EP2339185B1 - Hydraulic device - Google Patents
Hydraulic device Download PDFInfo
- Publication number
- EP2339185B1 EP2339185B1 EP20090015873 EP09015873A EP2339185B1 EP 2339185 B1 EP2339185 B1 EP 2339185B1 EP 20090015873 EP20090015873 EP 20090015873 EP 09015873 A EP09015873 A EP 09015873A EP 2339185 B1 EP2339185 B1 EP 2339185B1
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- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- line
- switched
- pumps
- 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.)
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Classifications
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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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
- F15B2211/20584—Combinations of pumps with high and low capacity
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
- F15B2211/20592—Combinations of pumps for supplying high and low pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/265—Control of multiple pressure sources
- F15B2211/2654—Control of multiple pressure sources one or more pressure sources having priority
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
- F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
Definitions
- the invention relates to a hydraulic control specified in the preamble of claim 1. Art.
- the larger flow rate of a pump via a circulation valve to the tank is derived as soon as there is a predetermined pressure value in the main line.
- the circulation valve is switched by a spring into the blocking position, so that the blocking position is present as long as there is no system pressure. Consequently, the common drive motor of the pumps must start against counterpressure, which is unfavorable for an AC motor, for example. Further, since the circulation valve operates leak-prone, after the pump with the larger flow rate promotes the tank, the pump with the smaller flow rate compensate for this leakage, which may mean that the total achievable with the smaller flow maximum pressure is limited or achieved only slowly or can not be kept.
- the invention has for its object to improve a hydraulic control of the type mentioned in that u. a.
- the following requirements can be met: When the pumps are switched off, the main line and the pumps should be depressurised. When starting, there should be no back pressure until a high-performance speed is reached. If only the pump with the smaller flow rate feeds the main line, no leakage should occur to achieve very high working pressures at the consumer with relatively small flow and can hold.
- the pressure switch always works the same way and so that with the pressure unit off the pump, the discharge lines from the pumps and the main line to Tank are relieved, and the locking position with a delay and soft is switched so that the drive motor is able to start without counter-pressure. As soon as the blocking position is switched, all flow rates can be used by the consumer. Once the predetermined pressure level is reached in the main line, the larger pressure flow is derived from the pressure switch to the tank, and is generated with the smaller flow rate very high working pressure.
- the throttle which is assigned to only one pump or pressure stage, advantageously with the lowest flow or for the maximum pressure, always acts so that the same pressure difference generated and from this pressure difference, the control pressures are generated, which switch the pressure switch to the blocking position, wherein of the
- Cross section of the restrictor specifically for the pump with the smaller flow rate or the smallest flow rate or the highest Pressure level is matched, on the one hand, the correct soft switching of the pressure switch is ensured, and on the other hand, the pressure difference at high working pressure is negligible.
- Leakage is reliably avoided in the blocking position of the pressure switch when the pressure switch is a 2/2-way seat valve with leak-tight dense blocking position, which has a valve seat arranged to the passage position of a spring-loaded valve cone and arranged in the discharge line.
- valve cone has different sized pressurizing surfaces, for example, such that the loading surface for acting in the switching direction to the passage position control pressure is smaller than the loading surface for acting in the switching direction to the blocking position control pressure, for example, with the lowest possible pressure difference to ensure the proper functioning of the pressure switch via the throttle.
- the ratio of the loading areas may be between about 2: 1 and 4: 1, and is, preferably, about 3: 1.
- valve cone in the pressure switch for at least two control pressures could have at least approximately equal loading surfaces.
- the throttle cross-section of the throttle is fixed.
- the throttle is arranged interchangeable in the pressure line, for example, depending on the lower flow rate and the maximum expected maximum pressure to use a suitable throttle.
- the throttle could be an adjusting throttle whose throttle cross-section is adjustable as needed.
- the throttle cross-section of the throttle, the force of the spring of the valve cone and the loading surfaces on the valve cone are matched to one another such that when switching on by a common drive motor, preferably a single-phase AC motor, drivable pumps at first via the pressure switch located in the passage position to the tank unloaded main line the delay of the start of the drive motor facilitating delay is generated up to the blocking position from a pressure of only about 5 bar to 10 bar pressure difference across the throttle.
- a common drive motor preferably a single-phase AC motor
- the resulting delay is sufficient to first accelerate the drive motor to a sufficiently powerful speed, or to compensate for the poor efficiency of, for example, the pump with the lower or lowest flow rate forming gear pump at a speed up to 300 U / min before the blocking position the pressure switch is switched and the pressure build-up in the main line begins.
- a further non-return valve blocking in the flow direction to the discharge line can be arranged between the main line and the control valve device of the hydraulic consumer so that the system pressure is maintained at the control valve device and only the main line, the pressure lines and the pumps are depressurized when the pressure source unit is switched off.
- An expedient embodiment of the hydraulic control may be composed of a plurality of connected block sections, wherein a first block section ports for the pumps and the tank and the shut-off valve, the maximum pressure relief valve, the check valve and the throttle, a second block section the pressure switch, and a third block section the further check valve and the control valve means for the hydraulic consumer.
- These block sections can be equipped with inexpensive standard hydraulic components.
