EP3078855B1 - Hydraulic assembly - Google Patents

Hydraulic assembly Download PDF

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Publication number
EP3078855B1
EP3078855B1 EP16164273.1A EP16164273A EP3078855B1 EP 3078855 B1 EP3078855 B1 EP 3078855B1 EP 16164273 A EP16164273 A EP 16164273A EP 3078855 B1 EP3078855 B1 EP 3078855B1
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EP
European Patent Office
Prior art keywords
pressure
high pressure
pressure pump
coupling
pump
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EP16164273.1A
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German (de)
French (fr)
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EP3078855A3 (en
EP3078855A2 (en
Inventor
Neels Schüder
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REINTJES GmbH
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REINTJES GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a hydraulic unit according to the preamble of claim 1.
  • a hydraulic unit is out of the DE 10 2010 023 713 A1 and the one based on the same priority document US 2011/000 5214 A1 and is used to provide hydraulic fluid at at least two different pressure levels. It is known to releasably rigidly couple the high pressure pump and the low pressure pump so that the drive drives both pumps. The disadvantage of this is that the pump requires a comparatively large coupling.
  • a system for avoiding idling in which a cylinder engine is automatically deactivated and put into operation.
  • a second oil pump is switched on via an electrically switchable clutch after a restart of the cylinder engine to supply a starting clutch with oil pressure. After starting, the second oil pump is switched off again. In this way, an electric motor saved in prior systems for driving the second oil pump during a standstill of the cylinder engine is saved.
  • the invention solves the problem by a hydraulic unit having the features of claim 1.
  • the clutch is designed so that its switching state can be changed by supplying hydraulic fluid that is at the pressure level generated by the low-pressure pump. It is possible that the actuation by means of the hydraulic fluid, which is under low pressure, further opens the clutch or that it is closed further.
  • the clutch according to the invention is designed so that it couples with application of low pressure with slip and transmits a driving torque to the high-pressure pump, so that the high-pressure pump emits hydraulic fluid at a high pressure, which is greater than the low pressure.
  • the clutch is slipping, it is understood that the high pressure pump does not rotate at the speed it rotates when the clutch is fully engaged. It is possible, but not necessary, that when the clutch is engaged with slip, a lower torque is transmitted than when fully engaged.
  • the high pressure pump delivers hydraulic fluid at a high pressure that is greater than the low pressure, pressurized fluid is available at a higher pressure level. If the high pressure that the high pressure pump gives off when the clutch is coupled with slip is less than the maximum high pressure, then by fully engaging the clutch, it is possible to increase the high pressure to the maximum possible high pressure, so with the hydraulic power pack several pressure levels can be generated.
  • Another advantage of the invention is that only one switching device, such as a valve, is necessary for actuating the clutch.
  • the hydraulic pump according to the invention is therefore simple and therefore robust.
  • the low-pressure pump is understood to mean, in particular, a pump which, due to the design, can bring hydraulic fluid to a maximum low pressure which is significantly lower than the pressure which can be maximally generated by the high-pressure pump.
  • the ratio between the maximum high pressure and the maximum low pressure is greater than four.
  • the low-pressure pump always produces the same low pressure.
  • the low pressure can fluctuate. Decisive is that the low pressure does not exceed a given maximum low pressure.
  • the high pressure pump it is possible, but not necessary, for the high pressure pump to always deliver the same high pressure.
  • the high-pressure pump at least temporarily emits a pressure which is even smaller than the low pressure.
  • the high-pressure pump is designed so that it can deliver a maximum high pressure, which is significantly greater than the maximum low pressure.
  • high pressure is understood in particular the pressure under which the hydraulic fluid is when it was pressurized by the high-pressure pump.
  • low pressure is meant the pressure of the hydraulic fluid under which the hydraulic fluid is under pressure from the low pressure pump.
  • the pressure side of the high pressure pump may be connected to the clutch via a pressure line.
  • the clutch If hydraulic fluid is passed to the clutch at low pressure, it will slip.
  • the high-pressure pump is then driven, supplying hydraulic fluid at a higher pressure, thus actuating the clutch in the same direction as the low-pressure hydraulic fluid.
  • the clutch is closed further, that is to say that the slip continues to drop and the clutch finally couples without slip. Since the high-pressure pump delivers hydraulic fluid under high pressure, the clutch can be made comparatively small because a high clutch pressure is applied.
  • the coupling is connected by means of a pressure line to the high-pressure pump, wherein the pressure line is designed so that a sudden pressure increase at a pressure side of the high-pressure pump, which is a differential pressure .DELTA.p greater than the clutch pressure in the clutch, after a half-life leads to a clutch pressure which is greater by half of the differential pressure ⁇ p, wherein the half-life is at least 200 milliseconds, in particular at least 500 milliseconds, more preferably at least 1000 milliseconds.
  • a cross section of the pressure line is chosen so small that the requirement is met. The smaller the cross section, the larger the half life. As a result, a sudden increase in the clutch pressure and the high pressure is avoided.
  • the pressure line has a flow-influencing device, in particular a throttle, a valve and / or a pressure reducer.
  • a flow-influencing device in particular a throttle, a valve and / or a pressure reducer.
  • High-pressure fluid flows through the pressure line in the clutch. The faster the pressure builds up in the clutch, the faster the clutch closes.
  • This is a positive feedback.
