EP1872018A1 - Pilot valve for a hydraulic motor - Google Patents

Pilot valve for a hydraulic motor

Info

Publication number
EP1872018A1
EP1872018A1 EP05804312A EP05804312A EP1872018A1 EP 1872018 A1 EP1872018 A1 EP 1872018A1 EP 05804312 A EP05804312 A EP 05804312A EP 05804312 A EP05804312 A EP 05804312A EP 1872018 A1 EP1872018 A1 EP 1872018A1
Authority
EP
European Patent Office
Prior art keywords
control
valve
groove
bore
control valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05804312A
Other languages
German (de)
French (fr)
Other versions
EP1872018B1 (en
Inventor
Markus Eschweiler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bucher Hydraulics AG
Original Assignee
Bucher Hydraulics AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bucher Hydraulics AG filed Critical Bucher Hydraulics AG
Publication of EP1872018A1 publication Critical patent/EP1872018A1/en
Application granted granted Critical
Publication of EP1872018B1 publication Critical patent/EP1872018B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]

Definitions

  • the invention relates to a control valve for a hydraulic motor according to the preamble of claim 1.
  • Hydromotors are used, for example, in cranes for driving hydraulic winches. With such a winch, loads can be lifted and lowered.
  • a hydraulic directional control valve which allows a load pressure independent control of a hydraulic motor.
  • DE-C2-41 36 991 a directional valve is known, which can be used for the same purpose.
  • the invention has for its object to provide a control valve which prevents the previously described torque fluctuations and pulsations without the need for an additional valve assembly, which was previously used to reduce the pulsation or torque fluctuation.
  • 1 shows a diagram of a control for a hydraulic motor
  • 2 shows a valve assembly as an additional unit for the function "lifting" according to a solution according to the prior art
  • Fig. 3. is a view of a spool within a valve body
  • Fig. 4 to 7 sections of the position of the spool relative to a control edge.
  • a hydraulic motor 1 which drives a not shown in detail winch for lifting and lowering a load 2.
  • Arrows on the hydraulic motor 1 is shown that the one direction of rotation of the hydraulic motor 1 causes the lowering of the load 2, the opposite direction of rotation of the hydraulic motor 1, the lifting of the load.
  • the hydraulic motor 1 is controllable by a control valve 3 designed as a directional control valve with the usual load connections A and B and with a pump connection P and a tank connection T. This corresponds to the known prior art. This also applies to an inserted into the supply line to the hydraulic motor 1 load-holding valve 4, which serves to control the load during lowering.
  • a hydraulic motor 1 comes in such applications preferably a Hubverdrängermaschine used, for example, an axial piston machine, as shown in "Dubbel: Taschenbuch for mechanical engineering", Springer-Verlag, 19th edition, on page H5.
  • this widespread type of machine has the disadvantage that the flow is not uniform, because this has a considerable degree of non-uniformity ⁇ . It may even follow that at the beginning of the Lifting the load 2, so at very low speed of the hydraulic motor 1, the load 2 drops briefly. This also applies when reducing the speed to stop the load 2. A rational work is hardly possible and there are dangerous moments.
  • valve assembly 10 for example, in the corresponding return line from the hydraulic motor 1, as shown in FIG.
  • the B-line valve assembly 10 which consists of two mutually parallel check valves, namely a biased check valve 11 and a non-biased check valve 12.
  • the applicant itself has created in 2001 such a valve assembly.
  • the hydraulic oil flowing from the hydraulic motor 1 to the control valve 3 must pass through the valve assembly 10.
  • a solution with such an additional valve assembly 10 is complicated to manufacture and expensive and requires space. But the invention is also particularly the object of improving such a solution in terms of functionality.
  • Fig. 3 is a view of a spool 20 is shown within a valve body 21, which are the control valve 3 associated.
  • the spool 20 is axially displaceable, which is indicated by a double arrow.
  • the axial displaceability is effected, as usual in such proportionally operating control valves, by means of at least one drive, wherein electrical, hydraulic or pneumatic drives find uses. Since in the present case, the number and type of drive for the spool 20 does not matter, such a drive has not been shown in the figure.
  • transverse bores are present in the valve body 21, which lead up to the longitudinal bore 22.
  • each of the working connection bores A, B must be operationally connectable to the tank connection bore T or to the pump connection bore P in order to enable "lifting" and "sinking" operation.
  • the spool 20 has, in order to produce the various connections between the terminal bores T, B, P, A and T, profiled annular grooves. Seen from the left, these are a B-tank groove 23, a B-control groove 24, a pump groove 25, an A-control groove 26 and an A-tank groove 27.
  • the principle is common to most directional control valves.
  • the relative position of the spool 20 in the longitudinal bore 22 is in the illustration in Fig. 3 so that the pump port hole P is completed, so that there is no connection to one of the adjacent working port holes A, B. It follows that the hydraulic motor 1 stands still because no hydraulic oil is supplied to it. Shown is the zero or neutral position.
  • the control valve 3 shown here for a hydraulic motor 1 now has an additional narrow auxiliary control groove 28, which is arranged between the B-tank groove 23 and the B-control groove 24.
  • auxiliary control groove 28 At the bottom of this Hilfs marsnut 28 begins a first transverse bore 29 which opens into a longitudinal bore 30, the other end is in communication with a second transverse bore 31.
  • This second transverse bore 31 establishes a connection to the B-tank groove 23 and thus to the tank connection bore T.
  • a biased check valve 32 is arranged with a biasing spring 33, in such a way that it is to be opened by a higher pressure from the working port bore B ago.
