EP0072952B1 - Hydraulic motor control device - Google Patents

Hydraulic motor control device Download PDF

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Publication number
EP0072952B1
EP0072952B1 EP82107131A EP82107131A EP0072952B1 EP 0072952 B1 EP0072952 B1 EP 0072952B1 EP 82107131 A EP82107131 A EP 82107131A EP 82107131 A EP82107131 A EP 82107131A EP 0072952 B1 EP0072952 B1 EP 0072952B1
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EP
European Patent Office
Prior art keywords
line
valve
pressure
annular groove
throttle
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Expired
Application number
EP82107131A
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German (de)
French (fr)
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EP0072952A2 (en
EP0072952A3 (en
Inventor
Günther Schwerin
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0072952A2 publication Critical patent/EP0072952A2/en
Publication of EP0072952A3 publication Critical patent/EP0072952A3/en
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Publication of EP0072952B1 publication Critical patent/EP0072952B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor

Definitions

  • the invention relates to a control device according to the preamble of the main claim.
  • a proportional directional control valve there is often the risk of so-called fixed throttling, which is understood to mean a state in which only as much pressure medium flows to the load to be lifted as there is a total loss of leakage; the device for the load to be lifted does not move.
  • This risk is particularly great in the case of the proportional valves mentioned above, because they do not switch, but gradually creep into the neutral position by means of proportional approximation, i. H. proportional to a control deviation that should eventually become zero.
  • control device with the characterizing features of the main claim has the advantage that the above-mentioned fixed throttling in proportional control valves can be largely prevented in the simplest way.
  • the control device has a pump 10, which sucks in pressure medium from a container 13 via a suction line 11 and a return line 12 and displaces it into a delivery line 14.
  • the delivery line 14 opens into a space 15 which merges into a chamber 16, the shoulder of these two spaces forming a valve seat 17 for a seat valve body 18 of a pressure compensator 20.
  • This is slidably guided in a housing bore 19 and is loaded on its side facing away from the closing cone 19 'by a compression spring 21 which is located in a pressure chamber 22.
  • a line 23 opens into the pressure chamber, which leads to an annular groove 24 on a slide bore 25, in which a control slide 26 is slidably guided.
  • the control slide can be adjusted proportionally, electromagnetically, mechanically or hydraulically, according to a setpoint.
  • annular grooves 28, 29 are formed on the control slide 26, which are separated from one another only by a narrow collar 30, the outer diameter of which corresponds to that of the control slide.
  • This also has a second, wider annular groove 31 which merges into a conical zone 32.
  • annular groove 33 is formed on the slide bore 25, to the left of the annular groove 24 there are three annular grooves 34, 35, 36 on the slide bore.
  • a line 38 leads from the annular groove 33 to the delivery line 14. From the line 38 goes out a line 39, which leads to a single-acting hydraulic cylinder 40 and in which a throttle 41 is arranged.
  • the line 23 leading from the pressure chamber 22 to the annular groove 24 likewise opens into the line 39; the throttle 41 lies between this mouth and that of the line 39 in the line 38.
  • a check valve 42 is arranged in front of the hydraulic cylinder 40.
  • a line 43 leads to the return line 12, which starts from a chamber 47, which is part of a slide bore 44, in which a control slide 45 is slidably guided.
  • a compression spring 46 arranged in the chamber 47 acts on it.
  • Four annular grooves 48 to 51 are formed on the slide bore 44, and a chamber 52 opposite the chamber 47.
  • a line 53 leads from the annular groove 48 to the line 39; it opens there in front of the check valve 42.
  • a line 54 leads to the annular groove 36 at the slide bore 25.
  • a line 55 leads to the line 38
  • a line 56 leads to a line 57, which is the chamber 52 and the annular groove 34 connects to one another.
  • a line 58 leads from the ring groove 51 to the line 56.
  • a throttle 59 or 60 is arranged in each of the two line branches 56 ', 56 "of the line 56.
  • Two ring grooves 63, 64 are formed on the control slide 45
  • Pressure compensator 20 leads a return line 61 to return line 12.
  • the pressure medium conveyed by the pump 10 flows against the valve body 18.
  • the compression spring 21 would press it onto its valve seat 17 if it were not for the path via the throttle 41 to the container 13, namely via the lines 39, 53, the annular groove 63 on the control slide 45, the interconnected annular grooves 48, 49, the line 54, the interconnected annular grooves 35, 36 on the slide bore 25 and the line 43.
  • a pressure difference arises at the throttle 41, by means of which the valve body 18 is held in the open position. This results in a neutral circulation, in which the pressure medium delivered by the pump 10 flows off with a low pressure drop, specifically via the chamber 16, the return line 61 and the return line 12.
  • a small, approximately constant control current always flows via the throttle 41 - as previously described - to container 13; the spring 21 keeps the pressure difference at the throttle 41 almost constant.