  • the flow rate influencing device By the flow rate influencing device, the strength of this positive feedback can be influenced. It is thus possible to influence a pressure curve in the pressure oil circuit. It is favorable if the flow-influencing device is adjustable in its throttling action.
  • the pressure curve is the dependence of high pressure on time.
  • the coupling is connected by means of a switching line with the low-pressure pump, wherein the switching line comprises a solenoid valve, in particular a proportional valve.
  • the solenoid valve By means of the solenoid valve, the clutch can be set to low pressure, so that the drive torque is partially transmitted to the high-pressure pump.
  • the low-pressure pump is part of a lubricating oil circuit.
  • Lubricating oil must be permanently provided at a relatively low pressure level.
  • the low-pressure pump is therefore particularly suitable as a lubricating oil pump.
  • a marine gear Under a marine gear is understood a transmission that is designed for installation in a ship. For this purpose, it must preferably be constructed so that it can switch to maximum reverse drive at maximum forward speed. In particular, the marine gear is therefore a reversing gear. It is favorable if the marine gear for transmitting has a power of at least 250 kilowatts.
  • the high-pressure pump is part of a pressure oil circuit.
  • the pressure oil circuit comprises a hydraulic actuator, such as a clutch.
  • hydraulic actuators are used only sporadically, so that it is not necessary that permanently hydraulic fluid is present at high pressure.
  • FIG. 1 shows a hydraulic unit 10 according to the invention with a low-pressure pump 12, a high-pressure pump 14 and a drive 16, which is formed in the present case by an electric motor.
  • the drive 16 for example, but also be an internal combustion engine, such as a main or auxiliary diesel of a ship.
  • the drive 16 is non-rotatably coupled to the low-pressure pump 12, in the present case by means of a shaft 18th
  • the low-pressure pump 12 discharges hydraulic fluid 20 into a switching line 22, which is at a low pressure p 12 .
  • the pressurized hydraulic fluid 20 could therefore also be referred to as low-pressure hydraulic fluid.
  • the hydraulic fluid is, for example, oil, in particular lubricating oil.
  • the high pressure pump 14 is connected via a double check valve 24 to the switching line 22.
  • the switching line 22 also includes a solenoid valve 26, with which the pressure p in the switching line 22 can be switched through to a coupling 28.
  • the solenoid valve 26 may be a proportional valve, but it is not necessary.
  • FIG. 1 shows the solenoid valve 26 in its zero pressure position, in which the coupling 28 is connected via a return line 30 to a sump 32.
  • ambient pressure may prevail in the sump 32.
  • the clutch 28 Since the clutch 28 is pressure-free, it is in the present embodiment in the open state. For example, to clutch plates 34.1, 34.2, ... held by a spring 36 at a distance. If the clutch 28 is acted upon by hydraulic fluid 20, the hydraulic fluid 20 presses on a piston 37, which in turn compresses the clutch discs 34.1, 34.2,... And thus at least partially closes the clutch 37.
  • the switching line 22 is connected to a lubricating oil receiver 38.
  • the hydraulic unit 10 supplies the lubricating oil receiver 38 with lubricating oil, but it is only provided hydraulic fluid to low pressure p 12 .
  • the lubricating oil receiver 38 is part of a lubricating oil circuit 39, which also includes the connecting lines.
  • FIG. 2 shows the solenoid valve 26 in its switching position in which the switching line 22, the clutch 28 with low pressure p 12 supplies.
  • a p 12 in the clutch 28 thus increases to the p 12 .
  • the low pressure p 12 is so strong that the clutch 28 couples with slippage. That is, a rotational frequency of a drive side of the clutch and thus usually a rotational frequency n 16 of the drive 16 is greater than a rotational frequency n 28 of the clutch 28 on its output side.
  • pressure line 40 The connection between the high-pressure pump 14 and the clutch 28 is referred to as pressure line 40. It should be noted that the pressure line 40 may be partially identical to the switching line 22 and in the embodiment shown also.
  • the pressure line 40 is in communication with a pressure oil receiver 42, such as a clutch or other hydraulic actuator, which is part of a pressure oil circuit 43.
  • FIG. 3 shows the state in which both pumps 12, 14 convey fluid. It can be seen that both pumps 12, 14 are supplied by a common supply line 44 from the sump 32 with hydraulic fluid. Hydraulic fluid returning from the lubricating oil receiver 38 and pressurized oil receiver 42 flows into the sump 32.
  • FIG. 4 shows the pressure curve of the clutch pressure p 28, SdT (t) in the clutch 28 in a hydraulic unit according to the prior art. It can be spotted, that the clutch pressure p SdT (t) abruptly increases and decreases, which is often undesirable. Also marked is a calculated pressure curve p 14 (t) for a hydraulic unit according to the invention. After a switching point t s , the pressure p 14 increases comparatively slowly. At a time t 1 , the high pressure pump 14 begins to promote. Due to the feedback effect, the drive torque M 28 increases as well as the result of the high pressure p 14 and thus the clutch pressure p 28th
  • the speed of the pressure increase of the clutch pressure p 28 can be reduced by providing a flow rate influencing device 45 (see FIG. 2) in the pressure line 40 between the pressure side of the high-pressure pump 14 and the clutch 28, as provided in a preferred embodiment.
  • FIG. 1 is arranged.
  • a cross-section of at least part of the pressure line 40 may be selected such that the pressure line has the effect of the flow-influencing device 45. So can the in FIG. 4 shown clutch pressure curve p 28 (t) can be achieved.
  • the clutch 28 fully couples, that is, without slippage, and the high pressure p 14 reaches its maximum value p 14, max . This corresponds to the maximum pressure that the high-pressure pump 14 supplies.
  • a flow-influencing device 45 for example a throttle
  • the pressure rise in the clutch 28 can be delayed.
  • the strength of the positive feedback and thus the time between the switching point and the time when the full high pressure is applied can be set.
  • FIGS. 1 to 3 show a further embodiment in which the coupling 28 comprises a linkage 46, by means of which the force is transmitted from a pressurized cylinder 48 to the clutch plates 34.
  • the functioning does not differ from that for the FIGS. 1 to 3 has been described.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Transmission Device (AREA)
  • Gear-Shifting Mechanisms (AREA)