  • the control edge for controlling the volumetric flow between the working connection bore B and the second tank connection bore T is designed in a particularly advantageous manner.
  • the spool 20 On both sides of the auxiliary control groove 28, the spool 20 has short cylindrical sections, namely to the right of a sealing cylinder 35 and left thereof sinen biasing cylinder 36. To the left are two frusto-conical sections, namely a first control taper portion 37 with a weaker surface inclination and then a second control cone section 38 with a stronger surface inclination.
  • FIGS. 4 to 7 an identical section of the control valve 3 is shown, which is shown in FIG. 3 with a dotted circle.
  • the aim is to show how the object of the invention is achieved with the inventive and the advantageous means.
  • FIG. 4 shows that a control edge 40 assigned to the working connection bore B lies in the region of the sealing cylinder 35.
  • the working connection bore B and the tank connection bore T (FIG. 3) located farther to the left.
  • the auxiliary control groove 28 is covered with the transverse bore 29 beginning therein from the control edge 40, the pressure prevailing in the working port bore B does not act in the transverse bore 29 into it.
  • This state is given when, as shown in Fig. 3, the connection of the pump port hole P is shut off both to the working port hole A and only working port bore B, so that the hydraulic motor 1 (Fig. 1) is stationary. Again, the zero or neutral position is shown.
  • the hydraulic motor 1 is hydraulically biased, with the result that the uneven startup at low speed is greatly improved in a very simple manner. Accordingly, the degree of non-uniformity ⁇ can not practically work as a non-uniform rotational movement during slow starting. Incidentally, this also applies to the slow speed after a delay from faster running.
  • Fig. 6 the state is shown in still further control of the control valve 3 in the "lifting" mode.
  • the control edge 40 by the relative to FIG. 5 further movement of the spool 20 to the right so that the first control taper portion 37 with the weaker surface inclination is right of the control edge 40.
  • hydraulic oil can now flow between the control edge 40 and the first control cone portion 37.
  • the hydraulic oil flowing back from the hydraulic motor 1 (FIG. 1) to the tank flows through both the check valve 32 (FIG. 3) and the ring cross section between the control edge 40 and the control cam portion 37.
  • control piston 20 is moved to the right, the greater the flow of hydraulic oil between the control edge 40 and control cone portion 37th That the check valve 32 does not close immediately when the control edge 40 comes into the region of the first control taper portion 37, is because that due to the flow between the control edge 40 and the control cone section 37, an equally high dynamic pressure is created as over the prestressed check valve 32.
  • the biasing spring 33 is dimensioned so that the resulting return bias is about 25 bar.
  • the surface inclination of the first control cone section 37 is dimensioned approximately such that the angle to the imaginary cylindrical surface of the control spool 20 is approximately 16 °.
  • the surface inclination of the second control cone portion 38 is advantageously about 26 °. The dimensions otherwise depend on the size of the control valve 3, ie of its maximum flow. But then it does not require any inventive step to optimize this measure.
  • the invention is always applicable when loads are to be lifted in devices with a hydraulic motor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)
  • Check Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Magnetically Actuated Valves (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

A pilot valve (3) is designed as a directional control valve in which a control slide (20) is movably disposed in a longitudinal bore (22) of the valve body (21) so as to control the flow of hydraulic oil between two working connecting bores (A, B), a pump connecting bore (P), and a reservoir connecting bore (T). A check valve (32) which is biased with the aid of a bias spring (33) is disposed within the control slide (20). The check valve (32) is connected to an auxiliary control groove (28) via a first transversal bore (29) while being connected to the B-reservoir groove (23) via a second transversal bore (31). The check valve (32) is to be opened from working connecting bore B while the auxiliary control groove (28) is arranged between the B control groove (24) and the B reservoir groove (23) and is delimited on both sides by means of sealing cylindrical areas (35, 36).

Description

Steuerventil für einen HydromotorControl valve for a hydraulic motor
Die Erfindung bezieht sich auf ein Steuerventil für einen Hydromotor gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a control valve for a hydraulic motor according to the preamble of claim 1.
Hydromotoren werden beispielsweise bei Kranen zum Antrieb hydraulischer Winden verwendet. Mit einer solchen Winde lassen sich Lasten heben und senken.Hydromotors are used, for example, in cranes for driving hydraulic winches. With such a winch, loads can be lifted and lowered.
Aus DE-Al-39 41 802 ist ein hydraulisches Wegeventil bekannt, das eine lastdruckunabhängige Steuerung eines Hydromotors ermöglicht. Aus DE-C2-41 36 991 ist ein Wegeventil bekannt, das für den gleichen Zweck angewendet werden kann.From DE-Al-39 41 802 a hydraulic directional control valve is known, which allows a load pressure independent control of a hydraulic motor. From DE-C2-41 36 991 a directional valve is known, which can be used for the same purpose.