- a hydraulic control which is fed from a pressure source unit with several pumps of different flow rates, relieve the main line and the pumps with switched-off pressure source unit via a pressure switch to the tank and switch the pressure switch via a throttle with delay to the blocking position, which is associated with the pump with the lowest flow rate or the maximum pressure level and is not affected by the flow rate of each additional pump.
- a hydraulic control H in Fig. 1 for at least one consumer V (for example, a double-acting differential cylinder) is fed by operated in shutdown pressure source unit Q having at least two pumps P1, P3 with different flow rates, which suck from a tank R and are driven by a common drive motor M.
- the drive motor M may be a single-phase AC motor, which starts with difficulty against load.
- the hydraulic control H is composed, for example, in block construction of three block sections I, II, III, which are penetrated by a continuous main line P and a continuous tank line 6.
- the pumps P1, P3 are connected via separate pressure lines 2, 3 to a node 1 of the main line P.
- the pump P1 has a smaller flow rate than the pump P3.
- the pump P1 is, for example, a high-pressure pump, for example a gear pump, with which a working pressure up to, for example, 800 bar can be generated.
- a drain line 5 from the tank R in which a shut-off valve 7 (spring-loaded pressure relief valve) is arranged, which can be controlled against the spring from a pilot line 9 with control pressure, the a node 8 is tapped off downstream of the node 1 in the main line P via a diaphragm 10.
- a check valve 40 is arranged, which blocks in the flow direction to the pump P3.
- a throttle 23 is arranged in the pressure line 2, however, upstream of the node 1 and downstream of a node 22, a throttle 23 is arranged.
- the throttle 23 may, if it has a fixed throttle cross section, be placed interchangeably in the pressure line 2, or may be an adjusting throttle whose throttle cross-section can not be changed as needed.
- the throttle cross section of the throttle 23 is adapted to the smaller flow rate of the pump P1 so that a certain pressure difference, for example of about 5 bar to 10 bar, is generated, which is used to a arranged in the block section II pressure switch 16 only in dependence To control operation of the pump P1 with the lower flow rate and the lowest flow rate.
- a further discharge line 12 branches off at a node 11 to the tank R, in which a maximum pressure limiting valve 13 is arranged, which can be actuated against an adjustable spring from the main line P.
- the shut-off valve 7 is designed for example to a response pressure between 10 bar and 150 bar, while the maximum pressure relief valve 13 is set to a response pressure up to 800 bar can be.
- node 14 of the main line P branches off a discharge line 15 to the tank R (to the tank line 6), in which the pressure switch 16 is arranged.
- the pressure switch 16 has the task, with switched-off pressure source unit Q, the pressure lines 2, 3 and the main line P to relieve the tank, and shut off the discharge line 15 after switching on the pressure source unit Q with a predetermined delay, namely leak-tight shut off.
- a predetermined delay namely leak-tight shut off.
- the pressure switch 16 is a 2/2-way seat valve with a leakage-tight in both directions of flow blocking position 17 and a substantially unthrottled passage position 18.
- the 2/2-way seat valve is connected by a spring 19 in the switching direction to the passage position 18 and parallel to it from a control line 20th acted upon by the node 14 and the pressure line P forth, ie the pressure downstream of the aperture 23, and in the switching direction to the blocking position 17 from a control line 21 which is connected to the node 22 and a control pressure corresponding to the pressure upstream of the aperture 23 picks up.
- a further check valve 24 is arranged in the main line P, which blocks in the flow direction to the node 14.
- the block section III includes a control valve device 25 for the consumer V, which is connected via working lines A, B to the control valve device 25.
- the working line B leads a connecting line 26 to the tank R and the tank line 6, via a pressure relief valve 27, which is adjustable to a response pressure of 10 bar to 300 bar, for example.
- the control valve device 25 is in the embodiment shown, a 4/2-way valve, which is operated either manually or by a magnet or a magnet and a pressure precontrol against spring force and at least for directional control of the consumer V is used.
- the pumps P1, P3 deliver different flow rates, the summed act on the main line P and, since the pressure switch 16 is in the passage position shown, are led to the tank R.
- a predetermined pressure difference which acts on the pressure switch 16 via the control lines 21 and 20, occurs at the throttle 23. Since the control pressure in the control line 21 is higher than the control pressure in the control line 20, as soon as a predetermined pressure difference of, for example, 5 bar to 10 bar has been generated at the throttle 23, and the pressure switch 16 is switched to the blocking position, so that the Relief line 15 is shut off.
- both pumps pump P1, P3, the pressure switch 16 is switched with a predetermined delay in the blocking position, which lasts until the predetermined pressure difference has been generated via the throttle 23 from the pump P1.
- an increasing pressure builds up in the main line P, which, when a predetermined pressure value is reached, causes the shut-off valve 7 to be switched from the blocking position shown (via the control line 9), so that the larger flow rate of the pump P3 is discharged to the tank R and the check valve 40 is in the blocking position, so that the pressure line 3 is isolated at node 1 from the main line P and the pressure line 2. Only the lower flow rate of the pump P1 is passed in the main line P to the control valve device 25.