  • the control slide 25 moves to its left end stop 45 ". This blocks the connection between the annular grooves 48, 49, with the result that no pressure medium is initially passed through can flow the throttle 41.
  • the compression spring 46 therefore decides up to which pressure the so-called fixed throttling is possible when approaching the operating state “lifting.”
  • the spring 46 is expediently designed such that this pressure is as little as possible higher than the neutral circulation pressure for which the pressure spring 21 of the pressure compensator is responsible.
  • the check valve 42 secures the load on the hydraulic cylinder against falling as long as the pressure in the system is still too low to allow “lifting”.
  • the load on the hydraulic cylinder is raised at least with the control current flowing through the choke 41.
  • the collar 30 interrupting the connection from the annular groove 35 to the annular groove 36, but the connection from the annular groove 24 to the annular groove 32 is opened via the conical zone 32 - this slide position corresponds to one Larger control deviation in the sense of lifting - an additional flow proportional to the cross-section (throttle point) at the conical zone 32 flows to the hydraulic cylinder, namely via line 38, the ring grooves 33, 24 and line 23 to line 39.
  • the throttle point at the conical zone 32 only takes effect now. It lies parallel to throttle 41.
  • Prolonged lifting causes the spool 26 to move to the right again (feedback in the control loop).
  • the collar 30 again establishes a connection between the ring grooves 35, 36.
  • this does not lead to any reaction since the control slide 45 still blocks the connection between the ring grooves 48, 49.
  • the pressure medium connection via the throttle 59 is practically irrelevant since its cross section is negligibly small compared to the passage between the ring grooves 50, 51.
  • the movement of the control slide 26 to the right continues (feedback), since the load in the hydraulic cylinder 40 is raised further.
  • the relief between the ring grooves 48, 49 is still blocked by the control slide 45.
  • a new cycle begins if the "Lifting" operating state is to occur again.
  • the exemplary embodiment according to FIG. 2 is largely the same as that according to FIG. 1, but has the following difference: the lines 56 and leading from the annular groove 50 to the line 58 56 'including throttle 59 are omitted. Instead, a line 67 containing a throttle 66 leads from the line 55 to the chamber 52. From this it can be seen that the two throttles 60, 66 are connected in parallel with respect to this chamber. As a result, compared to the exemplary embodiment according to FIG. 1, the gradient of the pressure drop in the chamber 52 becomes twice as high as before, so that the control slide 45 responds more quickly. There is no further change in the other mode of operation described above.
  • the lines shown in the drawing can also be housing channels in a common valve housing.
  • a slide valve can also be used instead of the switching valve.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Steuereinrichtung nach der Gattung des Hauptanspruchs. Bei einem derartigen, proportional arbeitenden Wegeventil besteht häufig die Gefahr des sogenannten Festdrosselns, worunter man einen Zustand versteht, bei dem gerade nur soviel Druckmittel zur anzuhebenden Last fließt, wie insgesamt an Leckage verloren geht; das Gerät für die zu hebende Last bewegt sich nicht. Dieses Gleichgewicht, bei dem die Druckmittelquelle ständig gegen den Lastdruck fördert (Lastdruck = Neutralumlaufdruck), bleibt bis zur nasch vollendeten Zerstörung der Druckmittelquelle erhalten. Diese Gefahr ist besonders groß bei den oben erwähnten, proportional arbeitenden Ventilen, weil sie nicht schaltend, sondern mittels proportionaler Annäherung schleichend in die Neutralstellung gelangen, d. h. proportional zu einer Regelabweichung, die schließlich zu Null werden soll.The invention relates to a control device according to the preamble of the main claim. With such a proportional directional control valve there is often the risk of so-called fixed throttling, which is understood to mean a state in which only as much pressure medium flows to the load to be lifted as there is a total loss of leakage; the device for the load to be lifted does not move. This equilibrium, in which the pressure medium source constantly delivers against the load pressure (load pressure = neutral circulating pressure), is maintained until the pressure medium source is destroyed. This risk is particularly great in the case of the proportional valves mentioned above, because they do not switch, but gradually creep into the neutral position by means of proportional approximation, i. H. proportional to a control deviation that should eventually become zero.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Steuereinrichtung mit den kennzeichnenden Merkmalen des Hauptanspruches hat demgegenüber den Vorteil, daß das oben erwähnte Festdrosseln bei Proportional-Regelventilen auf einfachste Weise weitestgehend verhindert werden kann.The control device according to the invention with the characterizing features of the main claim has the advantage that the above-mentioned fixed throttling in proportional control valves can be largely prevented in the simplest way.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Merkmale möglich. ZeichnungAdvantageous further developments and improvements of the features specified in the main claim are possible through the measures listed in the subclaims. drawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Diese zeigt in