Aus der Arbeitsweise von Hydromotoren, die meist als Axialkolbenmaschinen, seltener als Radialkolbenmaschinen gestaltet sind, ergibt sich konstruktionsbedingt, dass der Förderstrom nicht gleichmäßig ist, sondern zyklisch schwankt, also pulsiert, wie dies beispielsweise in "H. Ebertshäuser: Fluidtechnik von A bis Z", Vereinigte Fachverlage Krausskopf/Ingenieur-Digest, 1. Auflage 1989, auf den Seiten 31 und 353 bis 354 erwähnt ist. Daraus ergeben sich zwangsläufig Momentenschwankungen, die sich insbesondere bei niedrigen Drehzahlen unangenehm bemerkbar machen. Wird eine zunächst ruhende Last gehoben, so erfolgt die Bewegung aus dem Stillstand mehr oder weniger ruckartig. Der gleiche Effekt tritt auf, wenn die Last ihre Position beinahe erreicht hat, so dass dann die Endposition beinahe erreicht ist. Pulsationen der Bewegung sind auch hier sehr störend.From the mode of operation of hydraulic motors, which are usually designed as axial piston machines, more rarely than radial piston machines, results from the design that the flow is not uniform, but cyclically fluctuates, ie pulsates, as described for example in "H. Ebertshäuser: fluid technology from A to Z" , Vereinigte Fachverlage Krausskopf / Ingenieur-Digest, 1st edition 1989, is mentioned on pages 31 and 353-354. This inevitably results in torque fluctuations, which make themselves uncomfortable especially at low speeds. If an initially resting load is lifted, then the movement takes place from standstill more or less jerky. The same effect occurs when the load has almost reached its position, so that the final position is almost reached. Pulsations of the movement are also very disturbing here.
Der Erfindung liegt die Aufgabe zugrunde, ein Steuerventil zu schaffen, das die zuvor geschilderten Momentenschwankungen und Pulsationen verhindert, ohne dass es einer zusätzlichen Ventilbaugruppe bedarf, die bisher zur Reduzierung der Pulsation bzw. Momentenschwankung eingesetzt wurde.The invention has for its object to provide a control valve which prevents the previously described torque fluctuations and pulsations without the need for an additional valve assembly, which was previously used to reduce the pulsation or torque fluctuation.
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 wird ein Ausführungsbeispiel der Erfindung anhand der Zeichnung näher erläutert.An embodiment of the invention will be explained in more detail with reference to the drawing.
Es zeigen: Fig. 1 ein Schema einer Ansteuerung für einen Hydromotor, Fig. 2 eine Ventilbaugruppe als Zusatzaggregat für die Funkion "Heben" gemäß einer Lösung nach dem Stand der Technik,1 shows a diagram of a control for a hydraulic motor, 2 shows a valve assembly as an additional unit for the function "lifting" according to a solution according to the prior art,
Fig. 3. eine Ansicht eines Steuerschiebers innerhalb eines Ventilkörpers, undFig. 3. is a view of a spool within a valve body, and
Fig. 4 bis 7 Ausschnitte der Stellung des Steuerschiebers relativ zu einer Steuerkante.Fig. 4 to 7 sections of the position of the spool relative to a control edge.
In der Fig. 1 ist ein Hydromotor 1 gezeigt, der eine nicht näher gezeigte Seilwinde zum Heben und Senken einer Last 2 antreibt. Mit Pfeilen ist am Hydromotor 1 gezeigt, dass die eine Drehrichtung des Hydromotors 1 das Senken der Last 2 bewirkt, die entgegengesetzte Drehrichtung des Hydromotors 1 das Heben der Last. Der Hydromotor 1 ist ansteuerbar durch ein als Wegeventil ausgebildetes Steuerventil 3 mit den üblichen Lastanschlüssen A und B sowie mit einem Pumpenanschluss P und einem Tankanschluss T. Dies entspricht dem vorbekannten Stand der Technik. Dies gilt auch für ein in die Zuleitung zum Hydromotor 1 eingesetztes Lasthalteventil 4, das der Kontrolle der Last beim Senken dient.In Fig. 1, a hydraulic motor 1 is shown, which drives a not shown in detail winch for lifting and lowering a load 2. Arrows on the hydraulic motor 1 is shown that the one direction of rotation of the hydraulic motor 1 causes the lowering of the load 2, the opposite direction of rotation of the hydraulic motor 1, the lifting of the load. The hydraulic motor 1 is controllable by a control valve 3 designed as a directional control valve with the usual load connections A and B and with a pump connection P and a tank connection T. This corresponds to the known prior art. This also applies to an inserted into the supply line to the hydraulic motor 1 load-holding valve 4, which serves to control the load during lowering.
Im "Heben" -Betrieb strömt das Hydrauliköl vom Pumpenanschluss P des Steuerventils 3 und die A-Leitung durch das sich von selbst öffnende Rückschlagventil des Lasthalteventils 4 zum Hydromotor 1 und treibt diesen an. Gleichzeitig fließt eine identische Menge von Hydrauliköl vom Hydromotor 1 über die B-Leitung durch das Steuerventil 3 zum Tankanschluss T. Die proportionale Flussmengensteuerung erfolgt durch die proportionale Steuerung des Steuerventils 3. Dies ist im hydraulischen Schaltbild des Steuerventils 3 gezeigt.In the "lifting" operation, the hydraulic oil flows from the pump port P of the control valve 3 and the A-line through the self-opening check valve of the load-holding valve 4 to the hydraulic motor 1 and drives it. At the same time, an identical amount of hydraulic oil from the hydraulic motor 1 flows through the B-line through the control valve 3 to the tank port T. The proportional flow amount control is performed by the proportional control of the control valve 3. This is shown in the hydraulic circuit diagram of the control valve 3.
Ln "Senken"-Betrieb ist die Flussrichtung umgekehrt. Dabei erfolgt die Bewegungssteuerung durch das proportional ansteuerbare Lasthalteventil 4.In "sink" mode, the flow direction is reversed. The movement control is effected by the proportionally controllable load-holding valve 4.