Description

Die Erfindung betrifft ein Hydraulikaggregat gemäß dem Oberbegriff von Anspruch 1.The invention relates to a hydraulic unit according to the preamble of claim 1.

Ein Hydraulikaggregat ist aus der DE 10 2010 023 713 A1 und der auf das gleiche Prioritätsdokument zurückgehenden US 2011/000 5214 A1 bekannt und wird dazu verwendet, Hydraulikflüssigkeit auf zumindest zwei verschiedenen Druckniveaus bereit zu stellen. Es ist bekannt, die Hochdruck-Pumpe und die Niederdruck-Pumpe lösbar starr zu koppeln, sodass der Antrieb beide Pumpen antreibt. Nachteilig hieran ist, dass die Pumpe eine vergleichsweise große Kupplung benötigt.A hydraulic unit is out of the DE 10 2010 023 713 A1 and the one based on the same priority document US 2011/000 5214 A1 and is used to provide hydraulic fluid at at least two different pressure levels. It is known to releasably rigidly couple the high pressure pump and the low pressure pump so that the drive drives both pumps. The disadvantage of this is that the pump requires a comparatively large coupling.

Aus der JP 2010 174927 A ist ein System zum Vermeiden von Leerlauf bekannt, bei dem ein Zylindermotor automatisch außer und in Betrieb gesetzt wird. Es existieren zwei Ölpumpen, von denen eine fest mit dem Zylindermotor gekoppelt ist. Eine zweite Ölpumpe wird über eine elektrisch schaltbare Kupplung nach einem Wiederstarten des Zylindermotors zugeschaltet, um eine Startkupplung mit Öldruck zu versorgen. Nach dem Startvorgang wird die zweite Ölpumpe wieder abgeschaltet. Auf diese Weise wird ein Elektromotor eingespart, der in vorherigen Systemen zum Antreiben der zweiten Ölpumpe während eines Stillstands des Zylindermotors verwendet wurde.From the JP 2010 174927 A For example, a system for avoiding idling is known in which a cylinder engine is automatically deactivated and put into operation. There are two oil pumps, one of which is fixedly coupled to the cylinder engine. A second oil pump is switched on via an electrically switchable clutch after a restart of the cylinder engine to supply a starting clutch with oil pressure. After starting, the second oil pump is switched off again. In this way, an electric motor saved in prior systems for driving the second oil pump during a standstill of the cylinder engine is saved.

Aus der US 2014/0060681 A1 ist System zur Versorgung mit Hydrauliköl bekannt, bei dem zwei oder mehr Ölpumpen kaskadiert hintereinander geschaltet sind, sodass eine nachgeschaltete Ölpumpe bereits mit Öldruck beaufschlagt wird. Der Öldruck der ersten Ölpumpe wird verwendet, um eine Kupplung zu betätigen, die die zweite Ölpumpe mit ihrem Antriebsmotor verbindet.
Der Erfindung liegt die Aufgabe zu Grunde, das Hydraulikaggregat so auszugestalten, dass eine kleine Kupplung verwendbar ist.From the US 2014/0060681 A1 is known system for supplying hydraulic oil, in which two or more oil pumps are cascaded in series, so that a downstream oil pump is already subjected to oil pressure. The oil pressure of the first oil pump is used to actuate a clutch that connects the second oil pump to its drive motor.
The invention is based on the object, the hydraulic unit in such a way that a small coupling is used.

Die Erfindung löst das Problem durch ein Hydraulikaggregat mit den Merkmalen von Anspruch 1.The invention solves the problem by a hydraulic unit having the features of claim 1.

In anderen Worten ist die Kupplung so ausgebildet, dass ihr Schaltzustand durch Zuführen von Hydraulikflüssigkeit, die auf dem von der Niederdruck-Pumpe erzeugten Druckniveau ist, geändert werden kann. Es ist möglich, dass das Betätigen mittels des Hydraulikfluids, das unter Niederdruck steht, die Kupplung weiter geöffnet oder dass sie weiter geschlossen wird.In other words, the clutch is designed so that its switching state can be changed by supplying hydraulic fluid that is at the pressure level generated by the low-pressure pump. It is possible that the actuation by means of the hydraulic fluid, which is under low pressure, further opens the clutch or that it is closed further.

Die Kupplung ist erfindungsgemäß so ausgebildet, dass sie bei Beaufschlagen mit Niederdruck mit Schlupf kuppelt und ein Antriebs-Drehmoment auf die Hochdruck-Pumpe überträgt, sodass die Hochdruck-Pumpe Hydraulikflüssigkeit mit einem Hochdruck abgibt, der größer ist als der Niederdruck. Darunter, dass die Kupplung mit Schlupf kuppelt, wird verstanden, dass die Hochdruckpumpe nicht mit der Drehzahl dreht, mit der sie dreht, wenn die Kupplung vollständig eingekuppelt ist. Es ist möglich, nicht aber notwendig, dass dann, wenn die Kupplung mit Schlupf eingekuppelt ist, ein geringeres Drehmoment übertragen wird als im voll eingekuppelten Zustand.The clutch according to the invention is designed so that it couples with application of low pressure with slip and transmits a driving torque to the high-pressure pump, so that the high-pressure pump emits hydraulic fluid at a high pressure, which is greater than the low pressure. By assuming that the clutch is slipping, it is understood that the high pressure pump does not rotate at the speed it rotates when the clutch is fully engaged. It is possible, but not necessary, that when the clutch is engaged with slip, a lower torque is transmitted than when fully engaged.

Dadurch, dass die Hochdruck-Pumpe Hydraulikflüssigkeit mit einem Hochdruck abgibt, der größer ist als der Niederdruck, steht Druckfluid auf einem höheren Druckniveau zur Verfügung. Wenn der Hochdruck, den die Hochdruck-Pumpe abgibt, wenn die Kupplung mit Schlupf gekuppelt ist, kleiner ist als der maximale Hochdruck, ist es dann durch vollständiges Einkuppeln der Kupplung möglich, den Hochdruck auf den maximal möglichen Hochdruck zu steigern, sodass mit dem Hydraulikaggregat mehrere Druckniveaus erzeugbar sind.Because the high pressure pump delivers hydraulic fluid at a high pressure that is greater than the low pressure, pressurized fluid is available at a higher pressure level. If the high pressure that the high pressure pump gives off when the clutch is coupled with slip is less than the maximum high pressure, then by fully engaging the clutch, it is possible to increase the high pressure to the maximum possible high pressure, so with the hydraulic power pack several pressure levels can be generated.

Vorteilhaft an der Erfindung ist zudem, dass zum Betätigen der Kupplung lediglich eine Schaltvorrichtung, beispielsweise ein Ventil, notwendig ist. Die erfindungsgemäße Hydraulikpumpe ist daher einfach und damit robust aufgebaut.Another advantage of the invention is that only one switching device, such as a valve, is necessary for actuating the clutch. The hydraulic pump according to the invention is therefore simple and therefore robust.

Vorteilhaft ist zudem die Verbesserung des System-Wirkungsgrads, da die Hochdruck-Pumpe nur dann läuft, wenn Hochdruckfluid benötigt wird.It is also advantageous to improve the system efficiency, since the high pressure pump only runs when high pressure fluid is needed.

Es ist ein weiterer Vorteil, dass die Hochdruck-Pumpe dann einfach aus dem Drehmomentfluss geschaltet werden kann, wenn sie nicht benötigt wird. Dadurch werden Reibungsverluste vermieden und der Wirkungsgrad gesteigert.It is a further advantage that the high pressure pump can then be simply switched out of the torque flow when it is not needed. This prevents friction losses and increases efficiency.

