EP3289191B1 - Auxiliaries driving device - Google Patents

Auxiliaries driving device Download PDF

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Publication number
EP3289191B1
EP3289191B1 EP16719210.3A EP16719210A EP3289191B1 EP 3289191 B1 EP3289191 B1 EP 3289191B1 EP 16719210 A EP16719210 A EP 16719210A EP 3289191 B1 EP3289191 B1 EP 3289191B1
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EP
European Patent Office
Prior art keywords
oil
oil pump
pump
control valve
drive device
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EP16719210.3A
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German (de)
French (fr)
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EP3289191A1 (en
Inventor
Timm BRÖCKER
Tom MACHT
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Volkswagen AG
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Volkswagen AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0253—Pressure lubrication using lubricating pumps characterised by the pump driving means

Definitions

  • the invention relates to an auxiliary drive device with the features of claim 1.
  • the accessory drive device has a differential in the form of a planetary gear.
  • the planetary gear has a ring gear, a planet carrier and a sun gear.
  • a crankshaft of the motor vehicle is connected to the planet carrier, wherein the ring gear and the sun gear each serve as an output for each auxiliary unit.
  • Serving as an alternator three-phase generator is connected to the ring gear.
  • a water pump is connected to the sun gear of the planetary gear.
  • the ring gear is connected via a belt transmission with the alternator.
  • the sun gear is connected via another belt drive with the water pump.
  • the alternator and the water pump form ancillaries, which are driven by the internal combustion engine via the planetary gear.
  • a locking device is arranged, which shut down the water pump at a cold start.
  • the locking device is designed as an electromagnetic clutch.
  • the electromagnetic clutch brakes the water pump, the speed of the alternator is increased.
  • a controller is supplied with a signal dependent on the cooling water temperature. With a cold engine, only little or no cooling water throughput is desired.
  • the on-board voltage induced in the alternator depends directly on the drive speed of the alternator. When the rotational speed of the crankshaft is low, a high gear ratio can be achieved, so that the electric demand is covered even at an idling speed. On the other hand, a lowering of the transmission ratio at high engine speeds is possible.
  • the alternator can be operated in a favorable efficiency range of their characteristic field.
  • oil pumps for motor vehicles are known in the prior art. Oil is conveyed by means of the oil pump from an oil sump to lubrication points of the internal combustion engine. The oil pump is driven by the internal combustion engine of the motor vehicle via the crankshaft.
  • From the generic DE 38 14 750 A1 is a drive assembly with a planetary gear known.
  • the planetary gear is driven by an internal combustion engine via a ring gear.
  • a lubricant pump is driven by a sun gear.
  • a planetary carrier drives a shaft with a gear, which is in engagement with a gear.
  • the gear and the gear form a tooth pump. Both pumps are connected on their suction side with a lubricant reservoir and drive technology via the planetary gear with the internal combustion engine.
  • the GB 833 273 A shows two pumps which are driven by a planetary gear, namely a first sun gear and a second sun gear.
  • the two sun gears are coupled via planet gears with a ring gear.
  • the ring gear is driven by the crankshaft.
  • the invention is therefore based on the object to design the generic ancillary drive device such and further, so that the fuel consumption can be reduced.
  • the two ancillaries are designed as oil pumps. As a result, the mechanical drive power to the oil supply of the internal combustion engine can be reduced. With the help of the planetary gearbox, the two oil pumps are driven. Depending on the state ratio of the planetary gear and the input speed both oil pumps can be operated variable in number depending on each other. The two oil pumps can optionally be operated at different speeds.
  • the total delivery volume can be adapted to the needs. By an appropriate choice of geometrical delivery volumes, an adjustment of the total delivery volume flow and the oil pressure to the current needs of the internal combustion engine can be made substantially at constant input speed of the drive, namely the corresponding crankshaft.
  • the drive is formed in particular by the internal combustion engine of the motor vehicle.
  • the drive power required for oil supply can be reduced as needed.
  • the oil pumps can be operated in an efficiency-optimized range. As a result, the friction loss can be reduced.