- the pressure switch 16 in the shut-off position 17 leak-tight, no leaks occur on the pressure switch 16, so that (the check valve 40 closes leak-tight from tight) the lower flow rate of the pump P1 is sufficient to reach the desired maximum pressure up to 800 bar. Only then does the maximum pressure limiting valve 13 respond.
- the required maximum pressure for the consumer V is expediently at about 700 bar, so that the maximum pressure relief valve 13 only responds, if the risk of damage should occur.
- the load V can be moved thanks to the large total delivery, for example, in rapid traverse. Thereafter, the pressure is built up to the required maximum pressure only with the lower flow rate of the pump P1.
- the further check valve 24 blocks and eliminates the pressure difference across the throttle 23, so that the Pressure switch 16 is switched by the spring 19 back into the passage position shown.
- the pressure lines 2, 3 and the main line P are relieved again via the discharge line 15 to the tank R and the tank line 6.
- the pressure switch 16 (corresponding to the block section II in Fig. 1 ) is formed with a block-shaped housing 28 in which a valve seat 29 is provided in an inner chamber (a sleeve inserted into a bore), which cooperates with a seat surface 35 of a valve cone 32.
- the poppet 32 (shown in the blocking position of the pressure switch 16) has at both ends Beaufschlagungs vom A1, A2 for the control pressures from the control lines 21, 20 which are connected to housing chambers 33 and 34, respectively.
- the loading surface A1 for the control pressure from the control line 21 is formed on the valve cone 32 larger than the loading surface A2 for the control pressure from the control line 20.
- the ratio A1: A2 for example, be about 3: 1.
- An annular chamber 30 in the housing 28 is connected, for example, to the main pipe P, while an annular chamber 31 in the housing 28 is connected to the tank pipe 6 and the tank R.
- Fig. 3 illustrates the connection diagram on an outer side of the housing 28, wherein the control pressure is fed from the upstream of the throttle 23 to a connection representing the control line 21, from the pressure line P an opening is visible, as well as from the working lines A, B and the connecting line 26th , which pass through the housing 28, as well as the tank line 6, which is connected to the tank R.
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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)
Description
Die Erfindung betrifft eine Hydrauliksteuerung der im Oberbegriff des Patentanspruchs 1 angegebenen Art.The invention relates to a hydraulic control specified in the preamble of claim 1. Art.
Bei einer aus
Nun gibt es bei Einrichtungen, die solche Hydrauliksteuerungen benutzen, Anwendungsfälle, wie beispielsweise in einer Werkzeugmaschine, in einem tragbaren Hydraulikgerät, wie einem Drehmomentschrauber, einem Hubgerät, einer Blechschere, oder dgl., Anforderungen, gemäß denen der Verbraucher zunächst in einem Eilgang mit großer Fördermenge bewegt wird und danach bei kleiner Fördermenge hohen Arbeitsdruck benötigt. Damit kann verbunden sein, dass die Hauptleitung und die Pumpen dann drucklos geschaltet sein sollen, wenn die Pumpen abgeschaltet sind, so dass beim Anlaufen der Pumpen der Antriebsmotor, beispielsweise ein Einphasen-Wechselstrommotor, so wenig Gegendruck wie möglich zu überwinden hat, bis der Antriebsmotor auf eine ausreichende leistungsfähige Drehzahl gebracht werden konnte, wobei dann Gegendruck weich zunehmen soll. Wenn danach die Hydrauliksteuerung bei angetriebenen Pumpen in Betrieb ist, und nurmehr eine Pumpe mit kleiner Fördermenge die Hauptleitung speist, dürfen keine Leckagen im System auftreten, damit Höchstdrücke bis etwa 800 bar oder dgl. zumindest in der Hauptleitung und im Verbraucher erzielbar sind. Diese Anforderungen lassen sich bei der aus
Es ist bereits vorgeschlagen worden (europäische Patentanmeldung mit dem Aktenzeichen
Von Interesse sind ferner:
Der Erfindung liegt die Aufgabe zugrunde, eine Hydrauliksteuerung der eingangs genannten Art dahingehend zu verbessern, dass u. a. folgende Forderungen erfüllbar sind: Bei abgeschalteten Pumpen sollen die Hauptleitung und die Pumpen druckentlastet sein. Beim Anlaufen soll bis zum Erreichen einer leistungsfähigen Drehzahl kein Gegendruck herrschen. Wenn nurmehr die Pumpe mit der kleineren Fördermenge die Hauptleitung speist, soll keine Leckage auftreten, um sehr hohe Arbeitsdrücke am Verbraucher mit relativ kleiner Fördermenge erreichen und halten zu können.The invention has for its object to improve a hydraulic control of the type mentioned in that u. a. The following requirements can be met: When the pumps are switched off, the main line and the pumps should be depressurised. When starting, there should be no back pressure until a high-performance speed is reached. If only the pump with the smaller flow rate feeds the main line, no leakage should occur to achieve very high working pressures at the consumer with relatively small flow and can hold.
Die gestellte Aufgabe wird mit den Merkmalen des Patentanspruchs 1 gelöst.The stated object is achieved with the features of claim 1.