Im Rahmen der vorliegenden Beschreibung wird unter der Niederdruck-Pumpe insbesondere eine Pumpe verstanden, die bauartbedingt Hydraulikflüssigkeit auf einen maximalen Niederdruck bringen kann, der deutlich kleiner ist als der Druck, der von der Hochdruck-Pumpe maximal erzeugbar ist. Insbesondere ist das Verhältnis zwischen dem maximalen Hochdruck und dem maximalen Niederdruck größer als vier. Selbstverständlich ist es möglich, nicht aber notwendig, dass die Niederdruck-Pumpe stets den gleichen Niederdruck erzeugt. Beispielsweise kann der Niederdruck schwanken. Maßgeblich ist, dass der Niederdruck einen vorgegebenen maximalen Niederdruck nicht überschreitet.In the context of the present description, the low-pressure pump is understood to mean, in particular, a pump which, due to the design, can bring hydraulic fluid to a maximum low pressure which is significantly lower than the pressure which can be maximally generated by the high-pressure pump. In particular, the ratio between the maximum high pressure and the maximum low pressure is greater than four. Of course, it is possible, but not necessary, that the low-pressure pump always produces the same low pressure. For example, the low pressure can fluctuate. Decisive is that the low pressure does not exceed a given maximum low pressure.

Es ist möglich, nicht aber notwendig, dass die Hochdruck-Pumpe stets den gleichen Hochdruck abgibt. Insbesondere ist es denkbar, dass die Hochdruckpumpe zumindest zeitweise einen Druck abgibt, der sogar kleiner ist als der Niederdruck. Maßgeblich ist jedoch, dass die Hochdruck-Pumpe so ausgebildet ist, dass sie einen maximalen Hochdruck abgeben kann, der deutlich größer ist als der maximale Niederdruck.It is possible, but not necessary, for the high pressure pump to always deliver the same high pressure. In particular, it is conceivable that the high-pressure pump at least temporarily emits a pressure which is even smaller than the low pressure. What matters, however, is that the high-pressure pump is designed so that it can deliver a maximum high pressure, which is significantly greater than the maximum low pressure.

Unter dem Hochdruck wird insbesondere der Druck verstanden, unter dem das Hydraulikfluid steht, wenn es von der Hochdruck-Pumpe unter Druck gesetzt wurde. Unter dem Niederdruck wird derjenige Druck der Hydraulikflüssigkeit verstanden, unter dem die Hydraulikflüssigkeit steht, wenn sie von der Niederdruck-Pumpe unter Druck gesetzt wurde.Under the high pressure is understood in particular the pressure under which the hydraulic fluid is when it was pressurized by the high-pressure pump. By low pressure is meant the pressure of the hydraulic fluid under which the hydraulic fluid is under pressure from the low pressure pump.

Um die Kupplung mit der Hochdruckpumpe so zu verbinden, dass eine Erhöhung des von der Kupplung auf die Hochdruck-Pumpe übertragenen Drehmoments eine Erhöhung des Hochdrucks bewirkt, wobei die Erhöhung des Hochdrucks eine Erhöhung des Antriebs-Drehmoments auf die Hochdruck-Pumpe bewirkt, kann die Druckseite der Hochdruck-Pumpe mit der Kupplung über eine Druckleitung verbunden sein.To connect the clutch with the high pressure pump so that an increase in the torque transmitted by the clutch to the high pressure pump Increasing the high pressure causes, wherein the increase of the high pressure causes an increase of the drive torque to the high pressure pump, the pressure side of the high pressure pump may be connected to the clutch via a pressure line.

Wird Hydraulikfluid mit Niederdruck zur Kupplung geleitet, so kuppelt diese mit Schlupf. Daraufhin wird die Hochdruck-Pumpe angetrieben, liefert Hydraulikflüssigkeit mit einem höheren Druck und betätigt so die Kupplung in die gleiche Richtung wie das Hydraulikfluid mit Niederdruck. Dadurch wird gemäß einer Ausführungsform die Kupplung weiter geschlossen, das heißt, dass der Schlupf weiter sinkt und die Kupplung schließlich schlupffrei kuppelt. Da die Hochdruck-Pumpe unter einem hohen Druck stehendes Hydraulikfluid fördert, kann die Kupplung vergleichsweise klein ausgeführt werden, da ein hoher Kupplungsdruck aufgebracht wird.If hydraulic fluid is passed to the clutch at low pressure, it will slip. The high-pressure pump is then driven, supplying hydraulic fluid at a higher pressure, thus actuating the clutch in the same direction as the low-pressure hydraulic fluid. As a result, according to one embodiment, the clutch is closed further, that is to say that the slip continues to drop and the clutch finally couples without slip. Since the high-pressure pump delivers hydraulic fluid under high pressure, the clutch can be made comparatively small because a high clutch pressure is applied.

Alternativ bewirkt die Erhöhung des Hochdrucks eine Verminderung des Antriebs-Drehmoments auf die Hochdruck-Pumpe.Alternatively, increasing the high pressure causes the drive torque to be reduced to the high pressure pump.

Gemäß einer bevorzugten Ausführungsform ist die Kupplung mittels einer Druckleitung mit der Hochdruck-Pumpe verbunden, wobei die Druckleitung so ausgebildet ist, dass ein schlagartiger Druckanstieg an einer Druckseite der Hochdruck-Pumpe, der einen Differenzdruck Δp größer ist als der Kupplungsdruck in der Kupplung, nach einer Halbwertszeit zu einem Kupplungsdruck führt, der um die Hälfte des Differenzdrucks Δp größer ist, wobei die Halbwertszeit zumindest 200 Millisekunden, insbesondere zumindest 500 Millisekunden, besonders bevorzugt zumindest 1000 Millisekunden beträgt. Beispielsweise wird dazu ein Querschnitt der Druckleitung so klein gewählt, dass die Forderung erfüllt ist. Je kleiner der Querschnitt ist, desto größer ist die Halbwertszeit. Dadurch wird ein schlagartiger Anstieg des Kupplungsdrucks und des Hochdrucks vermieden.According to a preferred embodiment, the coupling is connected by means of a pressure line to the high-pressure pump, wherein the pressure line is designed so that a sudden pressure increase at a pressure side of the high-pressure pump, which is a differential pressure .DELTA.p greater than the clutch pressure in the clutch, after a half-life leads to a clutch pressure which is greater by half of the differential pressure Δp, wherein the half-life is at least 200 milliseconds, in particular at least 500 milliseconds, more preferably at least 1000 milliseconds. For example, a cross section of the pressure line is chosen so small that the requirement is met. The smaller the cross section, the larger the half life. As a result, a sudden increase in the clutch pressure and the high pressure is avoided.