Als Hydromotor 1 kommt bei solchen Anwendungsfällen bevorzugt eine Hubverdrängermaschine zum Einsatz, beispielsweise eine Axialkolbenmaschine, wie sie in "Dubbel: Taschenbuch für den Maschinenbau", Springer-Verlag, 19. Auflage, auf der Seite H5, gezeigt ist. Diese weit verbreitete Maschinenbauart hat aber den Nachteil, dass der Förderstrom nicht gleichmäßig ist, weil dieser einen erheblichen Ungleichförmigkeitsgrad δ aufweist. Daraus kann sogar folgen, dass bei Beginn des Anhebens der Last 2, also bei sehr kleiner Drehzahl des Hydromotors 1, die Last 2 kurzzeitig absinkt. Das gilt auch beim Verringern der Drehzahl zum Anhalten der Last 2. Ein rationelles Arbeiten ist so kaum möglich und es ergeben sich Gefahrenmomente.As a hydraulic motor 1 comes in such applications preferably a Hubverdrängermaschine used, for example, an axial piston machine, as shown in "Dubbel: Taschenbuch for mechanical engineering", Springer-Verlag, 19th edition, on page H5. However, this widespread type of machine has the disadvantage that the flow is not uniform, because this has a considerable degree of non-uniformity δ. It may even follow that at the beginning of the Lifting the load 2, so at very low speed of the hydraulic motor 1, the load 2 drops briefly. This also applies when reducing the speed to stop the load 2. A rational work is hardly possible and there are dangerous moments.
Um dieses gravierende Problem wenigstens teilweise zu beheben, hat man versucht, die ungleichförmige Drehbewegung bei Langsamlauf durch die Einbindung einer Ventilbaugruppe 10 zum Beispiel in die entsprechende Rücklaufleitung vom Hydromotor 1 zu verringern, wie dies in der Fig. 2 dargestellt ist. Hier ist im Zuge der B-Leitung die Ventilbaugruppe 10 angeordnet, die aus zwei parallel gegeneinander geschalteten Rückschlagventilen besteht, nämlich aus einem vorgespannten Rückschlagventil 11 und aus einen nicht vorgespannten Rückschlagventil 12. Die Anmelderin selbst hat im Jahre 2001 eine solche Ventilbaugruppe geschaffen. Damit ist eine teilweise Kompensation der Druckschwankungen im Hebebetrieb möglich. Das vom Hydromotor 1 zum Steuerventil 3 strömende Hydrauliköl muss die Ventilbaugruppe 10 passieren. Weil das nicht vorgespannte Rückschlagventil 12 in Sperrrichtung angeströmt wird, sperrt dieses, so dass das Hydrauliköl nur durch das vorgespannte Rückschlagventil 11 strömen kann, sofern sein Druck höher ist also die Kraft der Vorspannfeder. Dadurch entsteht der bedeutsame Effekt, dass der Hydromotor 1 hydraulisch vorgespannt ist, was zur Folge hat, dass der ungleichmäßige Anlauf mit kleiner Drehzahl auf sehr einfache Weise stark verbessert wird. Der Ungleichförmigkeitsgrad δ der Drehbewegung wird verbessert.To remedy this serious problem at least partially, it has been attempted to reduce the non-uniform rotational movement at low speed by the inclusion of a valve assembly 10, for example, in the corresponding return line from the hydraulic motor 1, as shown in FIG. Here, in the course of the B-line valve assembly 10 is arranged, which consists of two mutually parallel check valves, namely a biased check valve 11 and a non-biased check valve 12. The applicant itself has created in 2001 such a valve assembly. Thus, a partial compensation of the pressure fluctuations in the lifting operation is possible. The hydraulic oil flowing from the hydraulic motor 1 to the control valve 3 must pass through the valve assembly 10. Because the non-biased check valve 12 is flowed in the reverse direction, this locks, so that the hydraulic oil can flow only through the biased check valve 11, if its pressure is higher so the force of the biasing spring. This creates the significant effect that the hydraulic motor 1 is hydraulically biased, with the result that the uneven startup at low speed is greatly improved in a very simple manner. The degree of non-uniformity δ of the rotary motion is improved.
Eine Lösung mit einer solchen zusätzlichen Ventilbaugruppe 10 ist herstellungsmäßig aufwendig und teuer und benötigt Platz. Der Erfindung liegt aber insbesondere auch noch die Aufgabe zugrunde, eine solche Lösung hinsichtlich Funktionalität zu verbessern.A solution with such an additional valve assembly 10 is complicated to manufacture and expensive and requires space. But the invention is also particularly the object of improving such a solution in terms of functionality.