Unabhängig davon, wie viele Pumpen im Druckquellenaggregat vorgesehen sind, und wie und bei welchem Druck sich die Fördermenge in der Hauptleitung ändert, arbeitet die Druckweiche stets gleichartig und so, dass bei abgeschaltetem Druckaggregat die Pumpen förderseitig, die Druckleitungen von den Pumpen und die Hauptleitung zum Tank entlastet sind, und die Sperrstellung mit einer Verzögerung und weich geschaltet wird, so dass der Antriebsmotor ohne Gegendruck anzulaufen vermag. Sobald die Sperrstellung geschaltet ist, sind alle Fördermengen für den Verbraucher nutzbar. Sobald das vorbestimmte Druckniveau in der Hauptleitung erreicht ist, wird von der Druckweiche die größere Fördermenge zum Tank abgeleitet, und wird mit der kleineren Fördermenge sehr hoher Arbeitsdruck erzeugt. Die Drossel, die nur der einen Pumpe oder Druckstufe, zweckmäßig mit der geringsten Fördermenge oder für den Höchstdruck, zugeordnet ist, wirkt stets so, dass die gleiche Druckdifferenz erzeugt und aus dieser Druckdifferenz die Steuerdrücke erzeugt werden, die die Druckweiche zur Sperrstellung schalten, wobei derRegardless of how many pumps are provided in the pressure source unit, and how and at what pressure changes the flow rate in the main line, the pressure switch always works the same way and so that with the pressure unit off the pump, the discharge lines from the pumps and the main line to Tank are relieved, and the locking position with a delay and soft is switched so that the drive motor is able to start without counter-pressure. As soon as the blocking position is switched, all flow rates can be used by the consumer. Once the predetermined pressure level is reached in the main line, the larger pressure flow is derived from the pressure switch to the tank, and is generated with the smaller flow rate very high working pressure. The throttle, which is assigned to only one pump or pressure stage, advantageously with the lowest flow or for the maximum pressure, always acts so that the same pressure difference generated and from this pressure difference, the control pressures are generated, which switch the pressure switch to the blocking position, wherein of the
Querschnitt der Drossel speziell auf die Pumpe mit der kleineren Fördermenge bzw. der kleinsten Fördermenge oder der höchsten Druckstufe abgestimmt ist, dass einerseits das korrekte weiche Schalten der Druckweiche sichergestellt wird, und andererseits die Druckdifferenz bei hohem Arbeitsdruck vernachlässigbar gering ist. Für das ordnungsgemäße Arbeiten der Druckweiche reicht eine Druckdifferenz aus, die bei beispielsweise einem Maximaldruck von etwa 800 bar zu einem ohne weiteres in Kauf zu nehmenden Verlust von etwa 1 % oder geringfügig mehr führt. In der Sperrstellung der Druckweiche tritt keine Leckage auf, so dass die Pumpe mit der niedrigeren Fördermenge den hohen Arbeitsdruck problemlos zu erzeugen und halten vermag.Cross section of the restrictor specifically for the pump with the smaller flow rate or the smallest flow rate or the highest Pressure level is matched, on the one hand, the correct soft switching of the pressure switch is ensured, and on the other hand, the pressure difference at high working pressure is negligible. For proper operation of the pressure weir, a pressure difference sufficient, for example, a maximum pressure of about 800 bar to a readily be accepted loss of about 1% or slightly more. In the blocking position of the pressure switch no leakage occurs, so that the pump with the lower flow rate can easily produce and maintain the high working pressure.
Leckage wird in der Sperrstellung der Druckweiche zuverlässig vermieden, wenn die Druckweiche ein 2/2-Wegesitzventil mit leckagefrei dichter Sperrstellung ist, das einen zur Durchgangsstellung von einer federbeaufschlagten Ventilkegel und einen in der Entlastungsleitung angeordneten Ventilsitz aufweist.Leakage is reliably avoided in the blocking position of the pressure switch when the pressure switch is a 2/2-way seat valve with leak-tight dense blocking position, which has a valve seat arranged to the passage position of a spring-loaded valve cone and arranged in the discharge line.
Hierbei kann es zweckmäßig sein, wenn der Ventilkegel unterschiedlich große Druckbeaufschlagungsflächen aufweist, beispielsweise derart, dass die Beaufschlagungsfläche für den in Schaltrichtung zur Durchgangsstellung wirkenden Steuerdruck kleiner ist als die Beaufschlagungsfläche für den in der Schaltrichtung zur Sperrstellung beaufschlagenden Steuerdruck, beispielsweise um mit einer möglichst geringen Druckdifferenz über die Drossel das ordnungsgemäße Arbeiten der Druckweiche sicherzustellen. Das Verhältnis der Beaufschlagungsflächen kann zwischen etwa 2 : 1 und 4 : 1 liegen, und beträgt, vorzugsweise, etwa 3 : 1.It may be expedient if the valve cone has different sized pressurizing surfaces, for example, such that the loading surface for acting in the switching direction to the passage position control pressure is smaller than the loading surface for acting in the switching direction to the blocking position control pressure, for example, with the lowest possible pressure difference to ensure the proper functioning of the pressure switch via the throttle. The ratio of the loading areas may be between about 2: 1 and 4: 1, and is, preferably, about 3: 1.