Gemäß einer bevorzugten Ausführungsform weist die Druckleitung eine Durchflussbeeinflussungsvorrichtung auf, insbesondere eine Drossel, ein Ventil und/oder einen Druckminderer. Durch die Druckleitung fließt unter Hochdruck stehendes Fluid in die Kupplung. Je schneller sich der Druck in der Kupplung aufbaut, desto schneller schließt die Kupplung. Es handelt sich damit um eine positive Rückkupplung. Durch die Durchflussbeeinflussungsvorrichtung kann die Stärke dieser positiven Rückkupplung beeinflusst werden. Es ist damit möglich, einen Druckverlauf im Druckölkreislauf zu beeinflussen. Günstig ist es, wenn die Durchflussbeeinflussungsvorrichtung in ihrer Drosselwirkung einstellbar ist.According to a preferred embodiment, the pressure line has a flow-influencing device, in particular a throttle, a valve and / or a pressure reducer. High-pressure fluid flows through the pressure line in the clutch. The faster the pressure builds up in the clutch, the faster the clutch closes. This is a positive feedback. By the flow rate influencing device, the strength of this positive feedback can be influenced. It is thus possible to influence a pressure curve in the pressure oil circuit. It is favorable if the flow-influencing device is adjustable in its throttling action.

Der Druckverlauf ist die Abhängigkeit des Hochdrucks von der Zeit. Insbesondere kann es vorteilhaft sein, dass der Hochdruck nicht zu schnell auf seinen maximalen Wert ansteigt. In diesem Fall ist es günstig, wenn beispielsweise eine Drossel in der Druckleitung vorhanden ist. Diese verhindert einen zu schnellen Anstieg des Drucks in der Kupplung und damit einen zu schnellen Anstieg des Hochdrucks auf seinen maximalen Wert.The pressure curve is the dependence of high pressure on time. In particular, it may be advantageous that the high pressure does not rise too fast to its maximum value. In this case, it is favorable if, for example, a throttle is present in the pressure line. This prevents a too rapid increase in the pressure in the clutch and thus a too rapid increase in the high pressure to its maximum value.

Vorzugsweise ist die Kupplung mittels einer Schaltleitung mit der Niederdruck-Pumpe verbunden, wobei die Schaltleitung ein Magnetventil, insbesondere ein Proportionalventil, aufweist. Mittels des Magnetventils kann die Kupplung auf Niederdruck gelegt werden, sodass das Antriebs-Drehmoment teilweise auf die Hochdruck-Pumpe übertragen wird.Preferably, the coupling is connected by means of a switching line with the low-pressure pump, wherein the switching line comprises a solenoid valve, in particular a proportional valve. By means of the solenoid valve, the clutch can be set to low pressure, so that the drive torque is partially transmitted to the high-pressure pump.

Erfindungsgemäß ist zudem ein Schiffsgetriebe mit einem erfindungsgemäßen Hydraulikaggregat, wobei die Niederdruck-Pumpe Teil eines Schmierölkreislaufs ist. Schmieröl muss dauerhaft auf einem relativ geringen Druckniveau zur Verfügung gestellt werden. Die Niederdruck-Pumpe eignet sich daher besonders gut als Schmierölpumpe.According to the invention is also a marine gearbox with a hydraulic unit according to the invention, wherein the low-pressure pump is part of a lubricating oil circuit. Lubricating oil must be permanently provided at a relatively low pressure level. The low-pressure pump is therefore particularly suitable as a lubricating oil pump.

Unter einem Schiffsgetriebe wird ein Getriebe verstanden, dass zum Einbau in ein Schiff ausgebildet ist. Dazu muss es vorzugsweise so aufgebaut sein, dass es bei maximaler Vorwärtsfahrt auf maximale Rückwärtsfahrt umschalten kann. Insbesondere ist das Schiffsgetriebe daher ein Wendegetriebe. Günstig ist es, wenn das Schiffsgetriebe zum Übertragen eine Leistung von zumindest 250 Kilowatt besitzt.Under a marine gear is understood a transmission that is designed for installation in a ship. For this purpose, it must preferably be constructed so that it can switch to maximum reverse drive at maximum forward speed. In particular, the marine gear is therefore a reversing gear. It is favorable if the marine gear for transmitting has a power of at least 250 kilowatts.

Vorzugsweise ist die Hochdruckpumpe Teil eines Druckölkreislaufs. Beispielsweise umfasst der Druckölkreislauf einen hydraulischen Aktor, beispielsweise eine Kupplung. Derartige hydraulische Aktoren werden lediglich sporadisch verwendet, sodass es nicht notwendig ist, dass dauerhaft Hydraulikfluid mit Hochdruck vorhanden ist.Preferably, the high-pressure pump is part of a pressure oil circuit. For example, the pressure oil circuit comprises a hydraulic actuator, such as a clutch. Such hydraulic actuators are used only sporadically, so that it is not necessary that permanently hydraulic fluid is present at high pressure.

Im Folgenden wird die Erfindung anhand der beigefügten Zeichnungen näher erläutert. Dabei zeigt:

Figur 1
ein Schema einer erfindungsgemäßen Hydraulikpumpe, bei dem die Kupplung geöffnet ist,
Figur 2
das Hydraulikaggregat gemäß Figur 1, bei dem die Kupplung mit Schlupf kuppelt und
Figur 3
das Hydraulikaggregat mit geschlossener Kupplung,
Figur 4
einen Druckverlauf des Hochdrucks und
Figur 5
mit den Teilfiguren 5a, 5b und 5c ein erfindungsgemäßes Hydraulikaggregat, das ein Gestänge zum Schalten der Kupplung aufweist.
In the following the invention will be explained in more detail with reference to the accompanying drawings. Showing:
FIG. 1
a diagram of a hydraulic pump according to the invention, in which the clutch is open,
FIG. 2
the hydraulic unit according to FIG. 1 in which the clutch with slip couples and
FIG. 3
the hydraulic unit with closed clutch,
FIG. 4
a pressure curve of the high pressure and
FIG. 5
with the sub-figures 5a, 5b and 5c, an inventive hydraulic unit having a linkage for switching the clutch.