In der Fig. 3 ist eine Ansicht eines Steuerschiebers 20 innerhalb eines Ventilkörpers 21 gezeigt, die dem Steuerventil 3 zugehörig sind. In einer Längsbohrung 22 des Ventilkörpers 21 ist der Steuerschieber 20 axial verschiebbar, was mit einem Doppelpfeil angedeutet ist. Die axiale Verschiebbarkeit wird dabei, wie bei solchen proportional arbeitenden Steuerventilen üblich, mittels mindestens eines Antriebs bewirkt, wobei elektrische, hydraulische oder pneumatische Antriebe Verwendungen finden. Da es im vorliegenden Fall auf Zahl und Bauart des Antriebs für den Steuerschieber 20 nicht ankommt, wurde ein solcher Antrieb in der Figur nicht dargestellt. Wie bei solchen Steuerventilen üblich, sind Querbohrungen im Ventilkörper 21 vorhanden, die bis an die Längsbohrung 22 heranführen. In der Fig. 3 sind fünf derartige Querbohrungen gezeigt, nämlich von rechts her gesehen eine Tankanschlussbohrung T, sine erste Arbeitsanschlussbohrung A, eine Pumpenanschlussbohrung P, eine zweite Arbeitsanschlussbolirung B und eine weitere Tankanschlussbohrung T. Aus konstruktiven Gründen sind zwei Tankanschlussbohrungen T gezeigt, die in der Regel innerhalb des Ventilkörpers 21 zusammengeführt sind. Hintergrund ist, dass jede der Arbeitsanschlussbohrungen A, B betrieblich wechselweise mit der Tankanschlussbohrung T bzw. mit der Pumpenanschlussbohrung P verbindbar sein muss, um den "Heben"- und "Senken"-Betrieb zu ermöglichen.In Fig. 3 is a view of a spool 20 is shown within a valve body 21, which are the control valve 3 associated. In a longitudinal bore 22 of the valve body 21, the spool 20 is axially displaceable, which is indicated by a double arrow. The axial displaceability is effected, as usual in such proportionally operating control valves, by means of at least one drive, wherein electrical, hydraulic or pneumatic drives find uses. Since in the present case, the number and type of drive for the spool 20 does not matter, such a drive has not been shown in the figure. As is usual with such control valves, transverse bores are present in the valve body 21, which lead up to the longitudinal bore 22. In FIG. 3, five such transverse bores are shown, namely a tank connection bore T seen from the right, a first working connection bore A, a pump connection bore P, a second working connection bolt B and a further tank connection bore T. For constructional reasons, two tank connection bores T are shown the rule are brought together within the valve body 21. The background is that each of the working connection bores A, B must be operationally connectable to the tank connection bore T or to the pump connection bore P in order to enable "lifting" and "sinking" operation.
Der Steuerschieber 20 weist, um die verschiedenen Verbindungen zwischen den Anschlussbohrungen T, B, P, A und T herstellen zu können, profilierte Ringnuten auf. Von links her gesehen sind dies eine B-Tank-Nut 23, eine B-Steuernut 24, eine Pumpennut 25, eine A-Steuernut 26 und eine A-Tank-Nut 27. Das Prinzip ist den meisten Wegeventilen gemeinsam.The spool 20 has, in order to produce the various connections between the terminal bores T, B, P, A and T, profiled annular grooves. Seen from the left, these are a B-tank groove 23, a B-control groove 24, a pump groove 25, an A-control groove 26 and an A-tank groove 27. The principle is common to most directional control valves.
Die relative Lage des Steuerschiebers 20 in der Längsbohrung 22 ist bei der Darstellung in der Fig. 3 so, dass die Pumpenanschlussbohrung P abgeschlossen ist, dass also keine Verbindung zu einer der benachbarten Arbeitsanschlussbohrungen A, B besteht. Daraus folgt, dass der Hydromotor 1 still steht, weil ihm kein Hydrauliköl zugeführt wird. Gezeigt ist also die Null- bzw. Neutralstellung.The relative position of the spool 20 in the longitudinal bore 22 is in the illustration in Fig. 3 so that the pump port hole P is completed, so that there is no connection to one of the adjacent working port holes A, B. It follows that the hydraulic motor 1 stands still because no hydraulic oil is supplied to it. Shown is the zero or neutral position.
Erfindungsgemäß weist nun aber das hier gezeigte Steuerventil 3 für einen Hydromotor 1 (Fig. 1) eine zusätzliche schmale Hilfssteuernut 28 auf, die zwischen der B-Tank-Nut 23 und der B-Steuernut 24 angeordnet ist. Am Grund dieser Hilfssteuernut 28 beginnt eine erste Querbohrung 29, die in eine Längsbohrung 30 mündet, deren anderes Ende mit einer zweiten Querbohrung 31 in Verbindung steht. Diese zweite Querbohrung 31 stellt eine Verbindung zur B-Tank-Nut 23 und damit zur Tankanschlussbohrung T her. Bedeutendstes Merkmal der Erfindung ist nun, dass in dieser Längsbohrung 30 ein vorgespanntes Rückschlagventil 32 mit einer Vorspannfeder 33 angeordnet ist, und zwar so, dass es durch einen höheren Druck von der Arbeitsanschlussbohrung B her zu öffnen ist. Die Wirkungsweise wird später genauer beschrieben werden. /orteilhaft ist die Steuerkante zur Steuerung des Volumenstroms zwischen der \rbeitsanschlussbohrung B und der zweiten Tankanschlussbohrung T besonders ausgestaltet. Beidseits der Hilfssteuernut 28 weist der Steuerschieber 20 kurze zylindrische Abschnitte auf, nämlich rechts davon einen Dichtzylinder 35 und links davon sinen Vorspannzylinder 36. Nach links schließen sich zwei kegelstumpfförmige Abschnitte an, nämlich ein erster Steuerkegelabschnitt 37 mit einer schwächeren Flächenneigung und dann daran ein zweiter Steuerkegelabschnitt 38 mit einer stärkeren Flächenneigung.According to the invention, however, the control valve 3 shown here for a hydraulic motor 1 (FIG. 1) now has an additional narrow auxiliary control groove 28, which is arranged between the B-tank groove 23 and the B-control groove 24. At the bottom of this Hilfssteuernut 28 begins a first transverse bore 29 which opens into a longitudinal bore 30, the other end is in communication with a second transverse bore 31. This second transverse bore 31 establishes a connection to the B-tank groove 23 and thus to the tank connection bore T. The most significant feature of the invention is now that in this longitudinal bore 30, a biased check valve 32 is arranged with a biasing spring 33, in such a way that it is to be opened by a higher pressure from the working port bore B ago. The mode of action will be described in more detail later. The control edge for controlling the volumetric flow between the working connection bore B and the second tank connection bore T is designed in a particularly advantageous manner. On both sides of the auxiliary control groove 28, the spool 20 has short cylindrical sections, namely to the right of a sealing cylinder 35 and left thereof sinen biasing cylinder 36. To the left are two frusto-conical sections, namely a first control taper portion 37 with a weaker surface inclination and then a second control cone section 38 with a stronger surface inclination.