  • Figur 1 in schematischer Darstellung eine Steuereinrichtung für einen einfach wirkenden Verbraucher, und in
  • Figur 2 eine Abwandlung des Ausführungsbeispiels nach Figur 1.
An embodiment of the invention is shown in the drawing and explained in more detail in the following description. This shows in
  • Figure 1 is a schematic representation of a control device for a single-acting consumer, and in
  • Figure 2 shows a modification of the embodiment of Figure 1.

Beschreibung des AusführungsbeispielesDescription of the embodiment

Die Steuereinrichtung gemäß Fig. 1 weist eine Pumpe 10 auf, die über eine Saugleitung 11 und eine Rücklaufleitung 12 Druckmittel aus einem Behälter 13 ansaugt und in eine Förderleitung 14 verdrängt. Die Förderleitung 14 mündet in einen Raum 15, welcher in eine Kammer 16 übergeht, wobei die Schulter dieser beiden Räume einen Ventilsitz 17 für einen Sitzventilkörper 18 einer Druckwaage 20 bildet. Dieser ist gleitend in einer Gehäusebohrung 19 geführt und auf seiner dem Schließkegel 19' abgewandten Seite von einer Druckfeder 21 belastet, die sich in einer Druckkammer 22 befindet. In die Druckkammer mündet eine Leitung 23, die zu einer Ringnut 24 an einer Schieberbohrung 25 führt, in welcher ein Steuerschieber 26 gleitend geführt ist. Der Steuerschieber kann elektromagnetisch, mechanisch oder hydraulisch entsprechend einem eingegebenen Sollwert proportional verstellt werden.The control device according to FIG. 1 has a pump 10, which sucks in pressure medium from a container 13 via a suction line 11 and a return line 12 and displaces it into a delivery line 14. The delivery line 14 opens into a space 15 which merges into a chamber 16, the shoulder of these two spaces forming a valve seat 17 for a seat valve body 18 of a pressure compensator 20. This is slidably guided in a housing bore 19 and is loaded on its side facing away from the closing cone 19 'by a compression spring 21 which is located in a pressure chamber 22. A line 23 opens into the pressure chamber, which leads to an annular groove 24 on a slide bore 25, in which a control slide 26 is slidably guided. The control slide can be adjusted proportionally, electromagnetically, mechanically or hydraulically, according to a setpoint.

Am Steuerschieber 26 sind in einem etwa mittleren Bereich zwei Ringnuten 28, 29 ausgebildet, die nur durch einen schmalen Bund 30 voneinander getrennt sind, dessen Außendurchmesser dem des Steuerschiebers entspricht. Dieser weist noch eine zweite, breitere Ringnut 31 auf, die in eine kegelig ausgebildete Zone 32 übergeht. Rechts von der Ringnut 24 ist an der Schieberbohrung 25 noch eine Ringnut 33 ausgebildet, links von der Ringnut 24 befinden sich an der Schieberbohrung noch drei Ringnuten 34, 35, 36. Von der Ringnut 33 führt eine Leitung 38 zur Förderleitung 14. Von der Leitung 38 geht eine Leitung 39 aus, die zu einem einfach wirkenden Hydrozylinder 40 führt und in der eine Drossel 41 angeordnet ist. Die von der Druckkammer 22 zur Ringnut 24 führende Leitung 23 mündet ebenfalls in die Leitung 39 ; die Drossel 41 liegt zwischen diesem Mündungspunkt und demjenigen der Leitung 39 in die Leitung 38. Vor dem Hydrozylinder 40 ist ein Rückschlagventil 42 angeordnet.In an approximately central region, two annular grooves 28, 29 are formed on the control slide 26, which are separated from one another only by a narrow collar 30, the outer diameter of which corresponds to that of the control slide. This also has a second, wider annular groove 31 which merges into a conical zone 32. To the right of the annular groove 24, an annular groove 33 is formed on the slide bore 25, to the left of the annular groove 24 there are three annular grooves 34, 35, 36 on the slide bore. A line 38 leads from the annular groove 33 to the delivery line 14. From the line 38 goes out a line 39, which leads to a single-acting hydraulic cylinder 40 and in which a throttle 41 is arranged. The line 23 leading from the pressure chamber 22 to the annular groove 24 likewise opens into the line 39; the throttle 41 lies between this mouth and that of the line 39 in the line 38. A check valve 42 is arranged in front of the hydraulic cylinder 40.