Figur 1 zeigt ein erfindungsgemäßes Hydraulikaggregat 10 mit einer Niederdruck-Pumpe 12, einer Hochdruck-Pumpe 14 und einem Antrieb 16, der im vorliegenden Fall durch ein Elektromotor gebildet ist. Der Antrieb 16 kann beispielsweise aber auch ein Verbrennungsmotor sein, beispielsweise ein Haupt- oder Hilfsdiesel eines Schiffes. Der Antrieb 16 ist drehfest mit der Niederdruck-Pumpe 12 gekoppelt, im vorliegenden Fall mittels einer Welle 18. FIG. 1 shows a hydraulic unit 10 according to the invention with a low-pressure pump 12, a high-pressure pump 14 and a drive 16, which is formed in the present case by an electric motor. The drive 16, for example, but also be an internal combustion engine, such as a main or auxiliary diesel of a ship. The drive 16 is non-rotatably coupled to the low-pressure pump 12, in the present case by means of a shaft 18th

Die Niederdruck-Pumpe 12 gibt Hydraulikflüssigkeit 20 in eine Schaltleitung 22 ab, welche unter einem Niederdruck p12 steht. Die so unter Druck stehende Hydraulikflüssigkeit 20 könnte daher auch als Niederdruck-Hydraulikflüssigkeit bezeichnet werden. Bei der Hydraulikflüssigkeit handelt es sich beispielsweise um Öl, insbesondere Schmieröl.The low-pressure pump 12 discharges hydraulic fluid 20 into a switching line 22, which is at a low pressure p 12 . The pressurized hydraulic fluid 20 could therefore also be referred to as low-pressure hydraulic fluid. The hydraulic fluid is, for example, oil, in particular lubricating oil.

Die Hochdruck-Pumpe 14 ist über ein Doppel-Rückschlagventil 24 mit der Schaltleitung 22 verbunden. Die Schaltleitung 22 enthält zudem ein Magnetventil 26, mit dem der Druck p in der Schaltleitung 22 zu einer Kupplung 28 durchgeschaltet werden kann. Bei dem Magnetventil 26 kann es sich um ein Proportionalventil handeln, das ist aber nicht notwendig.The high pressure pump 14 is connected via a double check valve 24 to the switching line 22. The switching line 22 also includes a solenoid valve 26, with which the pressure p in the switching line 22 can be switched through to a coupling 28. The solenoid valve 26 may be a proportional valve, but it is not necessary.

Figur 1 zeigt das Magnetventil 26 in seiner Nulldruckstellung, in der die Kupplung 28 über eine Rückleitung 30 mit einem Sumpf 32 verbunden ist. In dem Sumpf 32 kann beispielsweise Umgebungsdruck herrschen. FIG. 1 shows the solenoid valve 26 in its zero pressure position, in which the coupling 28 is connected via a return line 30 to a sump 32. For example, ambient pressure may prevail in the sump 32.

Da die Kupplung 28 druckfrei ist, befindet sie sich in der vorliegenden Ausführungsform im geöffneten Zustand. Beispielsweise werden dazu Kupplungsscheiben 34.1, 34.2, ... durch eine Feder 36 auf Abstand gehalten. Wird die Kupplung 28 mit Hydraulikflüssigkeit 20 beaufschlagt, so drückt die Hydraulikflüssigkeit 20 auf einen Kolben 37, der wiederum die Kupplungsscheiben 34.1, 34.2, ... zusammenpresst und so die Kupplung 37 zumindest teilweise schließt.Since the clutch 28 is pressure-free, it is in the present embodiment in the open state. For example, to clutch plates 34.1, 34.2, ... held by a spring 36 at a distance. If the clutch 28 is acted upon by hydraulic fluid 20, the hydraulic fluid 20 presses on a piston 37, which in turn compresses the clutch discs 34.1, 34.2,... And thus at least partially closes the clutch 37.

Es ist zu erkennen, dass die Schaltleitung 22 mit einem Schmierölempfänger 38 verbunden ist. In der in Figur 1 gezeigten Betriebsstellung versorgt das Hydraulikaggregat 10 den Schmierölempfänger 38 mit Schmieröl, es wird aber lediglich Hydraulikflüssigkeit auf Niederdruck p12 bereitgestellt. Der Schmierölempfänger 38 ist Teil eines Schmierölkreislaufs 39, der auch die Verbindungsleitungen umfasst.It can be seen that the switching line 22 is connected to a lubricating oil receiver 38. In the in FIG. 1 shown operating position, the hydraulic unit 10 supplies the lubricating oil receiver 38 with lubricating oil, but it is only provided hydraulic fluid to low pressure p 12 . The lubricating oil receiver 38 is part of a lubricating oil circuit 39, which also includes the connecting lines.

Figur 2 zeigt das Magnetventil 26 in seiner Schaltstellung, in der die Schaltleitung 22 die Kupplung 28 mit Niederdruck p12 versorgt. Ein p12 in der Kupplung 28 steigt damit auf den p12 an. Der Niederdruck p12 ist so stark, dass die Kupplung 28 mit Schlupf kuppelt. Das heißt, dass eine Drehfrequenz einer Antriebsseite der Kupplung und damit zumeist eine Drehfrequenz n16 des Antriebs 16 größer ist als eine Drehfrequenz n28 der Kupplung 28 auf ihrer Abtriebsseite. FIG. 2 shows the solenoid valve 26 in its switching position in which the switching line 22, the clutch 28 with low pressure p 12 supplies. A p 12 in the clutch 28 thus increases to the p 12 . The low pressure p 12 is so strong that the clutch 28 couples with slippage. That is, a rotational frequency of a drive side of the clutch and thus usually a rotational frequency n 16 of the drive 16 is greater than a rotational frequency n 28 of the clutch 28 on its output side.