In den Fig. 4 bis 7 ist jeweils ein identischer Ausschnitt aus dem Steuerventil 3 gezeigt, der in der Fig. 3 mit einem gepunkteten Kreis dargestellt ist. Dabei geht es darum zu zeigen, wie mit den erfmdungsgemäßen und den vorteilhaften Mitteln die Aufgabe der Erfindung gelöst wird.In FIGS. 4 to 7, an identical section of the control valve 3 is shown, which is shown in FIG. 3 with a dotted circle. The aim is to show how the object of the invention is achieved with the inventive and the advantageous means.
In der Fig. 4 ist gezeigt, dass eine der Arbeitsanschlussbohrung B zugeordnete Steuerkante 40 im Bereich des Dichtzylinders 35 liegt. Somit besteht zwischen der Arbeitsanschlussbohrung B und der weiter links gelegenen Tankanschlussbohrung T (Fig. 3) keine Verbindung. Weil somit auch die Hilfssteuernut 28 mit der darin beginnenden Querbohrung 29 von der Steuerkante 40 abgedeckt ist, wirkt in die Querbohrung 29 hinein der in der Arbeitsanschlussbohrung B herrschende Druck nicht. Dieser Zustand ist gegeben, wenn, wie in Fig. 3 gezeigt, die Verbindung von der Pumpenanschlussbohrung P sowohl zur Arbeitsanschlussbohrung A als auch nur Arbeitsanschlussbohrung B abgesperrt ist, so dass der Hydromotor 1 (Fig. 1) still steht. Auch hier ist also die Null- bzw. Neutralstellung gezeigt.FIG. 4 shows that a control edge 40 assigned to the working connection bore B lies in the region of the sealing cylinder 35. Thus, there is no connection between the working connection bore B and the tank connection bore T (FIG. 3) located farther to the left. Because thus also the auxiliary control groove 28 is covered with the transverse bore 29 beginning therein from the control edge 40, the pressure prevailing in the working port bore B does not act in the transverse bore 29 into it. This state is given when, as shown in Fig. 3, the connection of the pump port hole P is shut off both to the working port hole A and only working port bore B, so that the hydraulic motor 1 (Fig. 1) is stationary. Again, the zero or neutral position is shown.
In der Fig. 5 ist jener Zustand gezeigt, bei dem der Steuerschieber 20 gegenüber der Steuerkante 40 so weit nach rechts verschoben ist, dass nun der in der Arbeitsanschlussbohrung B herrschende Druck wegen der frei liegenden Hilfssteuernut 28 in die Querbohrung 29 wirken kann. In diesem Zustand ist nun der Hydromotor 1 (Fig. 1) in Funktion, weil gleichzeitig, was aus der Fig. 3 ableitbar ist, wegen der Rechtsverschiebung des Steuerschiebers 20 Hydrauliköl von der Pumpenanschlussbohrung P zur ersten Arbeitsanschlussbohrung A und von dort zum Hydromotor 1 strömt. Das gleichzeitig vom Hydromotor 1 zum Tank zurückströmende Hydrauliköl kann nun aber nicht den direkten Weg von der Arbeitsanschlussbohrung B zur weiter links gelegenen Tankanschlussbohrung T nehmen, weil dieser Weg durch die Dichtwirkung des Vorspannzylinders 36 versperrt ist. Das zurückfließende Hydrauliköl drückt folglich das in der Längsbohrung 30 liegende vorgespannte Rückschlagventil 32 auf. Dadurch steigt entsprechend der Druck in der Arbeitsanschlussbohrung B auf einen Wert, der durch die Kraft der Vorspannfeder 33 des Rückschlagventils 32 (Fig. 3) bestimmt ist.5, the state is shown in which the spool 20 is moved so far to the right with respect to the control edge 40, that now prevail in the working port bore B pressure can act because of the exposed auxiliary control groove 28 in the transverse bore 29. In this state, the hydraulic motor 1 (FIG. 1) is now in operation, because at the same time, which can be derived from FIG. 3, hydraulic oil flows from the pump connection bore P to the first working connection bore A and from there to the hydraulic motor 1 because of the rightward displacement of the control slide 20 , However, the hydraulic oil flowing back from the hydraulic motor 1 to the tank at the same time can not now travel directly from the working port bore B to the tank connection bore T located further to the left, because this path is blocked by the sealing action of the pretensioning cylinder 36. The returning hydraulic oil consequently pushes the preloaded check valve 32 located in the longitudinal bore 30. As a result, the pressure in the working port bore B correspondingly increases to a value determined by the force of the biasing spring 33 of the check valve 32 (FIG. 3).
Durch diese Druckerhöhung in der Arbeitsanschlussbohrung B wird der Hydromotor 1 hydraulisch vorgespannt ist, was zur Folge hat, dass der ungleichmäßige Anlauf mit kleiner Drehzahl auf sehr einfache Weise stark verbessert wird. Der Ungleichförmigkeitsgrad δ kann sich entsprechend praktisch nicht als ungleichförmige Drehbewegung beim langsamen Anfahren auswirken. Das gilt im übrigen auch für den Langsamlauf nach einer Verzögerung aus schnellerem Lauf.By this pressure increase in the working port bore B, the hydraulic motor 1 is hydraulically biased, with the result that the uneven startup at low speed is greatly improved in a very simple manner. Accordingly, the degree of non-uniformity δ can not practically work as a non-uniform rotational movement during slow starting. Incidentally, this also applies to the slow speed after a delay from faster running.