Von der Ringnut 35 an der Schieberbohrung 25 führt eine Leitung 43 zur Rücklaufleitung 12, die ausgeht von einer Kammer 47, die Teil einer Schieberbohrung 44 ist, in der ein Steuerschieber 45 gleitend geführt ist. Auf ihn wirkt eine in der Kammer 47 angeordnete Druckfeder 46 ein. An der Schieberbohrung 44 sind vier Ringnuten 48 bis 51 ausgebildet sowie eine der Kammer 47 gegenüberliegende Kammer 52. Von der Ringnut 48 führt eine Leitung 53 zur Leitung 39 ; sie mündet dort vor dem Rückschlagventil 42. Von der Ringnut 49 führt eine Leitung 54 zur Ringnut 36 an der Schieberbohrung 25. Von der Ringnut 50 führt einerseits eine Leitung 55 zur Leitung 38, andererseits führt eine Leitung 56 zu einer Leitung 57, welche die Kammer 52 und die Ringnut 34 miteinander verbindet. Von der Ringnut 51 führt eine Leitung 58 zur Leitung 56. In den beiden Leitungszweigen 56', 56" der Leitung 56 ist je eine Drossel 59 bzw. 60 angeordnet. Am Steuerschieber 45 sind zwei Ringnuten 63, 64 ausgebildet. Von der Kammer 16 der Druckwaage 20 führt eine Rückleitung 61 zur Rücklaufleitung 12.From the annular groove 35 on the slide bore 25, a line 43 leads to the return line 12, which starts from a chamber 47, which is part of a slide bore 44, in which a control slide 45 is slidably guided. A compression spring 46 arranged in the chamber 47 acts on it. Four annular grooves 48 to 51 are formed on the slide bore 44, and a chamber 52 opposite the chamber 47. A line 53 leads from the annular groove 48 to the line 39; it opens there in front of the check valve 42. From the annular groove 49, a line 54 leads to the annular groove 36 at the slide bore 25. From the annular groove 50, on the one hand a line 55 leads to the line 38, on the other hand a line 56 leads to a line 57, which is the chamber 52 and the annular groove 34 connects to one another. A line 58 leads from the ring groove 51 to the line 56. A throttle 59 or 60 is arranged in each of the two line branches 56 ', 56 "of the line 56. Two ring grooves 63, 64 are formed on the control slide 45 Pressure compensator 20 leads a return line 61 to return line 12.

Das von der Pumpe 10 geförderte Druckmittel strömt gegen den Ventilkörper 18. Die Druckfeder 21 würde diesen auf seinen Ventilsitz 17 drücken, stünde dem nicht der Weg über die Drossel 41 zum Behälter 13 entgegen, und zwar über die Leitungen 39, 53, die Ringnut 63 am Steuerschieber 45, die miteinander verbundenen Ringnuten 48, 49, die Leitung 54, die miteinander verbundenen Ringnuten 35, 36 an der Schieberbohrung 25 sowie die Leitung 43. An der Drossel 41 entsteht eine Druckdifferenz, durch welche der Ventilkörper 18 in Offenstellung gehalten wird. Dies ergibt einen Neutralumläuf, in dem das von der Pumpe 10 geförderte Druckmittel unter niedrigem Druckverlust abfließt, und zwar über die Kammer 16, die Rückleitung 61 sowie die Rücklaufleitung 12. Über die Drossel 41 fließt stets ein kleiner, annähernd konstanter Steuerstrom - wie zuvor beschrieben - zum Behälter 13 ; die Feder 21 hält die Druckdifferenz an der Drossel 41 nahezu konstant.The pressure medium conveyed by the pump 10 flows against the valve body 18. The compression spring 21 would press it onto its valve seat 17 if it were not for the path via the throttle 41 to the container 13, namely via the lines 39, 53, the annular groove 63 on the control slide 45, the interconnected annular grooves 48, 49, the line 54, the interconnected annular grooves 35, 36 on the slide bore 25 and the line 43. A pressure difference arises at the throttle 41, by means of which the valve body 18 is held in the open position. This results in a neutral circulation, in which the pressure medium delivered by the pump 10 flows off with a low pressure drop, specifically via the chamber 16, the return line 61 and the return line 12. A small, approximately constant control current always flows via the throttle 41 - as previously described - to container 13; the spring 21 keeps the pressure difference at the throttle 41 almost constant.