Dadurch, dass die Kupplung 28 mit Schlupf kuppelt, wird ein Antriebsdrehmoment M28 auf die Hochdruck-Pumpe 14 übertragen. Die Hochdruck-Pumpe 14 bringt dadurch Hydraulikflüssigkeit 20 auf Hochdruck p14, der größer ist als der Niederdruck p12. Dadurch schaltet das Doppel-Rückschlagventil 24 und dadurch wird der Hochdruck p14 an die Kupplung 28 angelegt. Da also die Druckseite der Hochdruck-Pumpe 14 nun mit der Kupplung 28 verbunden ist, steigt der Kupplungsdruck p28 auf den Hochdruck p14 an.By coupling the clutch 28 with slip, a drive torque M 28 is transmitted to the high pressure pump 14. The high pressure pump 14 thereby brings hydraulic fluid 20 to high pressure p 14 , which is greater than the low pressure p 12th As a result, the double-check valve 24 switches and thereby the high-pressure p 14 is applied to the clutch 28. Thus, since the pressure side of the high pressure pump 14 is now connected to the clutch 28, the clutch pressure p 28 increases to the high pressure p 14 .

Die Verbindung zwischen der Hochdruck-Pumpe 14 und der Kupplung 28 wird als Druckleitung 40 bezeichnet. Es sei darauf hingewiesen, dass die Druckleitung 40 teilweise mit der Schaltleitung 22 identisch sein kann und in der gezeigten Ausführungsform auch ist. Die Druckleitung 40 steht in Verbindung mit einem Druckölempfänger 42, beispielsweise einer Kupplung oder einem sonstigen hydraulischen Aktor, der Teil eines Druckölkreislaufs 43 ist.The connection between the high-pressure pump 14 and the clutch 28 is referred to as pressure line 40. It should be noted that the pressure line 40 may be partially identical to the switching line 22 and in the embodiment shown also. The pressure line 40 is in communication with a pressure oil receiver 42, such as a clutch or other hydraulic actuator, which is part of a pressure oil circuit 43.

Durch den steigenden Druck in der Kupplung 28 nimmt der Schlupf in der Kupplung 28 immer weiter ab, bis die Kupplung schließlich vollständig eingekuppelt ist. In diesem Zustand sind der Antrieb 16 und die Hochdruck-Pumpe 14 drehfest miteinander verbunden.Due to the increasing pressure in the clutch 28, the slip in the clutch 28 continues to decrease until the clutch is finally fully engaged. In this state, the drive 16 and the high-pressure pump 14 are rotatably connected to each other.

Figur 3 zeigt den Zustand, in dem beide Pumpen 12, 14 Fluid fördern. Es ist zu erkennen, dass beide Pumpen 12, 14 durch eine gemeinsame Versorgungsleitung 44 aus dem Sumpf 32 mit Hydraulikflüssigkeit versorgt werden. Vom Schmierölempfänger 38 und Druckölempfänger 42 zurück laufende Hydraulikflüssigkeit fließt in den Sumpf 32. FIG. 3 shows the state in which both pumps 12, 14 convey fluid. It can be seen that both pumps 12, 14 are supplied by a common supply line 44 from the sump 32 with hydraulic fluid. Hydraulic fluid returning from the lubricating oil receiver 38 and pressurized oil receiver 42 flows into the sump 32.

Figur 4 zeigt den Druckverlauf des Kupplungsdrucks p28,SdT(t) in der Kupplung 28 bei einem Hydraulikaggregat nach dem Stand der Technik. Es ist zu erkennen, dass der Kupplungsdruck pSdT(t) schlagartig ansteigt und abfällt, was häufig unerwünscht ist. Eingezeichnet ist zudem ein errechneter Druckverlauf p14(t) für ein erfindungsgemäßes Hydraulikaggregat. Nach einem Schaltpunkt ts steigt der Druck p14 vergleichsweise langsam an. Zu einem Zeitpunkt t1 beginnt die Hochdruck-Pumpe 14 zu fördern. Aufgrund des Rückkopplungseffekts steigt das Antriebs-Drehmoment M28 ebenso an wie daraus resultierend der Hochdruck p14 und damit der Kupplungsdruck p28. FIG. 4 shows the pressure curve of the clutch pressure p 28, SdT (t) in the clutch 28 in a hydraulic unit according to the prior art. It can be spotted, that the clutch pressure p SdT (t) abruptly increases and decreases, which is often undesirable. Also marked is a calculated pressure curve p 14 (t) for a hydraulic unit according to the invention. After a switching point t s , the pressure p 14 increases comparatively slowly. At a time t 1 , the high pressure pump 14 begins to promote. Due to the feedback effect, the drive torque M 28 increases as well as the result of the high pressure p 14 and thus the clutch pressure p 28th

Die Geschwindigkeit des Druckanstieg des Kupplungsdrucks p28 kann verringert werden, indem - wie gemäß einer bevorzugten Ausführungsform vorgesehen - in der Druckleitung 40 zwischen der Druckseite der Hochdruck-Pumpe 14 und der Kupplung 28 eine Durchflussbeeinflussungsvorrichtung 45 (vgl. Figur 1) angeordnet wird. Alternativ oder zusätzlich kann ein Querschnitt zumindest eines Teils der Druckleitung 40 so gewählt sein, dass die Druckleitung die Wirkung der Durchflussbeeinflussungsvorrichtung 45 hat. So kann der in Figur 4 gezeigte Kupplungsdruck-Verlauf p28(t) erreicht werden.The speed of the pressure increase of the clutch pressure p 28 can be reduced by providing a flow rate influencing device 45 (see FIG. 2) in the pressure line 40 between the pressure side of the high-pressure pump 14 and the clutch 28, as provided in a preferred embodiment. FIG. 1 ) is arranged. Alternatively or additionally, a cross-section of at least part of the pressure line 40 may be selected such that the pressure line has the effect of the flow-influencing device 45. So can the in FIG. 4 shown clutch pressure curve p 28 (t) can be achieved.

Zu einem Durchschaltzeitpunkt t2 kuppelt die Kupplung 28 voll, das heißt ohne Schlupf, und der Hochdruck p14 erreicht seinen Maximalwert p14,max. Dies entspricht dem maximalen Druck, den die Hochdruck-Pumpe 14 liefert.At a switching time t 2, the clutch 28 fully couples, that is, without slippage, and the high pressure p 14 reaches its maximum value p 14, max . This corresponds to the maximum pressure that the high-pressure pump 14 supplies.