Bei einer alternativen Ausführungsform könnte der Ventilkegel in der Druckweiche für beide Steuerdrücke zumindest annähernd gleich große Beaufschlagungsflächen aufweisen.In an alternative embodiment, the valve cone in the pressure switch for at least two control pressures could have at least approximately equal loading surfaces.
Bei einer zweckmäßigen Ausführungsform ist der Drosselquerschnitt der Drossel festgelegt. Jedoch ist die Drossel austauschbar in der Druckleitung angeordnet, um beispielsweise abhängig von der niedrigeren Fördermenge und den maximal zu erwartenden Höchstdruck eine jeweils passende Drossel einzusetzen.In an expedient embodiment, the throttle cross-section of the throttle is fixed. However, the throttle is arranged interchangeable in the pressure line, for example, depending on the lower flow rate and the maximum expected maximum pressure to use a suitable throttle.
Alternativ könnte es sich bei der Drossel um eine Verstelldrossel handeln, deren Drosselquerschnitt nach Bedarf verstellbar ist.Alternatively, the throttle could be an adjusting throttle whose throttle cross-section is adjustable as needed.
Bei einer konkreten, zweckmäßigen Ausführungsform sind der Drosselquerschnitt der Drossel, die Kraft der Feder des Ventilkegels und die Beaufschlagungsflächen am Ventilkegel derart aufeinander abgestimmt, dass bei Einschalten der durch einen gemeinsamen Antriebsmotor, vorzugsweise einem Einphasen-Wechselmotor, antreibbaren Pumpen bei zunächst über die in der Durchgangsstellung befindliche Druckweiche zum Tank entlasteter Hauptleitung die das Anlaufen des Antriebsmotors erleichternde Verzögerung bis zur Sperrstellung aus einer nur etwa 5 bar bis 10 bar betragenden Druckdifferenz über die Drossel generiert wird. Die dadurch entstehende Verzögerung reicht aus, den Antriebsmotor zunächst bis auf eine ausreichend leistungsfähige Drehzahl zu beschleunigen, oder dem schlechten Wirkungsgrad einer beispielsweise die Pumpe mit der niedrigeren oder niedrigsten Fördermenge bildenden Zahnradpumpe bei einer Drehzahl bis beispielsweise 300 U/min zu kompensieren, ehe die Sperrstellung der Druckweiche geschaltet ist und der Druckaufbau in der Hauptleitung einsetzt.In a concrete, expedient embodiment, the throttle cross-section of the throttle, the force of the spring of the valve cone and the loading surfaces on the valve cone are matched to one another such that when switching on by a common drive motor, preferably a single-phase AC motor, drivable pumps at first via the pressure switch located in the passage position to the tank unloaded main line the delay of the start of the drive motor facilitating delay is generated up to the blocking position from a pressure of only about 5 bar to 10 bar pressure difference across the throttle. The resulting delay is sufficient to first accelerate the drive motor to a sufficiently powerful speed, or to compensate for the poor efficiency of, for example, the pump with the lower or lowest flow rate forming gear pump at a speed up to 300 U / min before the blocking position the pressure switch is switched and the pressure build-up in the main line begins.
Aus Sicherheitsgründen kann zwischen der Hauptleitung und der Steuerventileinrichtung des Hydroverbrauchers ein in Strömungsrichtung zur Entlastungsleitung sperrendes weiteres Rückschlagventil angeordnet sein, so dass der Systemdruck an der Steuerventileinrichtung gehalten und nur die Hauptleitung, die Druckleitungen und die Pumpen bei abgeschaltetem Druckquellenaggregat druckentlastet sind.For safety reasons, a further non-return valve blocking in the flow direction to the discharge line can be arranged between the main line and the control valve device of the hydraulic consumer so that the system pressure is maintained at the control valve device and only the main line, the pressure lines and the pumps are depressurized when the pressure source unit is switched off.
Eine zweckmäßige Ausführungsform der Hydrauliksteuerung kann aus mehreren verbundenen Blocksektionen zusammengesetzt sein, wobei eine erste Blocksektion Anschlüsse für die Pumpen und den Tank sowie das Abschaltventil, das Höchstdruckbegrenzungsventil, das Rückschlagventil und die Drossel, eine zweite Blocksektion die Druckweiche, und eine dritte Blocksektion das weitere Rückschlagventil und die Steuerventileinrichtung für den Hydroverbraucher aufweisen. Diese Blocksektionen können mit kostengünstigen Standard-Hydraulikkomponenten ausgestattet sein.An expedient embodiment of the hydraulic control may be composed of a plurality of connected block sections, wherein a first block section ports for the pumps and the tank and the shut-off valve, the maximum pressure relief valve, the check valve and the throttle, a second block section the pressure switch, and a third block section the further check valve and the control valve means for the hydraulic consumer. These block sections can be equipped with inexpensive standard hydraulic components.