Wird der Steuerschieber 26 so nach links bewegt, daß dabei die Verbindung für den Steuerstrom zwischen den Ringnuten 35 und 36 angedrosselt wird, dann steigt der Druck im System. Dieser Druck pflanzt sich auch in die Kammer 52 fort, und zwar über die Leitung 55, die Ringnut 50, die Leitung 56 und die Drosseln 59, 60 sowie die Leitung 57. Entsprechend der Drucksteigerung hat sich der Ventilkörper 18 seinem Ventilsitz 17 genähert. Dadurch ist der Neutralumlauf ebenfalls angedrosselt. Der an der Pumpe 10 herrschende Druck ist nur um die nahezu konstant bleibende Druckdifferenz an der Drossel 41 höher als der in der Ringnut 36 der Schieberbohrung 25 angedrosselte Druck.If the control slide 26 is moved to the left so that the connection for the control current between the ring grooves 35 and 36 is throttled, then the pressure in the system increases. This pressure also propagates into the chamber 52, specifically via the line 55, the annular groove 50, the line 56 and the throttles 59, 60 and the line 57. The valve body 18 has approached its valve seat 17 in accordance with the pressure increase. As a result, the neutral circulation is also throttled. The pressure prevailing at the pump 10 is only higher by the almost constant pressure difference at the throttle 41 than the throttled pressure in the annular groove 36 of the slide bore 25.

Überschreitet der Druck in der Kammer 52 das von der Druckfeder 46 gesetzte Maß, dann bewegt sich der Steuerschieber 25 an seinen linken Endanschlag 45". Dadurch wird die Verbindung zwischen den Ringnuten 48, 49 gesperrt, mit der Folge, daß zunächst kein Druckmittel mehr durch die Drossel 41 strömen kann. Das deshalb ausbleibende Druckgefälle stört das Gleichgewicht am Ventilkörper 18, der sich unter der Wirkung der Druckfeder 21 seinem Ventilsitz 17 solange nähert, bis der im System steigende Druck die Last am Hydrozylinder 40 bewegen kann. Die Druckfeder 46 entscheidet also, bis zu welchem Druck das sogenannte Festdrosseln bei Annäherung an den Betriebszustand « Heben » möglich ist. Zweckmäßigerweise wird die Feder 46 so ausgelegt, daß dieser Druck möglichst wenig höher ist als der Neutralumlaufdruck, für den die Druckfeder 21 der Druckwaage verantwortlich ist.If the pressure in the chamber 52 exceeds the dimension set by the compression spring 46, the control slide 25 moves to its left end stop 45 ". This blocks the connection between the annular grooves 48, 49, with the result that no pressure medium is initially passed through can flow the throttle 41. The pressure drop which is therefore absent disturbs the equilibrium on the valve body 18 which, under the action of the compression spring 21, approaches its valve seat 17 until the pressure rising in the system can move the load on the hydraulic cylinder 40. The compression spring 46 therefore decides up to which pressure the so-called fixed throttling is possible when approaching the operating state “lifting.” The spring 46 is expediently designed such that this pressure is as little as possible higher than the neutral circulation pressure for which the pressure spring 21 of the pressure compensator is responsible.

Das Rückschlagventil 42 sichert die Last am Hydrozylinder gegen Herabfallen, solange der Druck im System noch zu niedrig ist, um « Heben » zu ermöglichen. Die Last am Hydrozylinder wird mindestens mit dem durch die Drossel 41 fliessenden Steuerstrom gehoben. Für den Fall, daß der Steuerschieber 26 noch weiter links steht, wobei der Bund 30 die Verbindung von der Ringnut 35 zur Ringnut 36 unterbricht, aber die Verbindung von der Ringnut 24 zur Ringnut 32 über die kegelige Zone 32 aufgesteuert wird - diese Schieberstellung entspricht einer größeren Regelabweichung im Sinne von Heben - fließt ein dem Querschnitt (Drosselstelle) an der kegligen Zone 32 proportionaler Zusatzstrom zum Hydrozylinder, und zwar über die Leitung 38, die Ringnuten 33, 24 und die Leitung 23 zur Leitung 39. Die Drosselstelle an der kegligen Zone 32 wird nur jetzt wirksam. Sie liegt parallel zur Drossel 41.The check valve 42 secures the load on the hydraulic cylinder against falling as long as the pressure in the system is still too low to allow “lifting”. The load on the hydraulic cylinder is raised at least with the control current flowing through the choke 41. In the event that the control slide 26 is still further to the left, the collar 30 interrupting the connection from the annular groove 35 to the annular groove 36, but the connection from the annular groove 24 to the annular groove 32 is opened via the conical zone 32 - this slide position corresponds to one Larger control deviation in the sense of lifting - an additional flow proportional to the cross-section (throttle point) at the conical zone 32 flows to the hydraulic cylinder, namely via line 38, the ring grooves 33, 24 and line 23 to line 39. The throttle point at the conical zone 32 only takes effect now. It lies parallel to throttle 41.