  • the speed variation of the two oil pumps via a control valve.
  • the speed variation is set via the control valve.
  • the two oil pumps can be controlled or controlled by means of the control valve. In a first position of the control valve promotes the second oil pump and the first oil pump is. In a second position of the control valve is the second oil pump and the first oil pump delivers. When the first oil pump is stopped, the second oil pump rotates at the maximum possible speed. When the second oil pump is stopped, the first oil pump rotates at the maximum possible speed. As a result, different oil pressure levels can be realized.
  • the control valve blocks the flow through the first oil pump.
  • the control valve locks in the first position, in particular the flow through one of the first oil pump associated pressure line.
  • the flow through a second oil pump zuabel pressure line and the flow through a second oil pump associated with the suction line is released in the first position.
  • the control valve In the second position, the control valve allows the flow through the first oil pump.
  • the control valve opens in the second position in particular the flow through the first oil pump associated pressure line.
  • the flow through the second oil pump zugordnet pressure line and / or the flow through the second oil pump associated with the suction line is locked in the second position. The fact that the suction line is locked, prevents oil from the pump runs back into the oil sump. Due to the oil held in the second oil pump, the second oil pump is blocked.
  • the planetary gear is preferably driven via the ring gear.
  • the ring gear is drivingly coupled to the crankshaft.
  • the first oil pump is preferably non-rotatably connected to the sun gear of the planetary gear.
  • the second oil pump is rotatably connected to the planet carrier.
  • the second oil pump serves as a brake. If the planet carrier is held by means of the second oil pump, then the sun gear rotates at maximum speed. The first oil pump is driven at maximum speed.
  • the control valve is located in the second position, the suction line and the brake pressure line are closed, the second oil pump does not rotate.
  • the actuating piston is moved to the end position of the first position, the suction line and the pressure line of the brake are released and the pressure line of the first oil pump is closed.
  • the second oil pump or brake starts to rotate and the first oil pump slows down. When the actuating piston has reached the end position of the first position, the first oil pump is complete and only the second oil pump rotates and delivers.
  • the control valve is in particular pressure-actuated, wherein the voltage applied to the outlet of the two oil pumps oil pressure is returned to the control valve via a control line.
  • the output of the oil pumps form corresponding pressure lines.
  • the control valve is spring loaded against this oil pressure. If the force due to the oil pressure is less than the spring force, then the control valve is arranged in the first position, wherein the first oil pump is stationary and the second oil pump delivers. If the force due to the oil pressure is greater than the spring force, then the control valve is disposed in the second position, wherein the second oil pump is and promotes the first oil pump.
  • the first oil pump is coupled in a preferred embodiment with a sun gear and the second oil pump is coupled to a planet carrier.
  • the drive is coupled to a ring gear.
  • the drive is formed by a crankshaft of the motor vehicle.
  • the crankshaft may be coupled via an intermediate gear with the ring gear.
  • one of the oil pumps is coupled to a vacuum pump.
  • the coupled with the vacuum pump oil pump and the vacuum pump are formed by a tandem pump. This has the advantage that, in particular in the low speed range of the drive negative pressure can be provided. At the top Speed range, the not coupled with the vacuum pump oil pump can take over the significant delivery share and in particular operated alone. Further advantages over a vacuum pump driven by a separate electric drive are that the design as a tandem pump is cheaper than the electric drive, and the power consumption is lower than when using a conventional vacuum pump.
  • the first oil pump may be coupled to the vacuum pump.
  • the oil pump coupled to the vacuum pump is operatively coupled to the sun gear.
  • the coupled with the vacuum pump oil pump is functionally effective driven by the sun gear.
  • the vacuum pump runs at the speed of the sun gear, since the oil pump coupled to the vacuum pump is functionally effective driven by means of the sun gear and the drives of this oil pump and the vacuum pump are coupled.