Im Kern wird vorgesehen, in einer Hydrauliksteuerung, die aus einem Druckquellenaggregat mit mehreren Pumpen unterschiedlicher Fördermengen gespeist wird, die Hauptleitung und die Pumpen bei abgeschaltetem Druckquellenaggregat über eine Druckweiche zum Tank zu entlasten und die Druckweiche über eine Drossel mit Verzögerung in die Sperrstellung zu schalten, die der Pumpe mit der geringsten Fördermenge bzw. der Höchstdruckstufe zugeordnet ist und durch die Fördermenge jeder weiteren Pumpe nicht beeinflusst wird.Essentially, it is provided in a hydraulic control, which is fed from a pressure source unit with several pumps of different flow rates, relieve the main line and the pumps with switched-off pressure source unit via a pressure switch to the tank and switch the pressure switch via a throttle with delay to the blocking position, which is associated with the pump with the lowest flow rate or the maximum pressure level and is not affected by the flow rate of each additional pump.
Anhand der Zeichnungen wird eine Ausführungsform des Erfindungsgegenstandes erläutert. Es zeigen:
- Fig. 1
- ein Blockdiagramm einer Hydrauliksteuerung für einen Verbraucher,
- Fig. 2
- eine Seitenansicht einer Blocksektion der Hydrauliksteuerung, im Schnitt, und
- Fig. 3
- die Seitenansicht der Blocksektion, ungeschnitten.
- Fig. 1
- a block diagram of a hydraulic control for a consumer,
- Fig. 2
- a side view of a block section of the hydraulic control, in section, and
- Fig. 3
- the side view of the block section, uncut.
Eine Hydrauliksteuerung H in
Stromab des Knotens 8 in der Hauptleitung P zweigt eine weitere Ablassleitung 12 an einem Knoten 11 zum Tank R ab, in der ein Höchstdruckbegrenzungsventil 13 angeordnet ist, das gegen eine einstellbare Feder aus der Hauptleitung P aufsteuerbar ist. Das Abschaltventil 7 ist beispielsweise auf einen Ansprechdruck zwischen 10 bar und 150 bar ausgelegt, während das Höchstdruckbegrenzungsventil 13 auf einen Ansprechdruck bis zu 800 bar eingestellt sein kann. An einem in der Blocksektion II angeordneten Knoten 14 der Hauptleitung P zweigt eine Entlastungsleitung 15 zum Tank R (zur Tankleitung 6) ab, in der die Druckweiche 16 angeordnet ist. Die Druckweiche 16 hat die Aufgabe, bei abgeschaltetem Druckquellenaggregat Q die Druckleitungen 2, 3 und die Hauptleitung P zum Tank zu entlasten, und nach dem Einschalten des Druckquellenaggregats Q mit einer vorbestimmten Verzögerung die Entlastungsleitung 15 abzusperren, und zwar leckagefrei dicht abzusperren. Während der Verzögerungszeit bis zum Absperren der Entlastungsleitung 15 fördern die Pumpen P1, P3 somit über die Hauptleitung P zum Tank, so dass der Antriebsmotor M ohne nennenswerten Gegendruck anzulaufen vermag.Downstream of the node 8 in the main line P, a
Die Druckweiche 16 ist ein 2/2-Wegesitzventil mit einer in beiden Strömungsrichtungen leckagefrei dichten Sperrstellung 17 und einer im Wesentlichen ungedrosselten Durchgangsstellung 18. Das 2/2-Wegesitzventil wird durch eine Feder 19 in Schaltrichtung zur Durchgangsstellung 18 und parallel dazu aus einer Steuerleitung 20 von dem Knoten 14 bzw. der Druckleitung P her beaufschlagt, d.h. dem Druck stromab der Blende 23, und in Schaltrichtung zur Sperrstellung 17 aus einer Steuerleitung 21, die am Knoten 22 angeschlossen ist und einen Steuerdruck entsprechend dem Druck stromauf der Blende 23 abgreift.The
In der Blocksektion III ist in der Hauptleitung P ein weiteres Rückschlagventil 24 angeordnet, das in Strömungsrichtung zum Knoten 14 sperrt. Ferner enthält die Blocksektion III eine Steuerventileinrichtung 25 für den Verbraucher V, der über Arbeitsleitungen A, B an die Steuerventileinrichtung 25 angeschlossen ist. Von beispielsweise der Arbeitsleitung B führt eine Verbindungsleitung 26 zum Tank R bzw. zur Tankleitung 6, und zwar über ein Druckbegrenzungsventil 27, das beispielsweise auf einen Ansprechdruck von 10 bar bis 300 bar einstellbar ist. Die Steuerventileinrichtung 25 ist in der gezeigten Ausführungsform ein 4/2-Wegeventil, das entweder manuell oder durch einen Magneten oder einen Magneten und eine Druckvorsteuerung gegen Federkraft betätigbar ist und zumindest zur Richtungssteuerung des Verbrauchers V dient.In the block section III, a
Die Hydrauliksteuerung arbeitet wie folgt:
- Bei abgeschaltetem Druckquellenaggregat Q entsteht an
der Drossel 23 keine Druckdifferenz, so dass dieDruckweiche 16von der Feder 19 in die inFig. 1 dargestellte Durchgangsstellung geschaltet ist. Dadurch sind die Hauptleitung P bis zum weiteren Rückschlagventil 24, die 2, 3 und somit die Pumpen P1, P3 zum Tank R druckentlastet. Das Abschaltventil 7,Druckleitungen das Höchstdruckbegrenzungsventil 13und das Druckbegrenzungsventil 27 sind in Sperrstellungen geschaltet.