Anhaltendes Heben veranlaßt den Steuerschieber 26 dazu, sich wieder nach rechts zu bewegen (Rückführung im Regelkreis). Der Bund 30 stellt wieder Verbindung her zwischen den Ringnuten 35, 36. Dies führt jedoch zu keinerlei Reaktion, da der Steuerschieber 45 noch immer die Verbindung zwischen den Ringnuten 48, 49 sperrt.Prolonged lifting causes the spool 26 to move to the right again (feedback in the control loop). The collar 30 again establishes a connection between the ring grooves 35, 36. However, this does not lead to any reaction since the control slide 45 still blocks the connection between the ring grooves 48, 49.

Bewegt sich der Steuerschieber 26 noch weiter nach rechts, so daß der Bund 30 etwa in der Mitte der Ringnut 35 steht, dann wird Verbindung hergestellt von der Ringnut 35 über die Ringnut 29 am Steuerschieber zur Ringnut 34. Nun kann Druckmittel aus der Leitung 55 über die Ringnuten 50, 64 und 51, die Leitungen 58, 56, die Drossel 60 und die Leitung 57 sowie die Ringnuten 34, 35 zum Behälter 13 abströmen. An der Drossel 60 entsteht ein Druckabfall, der in der. Kammer 52 über die Leitung 57 eine Druckminderung hervorruft.If the control slide 26 moves further to the right, so that the collar 30 is approximately in the middle of the annular groove 35, then a connection is made from the annular groove 35 via the annular groove 29 on the control slide to the annular groove 34 the annular grooves 50, 64 and 51, the lines 58, 56, the throttle 60 and the line 57 and the annular grooves 34, 35 flow out to the container 13. At the throttle 60, a pressure drop occurs, which in the. Chamber 52 causes a pressure reduction via line 57.

Dabei spielt die Druckmittelverbindung über die Drossel 59 praktisch keine Rolle, da ihr Querschnitt gegenüber dem Durchgang zwischen den Ringnuten 50, 51 vernachlässigbar klein ist. Doch die Bewegung des Steuerschiebers 26 nach rechts hält an (Rückführung), da die Last im Hydrozylinder 40 weiter angehoben wird. Dabei ist die Entlastung zwischen den Ringnuten 48, 49 durch den Steuerschieber 45 weiterhin gesperrt.The pressure medium connection via the throttle 59 is practically irrelevant since its cross section is negligibly small compared to the passage between the ring grooves 50, 51. However, the movement of the control slide 26 to the right continues (feedback), since the load in the hydraulic cylinder 40 is raised further. The relief between the ring grooves 48, 49 is still blocked by the control slide 45.

Bei genügend großer Öffnung zwischen den Ringnuten 35 und 34 fällt der Druck in der Kammer 52 soweit, daß es der Feder 46 gelingt, den Steuerschieber 45 nach rechts zu verschieben. Dadurch wird der Durchgang zwischen den Ringnuten 50, 51 angedrosselt. So gewinnt die Drossel 59 an Bedeutung - der Druck in der Kammer 52 fällt rapide ab, da der Druckabbau nun über zur Drossel 60 in Reihe geschaltete zusätzliche Drosseln erfolgt, und zwar die Drossel 59, dazu parallel noch der angedrosselte Durchgang zwischen den Kammern 50, 51. Dieser rapide Druckabbau läßt den Durchgang zwischen den Ringnuten 50, 51 weiter schrumpfen - der Steuerschieber 45 verliert sein Gleichgewicht, er « kippt ». Das ist auch beabsichtigt, denn « Festdrosseln beim Verlassen von « Heben ist nur möglich, wenn der Steuerschieber 45 in allen Stellungen, bei denen der Durchgang zwischen den Ringnuten 48, 49 angedrosselt ist, stabiles Gleichgewicht findet. Befindet sich der Steuerschieber 45 wieder an seinem rechten Anschlag 45', so ist die Verbindung zwischen den Ringnuten 48, 49 weit geöffnet, so daß der über die Drossel 41 fließende Steuerstrom ungehindert zum Behälter 13 gelangen kann - wie eingangs beschrieben. Der Ventilkörper 18 der Druckwaage hat weit geöffnet. Dies ist die eingangs geschilderte Situation, nur der Steuerschieber 26 steht etwas weiter rechts.With a sufficiently large opening between the annular grooves 35 and 34, the pressure in the chamber 52 drops to such an extent that the spring 46 succeeds in displacing the control slide 45 to the right. As a result, the passage between the ring grooves 50, 51 is throttled. The throttle 59 thus becomes more important - the pressure in the chamber 52 drops rapidly, since the pressure is now reduced by means of additional throttles connected in series with the throttle 60, namely the throttle 59, and in addition the throttled passage between the chambers 50, 51. This rapid reduction in pressure causes the passage between the ring grooves 50, 51 to shrink further - the control slide 45 loses its balance, it "tilts". This is also intentional, because "fixed throttling when leaving" lifting is only possible if the control slide 45 finds a stable balance in all positions in which the passage between the ring grooves 48, 49 is throttled. If the control slide 45 is again at its right stop 45 ', the connection between the ring grooves 48, 49 is wide open, so that the control current flowing through the throttle 41 can reach the container 13 unhindered - as described at the beginning. The valve body 18 of the pressure compensator has opened wide. This is the situation described at the beginning, only the control slide 26 is a little further to the right.