In der Fig. 6 ist der Zustand bei noch weiterer Aufsteuerung des Steuerventils 3 in die "Heben"-Betriebsart gezeigt. Hier liegt nun die Steuerkante 40 durch die gegenüber Fig. 5 weitere Bewegung des Steuerschiebers 20 nach rechts so, dass der erste Steuerkegelabschnitt 37 mit der schwächeren Flächenneigung rechts von der Steuerkante 40 liegt. Damit kann nun Hydrauliköl zwischen der Steuerkante 40 und dem ersten Steuerkegelabschnitt 37 hindurchströmen. In diesem Zustand fließt das vom Hydromotor 1 (Fig. 1) zum Tank zurückfließende Hydrauliköl sowohl durch das Rückschlagventil 32 (Fig. 3) als auch über den Ringquerschnitt zwischen Steuerkante 40 und Steuerkegelabschnitt 37 hindurch. Je weiter der Steuerkolben 20 nach rechts bewegt wird, desto größer wird der Strom des Hydrauliköls auch zwischen Steuerkante 40 und Steuerkegelabschnitt 37. Dass das Rückschlagventil 32 nicht sofort dann schließt, wenn die Steuerkante 40 in den Bereich des ersten Steuerkegelabschnitts 37 kommt, liegt daran, dass durch die Strömung zwischen der Steuerkante 40 und dem Steuerkegelabschnitt 37 ein gleich hoher Staudruck wie über dem vorgespannten Rückschlagventil 32 entsteht.In Fig. 6, the state is shown in still further control of the control valve 3 in the "lifting" mode. Here is the control edge 40 by the relative to FIG. 5 further movement of the spool 20 to the right so that the first control taper portion 37 with the weaker surface inclination is right of the control edge 40. Thus, hydraulic oil can now flow between the control edge 40 and the first control cone portion 37. In this state, the hydraulic oil flowing back from the hydraulic motor 1 (FIG. 1) to the tank flows through both the check valve 32 (FIG. 3) and the ring cross section between the control edge 40 and the control cam portion 37. The further the control piston 20 is moved to the right, the greater the flow of hydraulic oil between the control edge 40 and control cone portion 37th That the check valve 32 does not close immediately when the control edge 40 comes into the region of the first control taper portion 37, is because that due to the flow between the control edge 40 and the control cone section 37, an equally high dynamic pressure is created as over the prestressed check valve 32.
Wird der Steuerschieber 20 gegenüber der Fig. 6 noch weiter nach rechts bewegt, nämlich in eine in der Fig. 7 gezeigte Stellung, bei der die Steuerkante 40 nun im Bereich des zweiten Steuerkegelabschnitts 38 mit der stärkeren Flächenneigung liegt, so ist der aus der Strömung resultierende Staudruck wegen des nun größeren freien Durchtrittsquerschnitts für das Hydrauliköl kleiner, was dazu führt, dass nun das Rückschlagventil 32 (Fig. 3) ichließt. Hydrauliköl fließt dann also nur noch durch den freien Raum zwischen Steuerkante 40 und den beiden Steuerkegelabschnitten 37, 38. Der Hydraulikölstrom und damit die Drehzahl des Hydromotors 1 sind nun aber so groß, dass der eingangs erwähnte Effekt des großen Ungleichförmigkeitsgrades δ nicht mehr auftritt. Bei diesem nun größeren freien Durchtrittsquerschnitt ist nun auch der Durchflusswiderstand Δp reduziert. Dies führt zu weniger Erwärmung des Hydrauliköls, was einen besonderen Vorteil darstellt.6, the control slide 20 is moved further to the right, namely in a position shown in FIG. 7, in which the control edge 40 is now in the region of the second control cone section 38 with the stronger surface inclination, then the flow resulting back pressure because of the now larger free passage cross-section for the hydraulic oil smaller, which means that now the check valve 32 (FIG. 3) ichließt. Hydraulic oil then flows only through the free space between the control edge 40 and the two control cone sections 37, 38. The hydraulic oil flow and thus the speed of the hydraulic motor 1 are now so large that the above-mentioned effect of the large degree of irregularity δ no longer occurs. In this now larger free passage cross section, the flow resistance Δp is now reduced. This leads to less heating of the hydraulic oil, which is a particular advantage.
Vorteilhaft wird die Vorspannfeder 33 so bemessen, dass die entstehende Rücklaufvorspannung etwa 25 bar beträgt.Advantageously, the biasing spring 33 is dimensioned so that the resulting return bias is about 25 bar.
Vorteilhaft wird die Flächenneigung des ersten Steuerkegelabschnitts 37 etwa so bemessen, dass der Winkel zur gedachten Zylinderfläche des Steuerschiebers 20 etwa 16° beträgt. Die Flächenneigung des zweiten Steuerkegelabschnitts 38 beträgt vorteilhaft etwa 26°. Die Maße hängen ansonsten von der Größe des Steuerventils 3 ab, also von dessen maximaler Durchströmung. Es bedarf dann aber keiner erfinderischen Tätigkeit, diese Maß zu optimieren.Advantageously, the surface inclination of the first control cone section 37 is dimensioned approximately such that the angle to the imaginary cylindrical surface of the control spool 20 is approximately 16 °. The surface inclination of the second control cone portion 38 is advantageously about 26 °. The dimensions otherwise depend on the size of the control valve 3, ie of its maximum flow. But then it does not require any inventive step to optimize this measure.