- When switched off pressure source unit Q is formed at the
throttle 23 no pressure difference, so that thepressure switch 16 of thespring 19 in the inFig. 1 shown passage position is switched. As a result, the main line P to thefurther check valve 24, the 2, 3 and thus the pumps P1, P3 to the tank R relieved of pressure. The shut-off valve 7, the maximumpressure lines pressure limiting valve 13 and thepressure limiting valve 27 are connected in blocking positions.
Wird das Druckquellenaggregat Q eingeschaltet, so liefern die Pumpen P1, P3 unterschiedliche Fördermengen, die summiert die Hauptleitung P beaufschlagen und, da die Druckweiche 16 in der gezeigten Durchgangsstellung ist, zum Tank R geleitet werden. Dabei entsteht jedoch an der Drossel 23 eine vorbestimmte Druckdifferenz, die über die Steuerleitungen 21 und 20 auf die Druckweiche 16 wirken. Da der Steuerdruck in der Steuerleitung 21 höher ist als der Steuerdruck in der Steuerleitung 20, wird, sobald eine vorbestimmte Druckdifferenz von beispielsweise 5 bar bis 10 bar an der Drossel 23 erzeugt worden ist, und die Druckweiche 16 in die Sperrstellung geschaltet, so dass die Entlastungsleitung 15 abgesperrt ist. Obwohl beide Pumpen P1, P3 fördern, wird die Druckweiche 16 mit einer vorbestimmten Verzögerung in die Sperrstellung geschaltet, die so lange dauert, bis über die Drossel 23 von der Pumpe P1 die vorbestimmte Druckdifferenz erzeugt worden ist. Bei weiterer gemeinsamer Förderung der Pumpen P1, P3 baut sich in der Hauptleitung P ein zunehmender Druck auf, der bei Erreichen eines vorbestimmten Druckwertes dazu führt, dass das Abschaltventil 7 aus der gezeigten Sperrstellung auf Durchgang geschaltet wird (über die Steuerleitung 9), so dass die größere Fördermenge der Pumpe P3 zum Tank R abgeleitet wird und das Rückschlagventil 40 in die Sperrstellung geht, so dass die Druckleitung 3 am Knoten 1 von der Hauptleitung P und der Druckleitung 2 isoliert ist. Nurmehr die geringere Fördermenge der Pumpe P1 wird in der Hauptleitung P zur Steuerventileinrichtung 25 geleitet. Da die Druckweiche 16 in der Absperrstellung 17 leckagefrei dicht ist, treten keine Leckagen über die Druckweiche 16 auf, so dass (das Rückschlagventil 40 sperrt leckagefrei dicht ab) die geringere Fördermenge der Pumpe P1 reicht, den gewünschten Höchstdruck bis zu 800 bar zu erreichen. Erst dann spricht das Höchstdruckbegrenzungsventil 13 an. Der erforderliche Höchstdruck für den Verbraucher V liegt zweckmäßigerweise bei etwa 700 bar, so dass das Höchstdruckbegrenzungsventil 13 nur anspricht, falls die Gefahr eines Schadens auftreten sollte.If the pressure source unit Q is turned on, the pumps P1, P3 deliver different flow rates, the summed act on the main line P and, since the
Bis zum Erreichen des vorbestimmten Druckwertes, an dem das Abschaltventil 7 anspricht, kann der Verbraucher V dank der großen Gesamtfördermenge beispielsweise in einem Eilgang bewegt werden. Danach erfolgt der Druckaufbau bis zum erforderlichen Höchstdruck nur mit der niedrigeren Fördermenge der Pumpe P1.Until reaching the predetermined pressure value at which the shut-off valve 7 responds, the load V can be moved thanks to the large total delivery, for example, in rapid traverse. Thereafter, the pressure is built up to the required maximum pressure only with the lower flow rate of the pump P1.
Sobald das Druckquellenaggregat Q (der Antriebsmotor M) abgeschaltet wird, sperrt das weitere Rückschlagventil 24 und entfällt die Druckdifferenz über die Drossel 23, so dass die Druckweiche 16 durch die Feder 19 wieder in die gezeigte Durchgangsstellung geschaltet wird. Die Druckleitungen 2, 3 und die Hauptleitung P werden wieder über die Entlastungsleitung 15 zum Tank R bzw. der Tankleitung 6 entlastete.As soon as the pressure source unit Q (the drive motor M) is switched off, the
Gemäß
Claims (9)
- Hydraulic control device (H), including at least one consumer (V), at least two pumps (P1, P3), separate pressure lines (2, 3), a node (1), a control valve assembly (25), a main line (P), a check valve (40), a relief line (5), and a switch-off valve (7), wherein the consumer (V) can be actuated out of a pressure aggregate comprising the at least two pumps (P1, P3) having different discharge quantities, which pumps can be switched on and switched off commonly, and which are connected via the separate pressure lines (2, 3) with the node (1) of the main line (P) which extends to the control valve assembly (25) of the consumer (V), wherein in the pressure line (3) of the pump (P3) having the larger discharge quantity the check valve (40) is arranged which blocks in flow direction to the pump (P3), and wherein the relief line (5) branches off from this pressure line (3) to a tank (R), in which relief line (5) the switch-off valve (7) is contained which can be actuated by a pilot pressure from the main line (P) in order to divert the larger discharge quantity to the tank (R) when a predetermined pressure value is reached in the main line (P), characterised in that a pressure gate (16) is arranged in an unloading line (15) extending from the main line (P) towards the tank (R), which pressure gate can be switched between a through flow position (18) and a leakage-free sealed blocking position (17) and can be actuated in switching direction to the through flow position at least by a control pressure derived from the main line (P) and in switching direction to the blocking position by a control pressure exclusively generated by the pump (P1) having the smaller discharge quantity, the pressure gate maintaining the through flow position when the pumps (P1, P3) are switched off, that the control pressure for actuating the pressure gate (16) in switching direction to the blocking position is derived from a pressure difference generated at an aperture (23) arranged upstream of the node (1) in the pressure line (2) of the pump (P1) having the smaller discharge quantity, and that the cross-section of the aperture (23) is adapted to the smaller discharge quantity such that the pressure gate (16) is switched into the blocking position (17) with a timewise delay after the pumps (P1, P3) are switched on.