  • At low speeds of the crankshaft is the planet carrier and the vacuum pump and the first oil pump promote with the corresponding maximum pump speed as a function of the respective crankshaft speed. As the engine speed increases, the speed of the sun gear decreases and the speed of the planet carrier increases.
  • the pump speed of the first oil pump and the vacuum pump is reduced and the planet carrier drives the second oil pump with increasing speed.
  • the coupled with the vacuum pump, the first oil pump and the vacuum pump thus have a sinking with increasing speed of the drive pump speed.
  • first oil pump can be stopped or operated only at low speed.
  • the vacuum pump is driven at the same speed as the coupled oil pump or by means of a ratio with a proportional speed. The Mamalaufrich the vacuum pump is thereby increased.
  • FIG. 1 an accessory drive device 1 for a motor vehicle is shown.
  • the accessory drive device 1 has a planetary gear 2.
  • two ancillaries 3, 4 are provided.
  • the two auxiliary units 3, 4 are by means of a drive (not shown in detail) via the planetary gear 2 drivable.
  • the drive is designed in particular as an internal combustion engine of the motor vehicle.
  • a crankshaft 5 is driven with a torque M.
  • the crankshaft 5 is mounted in a housing 6.
  • the planetary gear 2 has a ring gear 7, a planet carrier 8 with a plurality of planetary gears (not shown in detail) and a sun gear 9.
  • the planet gears are rotatably mounted on the planet carrier 8.
  • the planet gears are now on the one hand in meshing engagement with the internal toothing of the ring gear 7 and on the other in meshing engagement with the external toothing of the sun gear.
  • the crankshaft 5 is rotatably connected to the ring gear 7.
  • the crankshaft 5 drives the ring gear 7.
  • the ring gear 7 forms the drive member (unspecified) of the planetary gear 2.
  • the first auxiliary unit 3 is rotatably connected via a shaft 10 with the sun gear 9. Concentric with the shaft 10, a hollow shaft 11 is arranged, wherein the hollow shaft 11 rotatably connects the second auxiliary unit 4 with the planet carrier 8.
  • the planet carrier 8 drives the second auxiliary unit 4.
  • the two ancillaries 3, 4 are designed as oil pumps 12, 13.
  • the first auxiliary unit 3 is formed by a first oil pump 12 and the second auxiliary unit 4 is formed by a second oil pump 13.
  • the delivery volume can be adapted to the needs of the internal combustion engine by the speed variability of the planetary gear 2.
  • the two oil pumps 12, 13 are driven.
  • both oil pumps 12, 13 are operated variable in number depending on each other.
  • the second oil pump 13 rotates at the maximum possible speed.
  • the first oil pump 12 rotates at maximum speed
  • the second oil pump 13 By an appropriate choice of geometric delivery volumes, an adjustment of the total delivery volume flow to the current oil demand, regardless of the input speed of the crankshaft 5 are made.
  • the two oil pumps 12, 13 may be of identical construction. In an alternative embodiment, the oil pumps 12, 13 are formed differently.
  • the oil pump 12 and / or the oil pump 13 may be formed, for example, as gear pumps or as vane pumps.
  • the two oil pumps 12, 13 each have a rotor, wherein the rotor with the corresponding shaft 10 and the hollow shaft 11 is connected.
  • the two oil pumps 12, 13 promote oil from a common oil sump 14.
  • the oil is thereby conveyed from the oil sump 14 via the two oil pumps 12, 13 to the internal combustion engine 15.
  • Each of the oil pumps 12, 13 is a suction line 16, 18 and a pressure line 17, 19 assigned.
  • the oil pump 12 is associated with a suction line 16 and a pressure line 17.
  • the oil pump 13 is associated with a suction line 18 and a pressure line 19.
  • the accessory drive device 1 further comprises a control valve 20.
  • the control valve 20 has a plurality of unspecified ports.
  • a first pressure line section 17a can be connected to a second pressure line section 17b of the pressure line 17 by means of the control valve 20, or these two pressure line sections 17a, 17b can be separated from one another by means of the control valve 20.
  • the pressure line 17 of the first oil pump 12 can be blocked and opened by means of the control valve 20.
  • the pressure line 19 of the second oil pump 13 can be locked and opened.
  • the pressure line 19 has two pressure line sections 19a and 19b, wherein the two pressure line sections 19a, 19b are connectable and separable by means of the control valve 20.
  • the pressure line section 19 a is connected to an input of the control valve 20 and the pressure line section 19 b is connected to an output of the control valve 20.
  • the suction line 18 can be locked and opened.
  • the suction line 18 has two Saug effetsabête 18a, 18b, wherein the two Saug effetsabête 18a, 18b connected by means of the control valve 20 and are separable from each other.
