which has a first step (8) with a diameter D8, its end surface A8 being subjected directly to the control pressure PX; and
    - which has a second step (10) with a diameter D10 and a hydraulically active end surface A10;

    in that
    - the hydraulic drive (3, 3') has a primary control pressure chamber (7) and a secondary control pressure chamber (11),
    - where the end surface A8 of the first step (8) is subjected to the pressure in the primary control pressure chamber (7), and
    - the end surface A10 of the second step (10) is subjected to the pressure in the secondary control pressure chamber (11);

    and in that
    - a connection (12) containing a throttle point (13) is present between the primary control pressure chamber (7) and the secondary control pressure chamber (11).
  2. Valve (1) according to Claim 1, characterized in that the connection (12) containing the throttle point (13) is formed by a ring-shaped gap (14), which is defined by the inside diameter of the primary control pressure chamber (7) and the diameter D8 of the first step (8) of the control piston (5).
  3. Valve (1) according to Claim 2, characterized in that the ring-shaped gap (14) has a width of 0.01-0.04 mm.
  4. Valve (1) according to Claim 2 or Claim 3, characterized in that the valve (1) is a load-holding brake valve (22).
  5. Valve (1) according to Claim 2 or Claim 3, characterized in that the valve is a directional control valve (21).
  6. Valve (22) according to Claim 4, characterized in that a pressure relief check valve (30) is installed between the primary control pressure chamber (7) and the secondary control pressure chamber (11) to release the pressure from the secondary control pressure chamber (11) to the primary control pressure chamber (7).
  7. Valve (22) according to Claim 6, characterized in that the pressure difference at which the pressure relief check valve (30) opens can be determined by a spring (31).
  8. Valve (1, 21, 22) according to one of Claims 3-7, characterized in that a longitudinal groove (33) is cut into the cylindrical lateral surface of the first stage (8) at the end facing the secondary control pressure chamber (11).
  9. Valve (22) according to Claim 6 or Claim 7, characterized in that the pressure relief check valve (30) is located inside the hydraulic drive (3) between the primary control pressure chamber (7) and the secondary control pressure chamber (11).
  10. Valve (22) according to Claim 9, characterized in that an orifice (42) is installed between the control pressure connection (X) and the primary control pressure chamber (7).
EP04738137A 2003-08-27 2004-08-10 Hydraulically controlled valve comprising at least one hydraulic drive unit Revoked EP1540191B1 (en)

Applications Claiming Priority (3)

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CH14652003 2003-08-27
CH146503 2003-08-27
PCT/CH2004/000498 WO2005021978A1 (en) 2003-08-27 2004-08-10 Hydraulically controlled valve comprising at least one hydraulic drive unit

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EP1540191A1 EP1540191A1 (en) 2005-06-15
EP1540191B1 true EP1540191B1 (en) 2006-01-11

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US (1) US20060011875A1 (en)
EP (1) EP1540191B1 (en)
JP (1) JP2006515661A (en)
AT (1) ATE315729T1 (en)
DE (2) DE20314232U1 (en)
WO (1) WO2005021978A1 (en)

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CN111397894A (en) * 2020-04-24 2020-07-10 刘勇 Pollution tolerance test system for gear shifting constant pressure valve

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JP6910446B2 (en) * 2016-09-21 2021-07-28 クノル−ブレムゼ ジステーメ フューア ヌッツファールツォイゲ ゲゼルシャフト ミット ベシュレンクテル ハフツングＫｎｏｒｒ−Ｂｒｅｍｓｅ Ｓｙｓｔｅｍｅ ｆｕｅｒ Ｎｕｔｚｆａｈｒｚｅｕｇｅ ＧｍｂＨ Minimum pressure valve for screw compressors for vehicles, especially commercial vehicles
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DE20314232U1 (en) 2004-10-21
US20060011875A1 (en) 2006-01-19
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WO2005021978A1 (en) 2005-03-10
ATE315729T1 (en) 2006-02-15
EP1540191A1 (en) 2005-06-15

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