- Hydraulic control device according to claim 1, characterised in that the pressure gate (16) is a 2/2 multi-way seat valve having a valve cone (32) actuated by a spring (19) in switching direction to the through flow position and a valve seat (35) arranged in the unloading line (15).
- Hydraulic control device according to claim 2, characterised in that the valve cone (32) comprises pressure receiving surfaces (A1, A2) with different sizes for the control pressures, wherein the pressure receiving surface (A2) for the control pressure actuating the pressure gate in switching direction to the through flow position is smaller than the pressure receiving surface (A1) for the control pressure actuating the pressure gate in switching direction to the blocking position, preferably, with a ratio of the pressure receiving surfaces (A1, A2) between about 2:1 and 4:1, preferably about 3:1.
- Hydraulic control device according to claim 2, characterised in that that the valve cone (32) has actuating pressure receiving surfaces of at least substantially equal sizes for both control pressures.
- Hydraulic control device according to claim 1, characterised in that the cross-section of the aperture (23) is fixed, and that the aperture (23) is exchangeably arranged in the pressure line (2).
- Hydraulic control device according to claim 1, characterised in that the cross-section of the aperture (23) is adjustable.
- Hydraulic control device according to at least one of the preceding claims, characterised in that the cross-section of the aperture (23), the force of the spring (19) and the pressure receiving surfaces (A1, A2) at the valve cone (32) are adapted to each other such that when the common drive motor (M) of the pumps (P1, P3) is switched on while the main line (P) is relieved to the tank (R) via the pressure gate (16) switched to the through flow position, which drive motor (M), preferably, is a single phase-alternating current motor, the timewise delay until the pressure gate switches to the blocking position facilitating the start of the driving motor is generated via the aperture (23) from a pressure difference which amounts to about 5 bars to 10 bars.
- Hydraulic control device according to claim 1, characterised in that a further check valve (24) is arranged between the main line (P) and the control valve assembly (25) of the hydro-consumer (V), the further check valve (24) blocking in flow direction to the unloading line (16).
- Hydraulic control device according to at least one of the preceding claims, characterised in that the hydraulic control device is assembled from several interconnected block sections (I, II, III), among which a first block section (I) has connections for the pumps (P1, P3) and the tank (R) as well as the switching off valve (7), a maximum pressure limiting valve (13), the check valve (40) and the aperture (23), a second block section (II) has the pressure gate (16), and a third blocking section (III) has the further check valve (29) and the control valve assembly (25) for the hydro-consumer (V).
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20090015873 EP2339185B1 (en) | 2009-12-22 | 2009-12-22 | Hydraulic device |
ES09015873T ES2401560T3 (en) | 2009-12-22 | 2009-12-22 | Hydraulic control |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20090015873 EP2339185B1 (en) | 2009-12-22 | 2009-12-22 | Hydraulic device |
Publications (2)
Publication Number | Publication Date |
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EP2339185A1 EP2339185A1 (en) | 2011-06-29 |
EP2339185B1 true EP2339185B1 (en) | 2013-02-13 |
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ID=42167288
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP20090015873 Not-in-force EP2339185B1 (en) | 2009-12-22 | 2009-12-22 | Hydraulic device |
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EP (1) | EP2339185B1 (en) |
ES (1) | ES2401560T3 (en) |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4112821A (en) | 1976-12-03 | 1978-09-12 | Caterpillar Tractor Co. | Fluid control system for multiple circuited work elements |
KR870000506B1 (en) | 1981-05-02 | 1987-03-12 | 니시모도 후미히라(西元文平) | Hydraulic circuit system for civil engineering and architectural machinery |
US5446979A (en) | 1992-04-20 | 1995-09-05 | Hitachi Construction Machinery Co., Ltd. | Hydraulic circuit system for civil engineering and construction machines |
-
2009
- 2009-12-22 EP EP20090015873 patent/EP2339185B1/en not_active Not-in-force
- 2009-12-22 ES ES09015873T patent/ES2401560T3/en active Active
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EP2339185A1 (en) | 2011-06-29 |
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