Soll wieder der Betriebszustand « Heben » eintreten, dann beginnt ein neuer Zyklus.A new cycle begins if the "Lifting" operating state is to occur again.

Zum Senken der Last wird der Hydrozylinder 40 über ein willkürlich entsperrbares Rück- schlagventil 65 zum Behälter 13 entlastet.To decrease the load of the hydraulic cylinder 40 is an arbitrary unlockable non - return valve relieves 65 to the reservoir. 13

Das Ausführungsbeispiel nach Figur 2 gleicht weitgehend demjenigen nach Figur 1, weist aber folgenden Unterschied auf : Die von der Ringnut 50 zur Leitung 58 führenden Leitungen 56 und 56' samt Drossel 59 entfallen. Stattdessen führt von der Leitung 55 eine eine Drossel 66 enthaltende Leitung 67 zur Kammer 52. Daraus ist zu erkennen, daß die beiden Drosseln 60, 66 bezüglich dieser Kammer parallel geschaltet sind. Dadurch wird gegenüber dem Ausführungsbeispiel nach Figur 1 der Gradient des Druckabfalls in der Kammer 52 doppelt so hoch wie zuvor, so daß der Steuerschieber 45 schneller anspricht. An der sonstigen, zuvor beschriebenen Funktionsweise ergibt sich keine weitere Änderung.The exemplary embodiment according to FIG. 2 is largely the same as that according to FIG. 1, but has the following difference: the lines 56 and leading from the annular groove 50 to the line 58 56 'including throttle 59 are omitted. Instead, a line 67 containing a throttle 66 leads from the line 55 to the chamber 52. From this it can be seen that the two throttles 60, 66 are connected in parallel with respect to this chamber. As a result, compared to the exemplary embodiment according to FIG. 1, the gradient of the pressure drop in the chamber 52 becomes twice as high as before, so that the control slide 45 responds more quickly. There is no further change in the other mode of operation described above.

Die in der Zeichnung dargestellten Leitungen können auch Gehäusekanäle in einem gemeinsamen Ventilgehäuse sein.The lines shown in the drawing can also be housing channels in a common valve housing.

In der Druckwaage 20 kann anstelle des Schaltventils auch ein Schieberventil verwendet werden.In the pressure compensator 20, a slide valve can also be used instead of the switching valve.

Claims (5)