  • both the suction line 18 and the pressure line 19 of the second oil pump 13 are opened by means of the control valve 20.
  • the pressure line 17 of the first oil pump 12 is blocked by means of the control valve 20.
  • the first oil pump 12 is braked and the second oil pump 13 rotates and delivers.
  • the control valve 20 is pressure-actuated, the oil pressure applied at the outlet or in the pressure line sections 17b, 19b of the two oil pumps 12, 13 being fed back to the control valve 20 via a control line 21.
  • the control valve 20 is spring-loaded, and when the force due to the oil pressure is less than the spring force, the control valve 20 in the first position ( Fig. 3 ) is arranged. In the in Fig. 2 shown second position is a high oil pressure to the control line 21, so that the spring is compressed. When the force due to the oil pressure is greater than the spring force, the control valve 20 in the second position ( Fig. 2 ) arranged. This results in the control depending on the oil pressure. In the in Fig. 3 illustrated basic position or first position is a low oil pressure 21, wherein the spring force is sufficient to move the actuator piston in the first position.
  • FIG. 3 an accessory drive device 22 is shown.
  • the accessory drive device 22 is constructed similar to the accessory drive device 22, with like reference numerals now being used for parts that are substantially functionally identical.
  • the ancillary drive device 22 also has a planetary gear 2 and two ancillaries 3, 4 in the form of oil pumps 12, 13.
  • the planetary gear 2 has a ring gear 7, a planet carrier 8 and a sun gear 9.
  • the ring gear 5 is functionally effective via the crankshaft 5 driven.
  • the crankshaft 5 is coupled via a module drive 23 with the ring gear 7.
  • the module drive 23 consists essentially of a non-rotatably mounted on the crankshaft 5 gear 24, an intermediate 25 and a further gear 26, wherein the gear 26 in particular rotatably on a hollow shaft 27 is arranged.
  • the sun gear 9 drives the first oil pump 12 via a first pump shaft 28.
  • the planet carrier 8 drives the second oil pump 13 via a second pump shaft 29.
  • one of the oil pumps 12, 13, namely, in particular, the first oil pump 12 is operatively coupled in terms of drive technology to a vacuum pump 30.
  • the vacuum pump 30 is operatively coupled to the pump shaft 28 via an intermediate shaft 31.
  • the vacuum pump 30 may serve, for example, to supply a brake booster or the like.
  • the coupled to the vacuum pump 30, first oil pump 12 and the vacuum pump 30 are functionally effective by means of the sun gear 9 drivable.
  • the first oil pump 11 and the vacuum pump 30 are operated at the same pump speed.
  • the pump speed of the second oil pump 13 differs in particular from the speed of the first oil pump 12 and thus also the speed of the vacuum pump 30.
  • the coupled to the vacuum pump 30, the first oil pump 12 and the vacuum pump 30 have a sinking with increasing speed of the drive pump speed.
  • the second oil pump 13 has an increasing pump speed with increasing speed of the drive. In the range of the maximum speed of the drive, it is conceivable that the first oil pump 12 and the vacuum pump are substantially and the second oil pump 13 is operated alone. In the low speed range is promoted mainly by means of the first oil pump 12 and thereby the vacuum pump 30 is driven, as in particular in the low speed range pumping capacity of the vacuum pump 30 is required.
  • the accessory drive device 22 is operated such that the vacuum pump 30 does not or only at low speed rotates at high speeds. This increases the endurance capability of the vacuum pump 30 and serves the consumption reduction.
  • Fig. 5 are different delivery volume above the engine speed, ie the speed of the crankshaft 5 applied. It is a maximum delivery volume 32, a minimum delivery volume 33 and a demand curve 34 of an internal combustion engine shown.
  • the total delivery volume V ⁇ Ges results from the sum of the delivery volumes of the first oil pump 12 V ⁇ Pumpe1 and the second oil pump 13 V ⁇ Pumpe2 .
  • the minimum delivery volume 32 adjusts itself when the planet carrier 8 is stationary, ie when the rotational speed n planet carrier is equal to zero revolutions per minute and thus the first oil pump 12 is running at maximum rotational speed.
  • the minimum delivery volume 33 results when the sun gear is stationary, ie when substantially only the second oil pump 13 is driven and the speed of the sun gear n sun is equal to zero revolutions per minute.
  • the demand curve 34 lies between the maximum delivery volume 32 and the minimum delivery volume 33 for all illustrated engine speeds. At high engine speeds while the demand curve 34 is closer to the minimum delivery volume 33, so by adjusting the total delivery volume V ⁇ Ges to the demand curve 34, the first oil pump 12 has little or no need to promote to meet the demand.