Mittels einer Durchflussbeeinflussungsvorrichtung 45, beispielsweise einer Drossel, kann der Druckanstieg in der Kupplung 28 verzögert werden. Damit kann die Stärke der positiven Rückkopplung und damit die Zeit zwischen dem Schaltpunkt und dem Zeitpunkt, zu dem der volle Hochdruck anliegt, eingestellt werden.By means of a flow-influencing device 45, for example a throttle, the pressure rise in the clutch 28 can be delayed. Thus, the strength of the positive feedback and thus the time between the switching point and the time when the full high pressure is applied, can be set.

Die Figuren 5a, 5b und 5c zeigen eine weitere Ausführungsform, bei der die Kupplung 28 ein Gestänge 46 aufweist, mittels dem die Kraft von einem druckbeaufschlagten Zylinder 48 auf die Kupplungsscheiben 34 übertragen wird. Die Funktionsweise unterscheidet sich nicht von derjenigen, die für die Figuren 1 bis 3 beschrieben wurde. Bezugszeichenliste 10 Hydraulikaggregat p12 Niederdruck 12 Niederdruck-Pumpe p14 Hochdruck 14 Hochdruck-Pumpe p28 Kupplungsdruck 16 Antrieb Δp Differenzdruck 18 Welle M28 Antriebs-Drehmoment n Drehfrequenz 20 Hydraulikflüssigkeit ts Schaltpunkt 22 Schaltleitung 24 Doppel-Rückschlagventil 26 Magnetventil 28 Kupplung 30 Rückleitung 32 Sumpf 34 Kupplungsscheiben 36 Feder 37 Kolben 38 Schmierölempfänger 39 Schmierölkreislauf 40 Druckleitung 42 Druckölempfänger 43 Druckölkreislauf 44 Versorgungsleitung 45 Durchflussbeeinflussungsvorrichtung 46 Gestänge 48 Zylinder The Figures 5a, 5b and 5c show a further embodiment in which the coupling 28 comprises a linkage 46, by means of which the force is transmitted from a pressurized cylinder 48 to the clutch plates 34. The functioning does not differ from that for the FIGS. 1 to 3 has been described. <B> LIST OF REFERENCES </ b> 10 hydraulic power unit p 12 low pressure 12 Low pressure pump p 14 high pressure 14 High pressure pump p 28 clutch pressure 16 drive Ap differential pressure 18 wave M 28 Driving torque n rotational frequency 20 hydraulic fluid ts switching point 22 switching line 24 Double check valve 26 magnetic valve 28 clutch 30 return 32 swamp 34 clutch discs 36 feather 37 piston 38 Oil receiver 39 Lubricating oil circuit 40 pressure line 42 Pressure oil receiver 43 Pressure oil circulation 44 supply line 45 Flow influencing device 46 linkage 48 cylinder

Claims (7)

  1. Hydraulic unit (10) with
    (a) a low pressure pump (12) for emitting low pressure (p12) hydraulic fluid (20),
    (b) a drive (16) that is connected to the low pressure pump (12) in order to drive it,
    (c) a high pressure pump (14) for emitting high pressure (p14) hydraulic fluid (20),
    wherein a maximum pressure that can be emitted by the high pressure pump (14) is greater than a maximum pressure that be emitted by the low pressure pump (12), and
    (d) a coupling (28) by means of which the high pressure pump (14) can be reversibly switched into a torque flow with the drive (16),
    (e) wherein the coupling (28) is connected to the low pressure pump (12) in such a way that the coupling (28) can be activated by means of hydraulic fluid (20) at a low pressure (p12),
    (f) wherein the coupling (28) is configured such that, when it is subjected to low pressure (p12), it couples with a slip and transfers a drive torque (M28) to the high pressure pump (14) so the high pressure pump (14) emits hydraulic fluid (20) at a high pressure (p14) which is greater than the low pressure (p12),
    (g) wherein the coupling (28) is connected to the high pressure pump (14) in such a way that an increase in the drive torque (M28) that is transferred from the coupling (28) to the high pressure pump (14) causes an increase in the high pressure (p14),
    characterised by the fact that
    (h) the coupling (28) is connected to the high pressure pump (14) such that the increase in the high pressure (p14) causes an increase in the drive torque (M28) on the high pressure pump (14).
  2. Hydraulic unit (10) according to claim 1, characterised by the fact that
    - the coupling (28) is connected to the high pressure pump (14) by means of a pressure line and
    - the pressure line (40) is designed in such a way that a sudden increase in pressure on a pressure side of the high pressure pump (14), which is greater than the coupling pressure p28 in the coupling by a differential pressure of Δp, leads to a coupling pressure that is greater by half of the differential pressure Δp after a half-life,
    - wherein the half-life is at least 200 milliseconds.
  3. Hydraulic unit (10) according to claim 2, characterised by the fact that the pressure line (40) comprises a flow rate influencing device (45), in particular a throttle, a valve and/or a pressure relief device.
  4. Hydraulic device (10) according to one of the above claims, characterised by the fact that
    - the coupling (28) is connected to the low pressure pump (12) by means of a switch line (22) and
    - the switch line (22) comprises a magnetic valve (26), especially a proportional valve.
  5. Marine gearbox with
    (a) a hydraulic unit (10) according to one of the above claims,
    (b) wherein the low pressure pump (12) is part of a lubricant circuit (39).
  6. Marine gearbox according to claim 5, characterised by the fact that the high pressure pump (14) is part of a pressure oil circuit (43).
  7. Marine gearbox according to claim 6, characterised by
    a coupling (28), which forms part of the pressure oil circuit (43) and is designed to switch by means of hydraulic fluid (20) at high pressure (p14).
EP16164273.1A 2015-04-10 2016-04-07 Hydraulic assembly Active EP3078855B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015206464.6A DE102015206464A1 (en) 2015-04-10 2015-04-10 hydraulic power unit

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EP3078855A3 EP3078855A3 (en) 2016-10-19
EP3078855B1 true EP3078855B1 (en) 2019-01-30

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ID=55806139

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Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010174927A (en) * 2009-01-27 2010-08-12 Toyota Motor Corp Idling stop system
DE102010023713A1 (en) * 2009-07-06 2011-03-17 Schaeffler Technologies Gmbh & Co. Kg hydraulic arrangement
KR101394039B1 (en) * 2012-09-03 2014-05-12 현대자동차 주식회사 Oil pressure supply system of automatic transmission

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TR201903976T4 (en) 2019-04-22
EP3078855A3 (en) 2016-10-19
EP3078855A2 (en) 2016-10-12

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