Die Erfindung ist immer dann anwendbar, wenn bei Vorrichtungen mit einem Hydromotor Lasten gehoben werden sollen. The invention is always applicable when loads are to be lifted in devices with a hydraulic motor.

Claims

Patentansprüche claims
1. Steuerventil (3) für einen Hydromotor (1), mit dem in einer Vorrichtung Lasten (2) zu heben sind, wobei das Steuerventil (3) als Wegeventil gestaltet ist, bei dem ein Steuerschieber (20) in einer Längsbohrung (22) eines Ventilkörpers (21) verschiebbar angeordnet ist, um den Fluss von Hydrauliköl zwischen zwei Arbeitsanschlussbohrungen (A, B), einer Pumpenanschlussbohrung (P) und einer Tankanschlussbohrung (T) zu steuern, wobei der Steuerschieber (20) eine B-Tank- Nut (23), eine B-Steuernut (24), eine Pumpennut (25), eine A-Steuernut (26) und gegebenenfalls eine A-Tank-Nut (27) aufweist, dadurch gekennzeichnet,A control valve (3) for a hydraulic motor (1) for lifting loads (2) in a device, wherein the control valve (3) is designed as a directional control valve, in which a control slide (20) is arranged in a longitudinal bore (22). a valve body (21) is slidably arranged to control the flow of hydraulic oil between two working port holes (A, B), a pump port hole (P) and a tank port hole (T), wherein the spool (20) a B-tank groove ( 23), a B-control groove (24), a pump groove (25), an A-control groove (26) and optionally an A-tank groove (27), characterized
- dass innerhalb des Steuerschiebers (20) ein mittels einer Vorspannfeder (33) vorgespanntes Rückschlagventil (32) angeordnet ist, das einerseits über eine erste Querbohrung (29) mit einer Hüfssteuernut (28) verbunden ist und andererseits über eine zweite Querbohrung (31) mit der B-Tank-Nut (23) verbunden ist, dass das Rückschlagventil (32) von der Arbeitsanschlussbohrung B her zu öffnen ist und dass die Hüfssteuernut (28) zwischen der B-Steuernut (24) und der B-Tank-Nut (23) angeordnet und beidseits durch dichtende zylindrische Flächen (35, 36) begrenzt ist.- That within the spool (20) by means of a biasing spring (33) biased check valve (32) is arranged, on the one hand via a first transverse bore (29) with a Hüfssteuernut (28) is connected and on the other hand via a second transverse bore (31) the B-tank groove (23) is connected to open the check valve (32) from the working port bore B and that the Hüfssteuernut (28) between the B-control groove (24) and the B-tank groove (23 ) and on both sides by sealing cylindrical surfaces (35, 36) is limited.
2. Steuerventil (3) nach Anspruch 1, dadurch gekennzeichnet, dass die Vorspannfeder (33) so bemessen ist, dass sie eine Rücklaufvorspannung von etwa 25 bar erzeugt.Second control valve (3) according to claim 1, characterized in that the biasing spring (33) is dimensioned so that it generates a return bias of about 25 bar.
3. Steuerventil (3) nach Anspruch 2, dadurch gekennzeichnet, dass sich an den die eine zylindrische Fläche bildenden Vorspannzylinder (36) in Richtung B-Tank-Nut (23) ein erster kegelstumpfförmiger Steuerkegelabschnitt (37) anschließt.3. Control valve (3) according to claim 2, characterized in that adjoining the a cylindrical surface forming biasing cylinder (36) in the direction B-tank groove (23), a first frusto-conical control taper portion (37).
4. Steuerventil (3) nach Anspruch 3, dadurch gekennzeichnet, dass die Flächenneigung des ersten Steuerkegelabschnitts (37) etwa so bemessen, dass der Winkel zur gedachten Zylinderfläche des Steuerschiebers (20) etwa 16° beträgt.4. control valve (3) according to claim 3, characterized in that the surface inclination of the first control cone portion (37) approximately sized so that the angle to the imaginary cylindrical surface of the spool (20) is about 16 °.
5. Steuerventil (3) nach Anspruch 4, dadurch gekennzeichnet, dass sich an den ersten kegelstumpfförmigen Steuerkegelabschnitt (37) ein zweiter kegelstumpfförmiger Steuerkegelabschnitts (38) anschließt. 5. control valve (3) according to claim 4, characterized in that adjoining the first frustoconical control taper portion (37), a second frusto-conical control taper portion (38).
6. Steuerventil (3) nach Anspruch 5, dadurch gekennzeichnet, dass die Flächenneigung des zweiten Steuerkegelabschnitts (38) etwa so bemessen, dass der Winkel zur gedachten Zylinderfläche des Steuerschiebers (20) etwa 26° beträgt. 6. control valve (3) according to claim 5, characterized in that the surface inclination of the second control cone portion (38) approximately sized so that the angle to the imaginary cylindrical surface of the spool valve (20) is about 26 °.
EP05804312A 2005-04-20 2005-12-01 Pilot valve for a hydraulic motor Not-in-force EP1872018B1 (en)

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PCT/CH2005/000717 WO2006111031A1 (en) 2005-04-20 2005-12-01 Pilot valve for a hydraulic motor

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ATE403807T1 (en) 2008-08-15
JP2008537069A (en) 2008-09-11
US7921879B2 (en) 2011-04-12

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