Description

Die Erfindung betrifft eine Nebenaggregatsantriebsvorrichtung mit den Merkmalen des Patentanspruches 1.The invention relates to an auxiliary drive device with the features of claim 1.

Aus der DE 42 00 918 C1 ist eine Nebenaggregatsantriebsvorrichtung eines Kraftfahrzeuges bekannt. Die Nebenaggregatsantriebsvorrichtung weist ein Ausgleichsgetriebe in Form eines Planetengetriebes auf. Das Planetengetriebe weist ein Hohlrad, einen Planetenträger und ein Sonnenrad auf. Eine Kurbelwelle des Kraftfahrzeuges ist mit dem Planetenträger verbunden, wobei das Hohlrad und das Sonnenrad jeweils als Abtrieb für jeweils ein Nebenaggregat dienen. Ein als Lichtmaschine dienender Drehstromgenerator ist mit dem Hohlrad verbunden. Eine Wasserpumpe ist mit dem Sonnenrad des Planetengetriebes verbunden. Das Hohlrad ist über ein Umschlingungsgetriebe mit dem Drehstromgenerator verbunden. Das Sonnenrad ist über ein weiteres Umschlingungsgetriebe mit der Wasserpumpe verbunden. Der Drehstromgenerator und die Wasserpumpe bilden Nebenaggregate, die mittels des Verbrennungsmotors über das Planetengetriebe antreibbar sind. Zwischen dem Abtrieb des Planetengetriebes und der Wasserpumpe ist eine Feststellvorrichtung angeordnet, die bei einem Kaltstart die Wasserpumpe stilllegt. Die Feststellvorrichtung ist als elektromagnetische Kupplung ausgebildet. Wenn die elektromagnetische Kupplung die Wasserpumpe bremst, wird die Drehzahl der Lichtmaschine erhöht. Bei einem Kaltstart des Verbrennungsmotors wird einem Regler ein von der Kühlwassertemperatur abhängiges Signal zugeführt. Bei kalter Brennkraftmaschine ist nur ein geringer oder gar kein Kühlwasserdurchsatz erwünscht. Die in der Lichtmaschinen induzierte Bordspannung hängt direkt von der Antriebsdrehzahl der Lichtmaschine ab. Wenn die Drehzahl der Kurbelwelle niedrig ist, kann ein hohes Übersetzungsverhältnis erreicht werden, so dass der elektrische Bedarf auch bei einer Leerlaufdrehzahl gedeckt ist. Andererseits ist ein Absenken des Übersetzungsverhältnis bei hohen Motordrehzahlen möglich. Die Lichtmaschine kann in einem günstigen Wirkungsgradbereich ihres Kennfeldes betrieben werden.From the DE 42 00 918 C1 An ancillary drive device of a motor vehicle is known. The accessory drive device has a differential in the form of a planetary gear. The planetary gear has a ring gear, a planet carrier and a sun gear. A crankshaft of the motor vehicle is connected to the planet carrier, wherein the ring gear and the sun gear each serve as an output for each auxiliary unit. Serving as an alternator three-phase generator is connected to the ring gear. A water pump is connected to the sun gear of the planetary gear. The ring gear is connected via a belt transmission with the alternator. The sun gear is connected via another belt drive with the water pump. The alternator and the water pump form ancillaries, which are driven by the internal combustion engine via the planetary gear. Between the output of the planetary gear and the water pump, a locking device is arranged, which shut down the water pump at a cold start. The locking device is designed as an electromagnetic clutch. When the electromagnetic clutch brakes the water pump, the speed of the alternator is increased. During a cold start of the internal combustion engine, a controller is supplied with a signal dependent on the cooling water temperature. With a cold engine, only little or no cooling water throughput is desired. The on-board voltage induced in the alternator depends directly on the drive speed of the alternator. When the rotational speed of the crankshaft is low, a high gear ratio can be achieved, so that the electric demand is covered even at an idling speed. On the other hand, a lowering of the transmission ratio at high engine speeds is possible. The alternator can be operated in a favorable efficiency range of their characteristic field.