1. Control device for a hydraulic consuming device (40), having a pressure balance (20) and a proportionally working directional control valve (26), via which the pressure medium delivered from a pressure-medium source (10) flows in the working position at least partially to the consuming device (40), but in the neutral position flows to a container (13), and in which a line connection (14, 39) leads from the pressure-medium source (10) directly to the consuming device (40), in which line connection (14, 39) a throttle valve (41) is arranged and the differential pressure produced at the latter is active at the pressure balance (20) which controls the operating sequence from the pump delivery line (14) to the container (13), is normally closed and opens as a function of the pressure differential at the throttle valve (41), and also having a slide valve (45) loaded by a spring (46), characterised in that two lines (55, 53) which emerge from the line connection (14, 39) and on both sides from the throttle valve (41) lead to the slide valve (45), and the slide valve, in its normal position, connects the consumer-side line (39) of the line connection (14, 39), to the directional control valve (26) and separates them from one another in the operating position, that the delivery line (14) is constantly connected via at least one further throttle valve (66) to the end face (52) of the slide valve (45), which end face (52) is opposite the spring (46), and that, in the neutral position of the directional control valve (26), the pressure medium delivered from the pressure-medium source (10) flows via the throttle valve (41), the slide valve (45) and the directional control valve (26) to the container (13).
2. Device according to Claim 1, characterised in that two throttle valves (59, 60) connected one behind the other are arranged in the constant connection (55, 56 ; 55, 67) between the delivery line (14) and the end face (52) or the chamber located there of the slide valve (45), with a short-circuit line (58) being open in the operating position of the slide valve, which short-circuit line (58) opens out between the two throttle valves (59, 60) and enables a pressure medium to flow from the delivery line (14) to the chamber (52) only via the second throttle valve (60) (Fig. 1).
3. Device according to Claim 1 or 2, characterised in that the pressure balance (20) is designed as a seat valve and has a valve body (18) loaded by a spring (21), and that a line connection (23) emerges from the space (22) which accommodates the spring and is loaded by pressure behind the throttle valve (41), which line connection (23) leads on the one hand to the consuming device (40) and on the other hand opens out at an annular groove (24) made on the directional control valve (26), which annular groove (24) can be connected to a line (38) by means of a collar (32) made on the control slide of the directional control valve, which line (38) leads to the delivery line (14).
4. Device according to one of Claims 1 to 3, characterised in that a line (55) emerges from an annular groove (33) made on the directional control valve (26), which annular groove (33) is in connection with the pump delivery line (14), which line (55) leads to an annular groove (50) of the slide valve (45), which annular groove (50) can be brought into connection with a second annular groove (51) by means of control slide of the slide valve, that, from one (50) of these two annular grooves, a line connection (56, 57) containing the two throttle valves (59, 60) leads on the one hand to the directional control valve (26) and on the other hand to the end face (52) of the slide valve (45), which end face (52) is opposite the spring (46), and that a line connection (58) emerges from the other annular groove (51), which line connection (58) opens into the line (56) between the two throttle valves (59, 60).
5. Control device according to Claim 1, characterised in that two throttle valves (60, 66) connected in parallel are arranged in the constant connection (55, 67) between the delivery line (14) and the end face (52) of the slide valve (45), which end face (52) is opposite the spring (46), one (66) of which throttle valves (60, 66) is constantly active, and the other (60) is only active when the slide valve (45) is located in the operating position (Fig. 2).
EP82107131A 1981-08-20 1982-08-06 Hydraulic motor control device Expired EP0072952B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3132904 1981-08-20
DE3132904 1981-08-20
DE3200868 1982-01-14
DE19823200868 DE3200868A1 (en) 1981-08-20 1982-01-14 CONTROL DEVICE FOR A HYDRAULIC CONSUMER

Publications (3)

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EP0072952A2 EP0072952A2 (en) 1983-03-02
EP0072952A3 EP0072952A3 (en) 1984-08-01
EP0072952B1 true EP0072952B1 (en) 1986-05-07

Family

ID=25795396

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82107131A Expired EP0072952B1 (en) 1981-08-20 1982-08-06 Hydraulic motor control device

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EP (1) EP0072952B1 (en)
DE (2) DE3200868A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3909291C2 (en) * 1989-03-21 1998-10-29 Heilmeier & Weinlein Directional control valve with pressure compensator
IT1272019B (en) * 1992-03-21 1997-06-10 Barmag Barmer Maschf HYDRAULIC CONTROL DEVICE
DE4219552C2 (en) * 1992-06-15 1996-03-07 Rexroth Mannesmann Gmbh Pilot operated two-way valve with adjustable, pressure-independent closing time

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1928896B1 (en) * 1969-06-06 1970-11-12 Internat Harvester Co Mbh Control device for a hydraulic power transmission, in particular for a tractor hydraulics
DE2617008A1 (en) * 1976-04-17 1977-11-03 Bosch Gmbh Robert CONTROL DEVICE FOR HYDRAULIC POWER TRANSFER

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH266725A (en) * 1945-05-21 1950-02-15 Denison Eng Co Hydraulic device for operating machine tools.
US3951162A (en) * 1971-11-03 1976-04-20 Koehring Company Control valve with flow control means
US4184410A (en) * 1978-03-15 1980-01-22 Caterpillar Tractor Co. Low pressure signal driven flow control system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1928896B1 (en) * 1969-06-06 1970-11-12 Internat Harvester Co Mbh Control device for a hydraulic power transmission, in particular for a tractor hydraulics
DE2617008A1 (en) * 1976-04-17 1977-11-03 Bosch Gmbh Robert CONTROL DEVICE FOR HYDRAULIC POWER TRANSFER

Also Published As

Publication number Publication date
DE3270997D1 (en) 1986-06-12
EP0072952A2 (en) 1983-03-02
EP0072952A3 (en) 1984-08-01
DE3200868A1 (en) 1983-03-03

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