Ferner sind im Stand der Technik Ölpumpen für Kraftfahrzeuge bekannt. Öl wird mittels der Ölpumpe aus einem Ölsumpf zu Schmierstellen des Verbrennungsmotors gefördert. Die Ölpumpe wird dabei von dem Verbrennungsmotor des Kraftfahrzeuges über die Kurbelwelle angetrieben.Furthermore, oil pumps for motor vehicles are known in the prior art. Oil is conveyed by means of the oil pump from an oil sump to lubrication points of the internal combustion engine. The oil pump is driven by the internal combustion engine of the motor vehicle via the crankshaft.

Aus der gattungsbildenden DE 38 14 750 A1 ist eine Antriebanordnung mit einem Planetengetriebe bekannt. Das Planetengetriebe wird durch eine Brennkraftmaschine über ein Ringrad angetrieben. Eine Schmiermittelpumpe wird über ein Sonnenrad angetrieben. Ein Planetenträger treibt eine Welle mit einem Zahnrad an, das im Eingriff mit einem Zahnrad steht. Das Zahnrad und das Zahnrad bilden eine Zahnpumpe. Beide Pumpen sind auf ihrer Saugseite mit einem Schmiermittelvorratsbehälter und antriebstechnisch über das Planetengetriebe mit der Brennkraftmaschine verbunden.From the generic DE 38 14 750 A1 is a drive assembly with a planetary gear known. The planetary gear is driven by an internal combustion engine via a ring gear. A lubricant pump is driven by a sun gear. A planetary carrier drives a shaft with a gear, which is in engagement with a gear. The gear and the gear form a tooth pump. Both pumps are connected on their suction side with a lubricant reservoir and drive technology via the planetary gear with the internal combustion engine.

Die GB 833 273 A zeigt zwei Pumpen, die über ein Planetengetriebe, nämlich ein erstes Sonnenrad und ein zweites Sonnenrad angetrieben werden. Die beiden Sonnenräder sind über Planetenräder mit einem Ringrad gekoppelt. Das Ringrad wird von der Kurbelwelle angetrieben.The GB 833 273 A shows two pumps which are driven by a planetary gear, namely a first sun gear and a second sun gear. The two sun gears are coupled via planet gears with a ring gear. The ring gear is driven by the crankshaft.

Aus der CN 203 098 784 U ist eine Anordnung mit einem Planetengetriebe bekannt, wobei eine Ölpumpe von einem Sonnenrad angetrieben wird. Ein Ringrad treibt eine weitere Ölpumpe an.From the CN 203 098 784 U an arrangement with a planetary gear is known, wherein an oil pump is driven by a sun gear. A ring gear drives another oil pump.

Aus der JP 2007 263354 A ist eine Anordnung mit einem Planetengetriebe bekannt, wobei entweder Planetenräder und ein Ringrad oder ein Sonnenrad und die Planetenräder zum Antrieb von zwei Ölpumpen dienen.From the JP 2007 263354 A an arrangement with a planetary gear is known, either planetary gears and a ring gear or a sun gear and the planet gears are used to drive two oil pumps.

Aus der US 5 512 021 A ist eine Anordnung mit einem Planetengetriebe bekannt, wobei eine erste Pumpe über ein Ringrad angetrieben wird. Eine zweite Pumpe wird über ein Schwungrad vom Motor angetrieben.From the US 5 512 021 A an arrangement with a planetary gear is known, wherein a first pump is driven by a ring gear. A second pump is driven by a flywheel from the engine.

Der gattungsbildende Stand der Technik ist noch nicht optimal ausgebildet. Beim Antrieb der Nebenaggregate können Reibungsverluste auftreten, die zu einem erhöhten Kraftstoffverbrauch führen können.The generic state of the art is not yet optimally formed. When driving the ancillaries friction losses can occur, which can lead to increased fuel consumption.

Der Erfindung liegt daher die Aufgabe zugrunde, die gattungsbildende Nebenaggregatsantriebsvorrichtung derart auszugestalten und weiterzubilden, so dass der Kraftstoffverbrauch vermindert werden kann.The invention is therefore based on the object to design the generic ancillary drive device such and further, so that the fuel consumption can be reduced.

Diese der Erfindung zugrunde liegende Aufgabe wird nun durch eine Nebenaggregatsantriebsvorrichtung mit den Merkmalen des Patentanspruches 1 gelöst.This object of the invention is now achieved by an auxiliary drive device with the features of claim 1.

Die beiden Nebenaggregate sind als Ölpumpen ausgebildet. Hierdurch kann die mechanische Antriebsleistung zur Ölversorgung des Verbrennungsmotors reduziert werden. Mit Hilfe des Planetengetriebes werden die beiden Ölpumpen angetrieben. In Abhängigkeit von der Standübersetzung des Planetengetriebes und der Eingangsdrehzahl können beide Ölpumpen in Abhängigkeit voneinander drehzahlvariabel betrieben werden. Die beiden Ölpumpen können wahlweise mit unterschiedlichen Drehzahlen betrieben werden. Das Gesamtfördervolumen kann an den Bedarf angepasst werden. Durch eine entsprechende Wahl der geometrischen Fördervolumina kann eine Anpassung des Gesamtfördervolumenstroms und des Öldrucks an den aktuellen Bedarf des Verbrennungsmotors im Wesentlichen auch bei konstanter Eingangsdrehzahl des Antriebs, nämlich der entsprechenden Kurbelwelle vorgenommen werden. Der Antrieb ist insbesondere durch den Verbrennungsmotor des Kraftfahrzeuges gebildet. Die zur Ölversorgung benötigte Antriebsleistung ist bedarfsgerecht reduzierbar. Die Ölpumpen sind in einem wirkunsgradoptimierten Bereich betreibbar. Dadurch ist die Reibleistung verringerbar.The two ancillaries are designed as oil pumps. As a result, the mechanical drive power to the oil supply of the internal combustion engine can be reduced. With the help of the planetary gearbox, the two oil pumps are driven. Depending on the state ratio of the planetary gear and the input speed both oil pumps can be operated variable in number depending on each other. The two oil pumps can optionally be operated at different speeds. The total delivery volume can be adapted to the needs. By an appropriate choice of geometrical delivery volumes, an adjustment of the total delivery volume flow and the oil pressure to the current needs of the internal combustion engine can be made substantially at constant input speed of the drive, namely the corresponding crankshaft. The drive is formed in particular by the internal combustion engine of the motor vehicle. The drive power required for oil supply can be reduced as needed. The oil pumps can be operated in an efficiency-optimized range. As a result, the friction loss can be reduced.

Es erfolgt die Drehzahlvariation der beiden Ölpumpen über ein Steuerventil. Die Drehzahlvariation wird über das Steuerventil eingestellt. Die beiden Ölpumpen sind mittels des Steuerventils regelbar oder steuerbar. In einer ersten Stellung des Steuerventils fördert die zweite Ölpumpe und die erste Ölpumpe steht. In einer zweiten Stellung des Steuerventils steht die zweite Ölpumpe und die erste Ölpumpe fördert. Wenn die erste Ölpumpe steht, dreht die zweite Ölpumpe mit maximal möglicher Drehzahl. Wenn die zweite Ölpumpe steht, dreht die erste Ölpumpe mit maximal möglicher Drehzahl. Hierdurch lassen sich unterschiedliche Öldruckstufen realisieren.There is the speed variation of the two oil pumps via a control valve. The speed variation is set via the control valve. The two oil pumps can be controlled or controlled by means of the control valve. In a first position of the control valve promotes the second oil pump and the first oil pump is. In a second position of the control valve is the second oil pump and the first oil pump delivers. When the first oil pump is stopped, the second oil pump rotates at the maximum possible speed. When the second oil pump is stopped, the first oil pump rotates at the maximum possible speed. As a result, different oil pressure levels can be realized.

In der ersten Stellung sperrt das Steuerventil den Durchfluss durch die erste Ölpumpe. Das Steuerventil sperrt in der ersten Stellung insbesondere den Durchfluss durch eine der ersten Ölpumpe zugeordnet Druckleitung. Der Durchfluss durch eine der zweiten Ölpumpe zugordnet Druckleitung und der Durchfluss durch eine der zweiten Ölpumpe zugeordneten Saugleitung ist in der ersten Stellung freigegeben.In the first position, the control valve blocks the flow through the first oil pump. The control valve locks in the first position, in particular the flow through one of the first oil pump associated pressure line. The flow through a second oil pump zugeordnet pressure line and the flow through a second oil pump associated with the suction line is released in the first position.

In der zweiten Stellung ermöglicht das Steuerventil den Durchfluss durch die erste Ölpumpe. Das Steuerventil öffnet in der zweiten Stellung insbesondere den Durchfluss durch die der ersten Ölpumpe zugeordnet Druckleitung. Der Durchfluss durch die der zweiten Ölpumpe zugordnet Druckleitung und/oder der Durchfluss durch die der zweiten Ölpumpe zugeordneten Saugleitung ist in der zweiten Stellung gesperrt. Dadurch, dass die Saugleitung gesperrt ist, ist verhindert, dass Öl aus der Pumpe in den Ölsumpf zurückläuft. Durch das in der zweiten Ölpumpe gehaltene Öl ist die zweite Ölpumpe blockiert.In the second position, the control valve allows the flow through the first oil pump. The control valve opens in the second position in particular the flow through the first oil pump associated pressure line. The flow through the second oil pump zugordnet pressure line and / or the flow through the second oil pump associated with the suction line is locked in the second position. The fact that the suction line is locked, prevents oil from the pump runs back into the oil sump. Due to the oil held in the second oil pump, the second oil pump is blocked.

Das Planetengetriebe wird vorzugsweise über das Hohlrad angetrieben. Das Hohlrad ist antriebstechnisch mit der Kurbelwelle gekoppelt. Die erste Ölpumpe ist vorzugsweise drehfest mit dem Sonnenrad des Planetengetriebes verbunden. Die zweite Ölpumpe ist drehfest mit dem Planetenträger verbunden. Die zweite Ölpumpe dient als Bremse. Wird der Planetenträger mittels der zweiten Ölpumpe festgehalten, so dreht sich das Sonnenrad mit maximaler Drehzahl. Die erste Ölpumpe wird mit maximaler Drehzahl angetrieben. Wenn das Steuerventil in der zweiten Stellung angeordnet ist, sind die Saugleitung und die Druckleitung der Bremse verschlossen, die zweite Ölpumpe dreht sich nicht. Wird der Stellkolben zur Endlage der ersten Stellung bewegt, werden die Saugleitung und die Druckleitung der Bremse freigegeben und die Druckleitung der ersten Ölpumpe wird geschlossen. Die zweite Ölpumpe bzw. die Bremse beginnt zu drehen und die erste Ölpumpe wird langsamer. Ist der Stellkolben in der Endlage der ersten Stellung angelangt, steht die erste Ölpumpe komplett und nur die zweite Ölpumpe dreht und fördert.The planetary gear is preferably driven via the ring gear. The ring gear is drivingly coupled to the crankshaft. The first oil pump is preferably non-rotatably connected to the sun gear of the planetary gear. The second oil pump is rotatably connected to the planet carrier. The second oil pump serves as a brake. If the planet carrier is held by means of the second oil pump, then the sun gear rotates at maximum speed. The first oil pump is driven at maximum speed. When the control valve is located in the second position, the suction line and the brake pressure line are closed, the second oil pump does not rotate. If the actuating piston is moved to the end position of the first position, the suction line and the pressure line of the brake are released and the pressure line of the first oil pump is closed. The second oil pump or brake starts to rotate and the first oil pump slows down. When the actuating piston has reached the end position of the first position, the first oil pump is complete and only the second oil pump rotates and delivers.

Das Steuerventil ist insbesondere druckbetätigt, wobei der am Ausgang der beiden Ölpumpen anliegende Öldruck auf das Steuerventil über eine Steuerleitung zurückgeführt ist. Den Ausgang der Ölpumpen bilden dabei entsprechende Druckleitungen. Das Steuerventil ist gegen diesen Öldruck federbelastet. Wenn die Kraft aufgrund des Öldrucks kleiner als die Federkraft ist, dann ist das Steuerventil in der ersten Stellung angeordnet, wobei die erste Ölpumpe steht und die zweite Ölpumpe fördert. Wenn die Kraft aufgrund des Öldrucks größer als die Federkraft ist, dann ist das Steuerventil in der zweiten Stellung angeordnet, wobei die zweite Ölpumpe steht und die erste Ölpumpe fördert.The control valve is in particular pressure-actuated, wherein the voltage applied to the outlet of the two oil pumps oil pressure is returned to the control valve via a control line. The output of the oil pumps form corresponding pressure lines. The control valve is spring loaded against this oil pressure. If the force due to the oil pressure is less than the spring force, then the control valve is arranged in the first position, wherein the first oil pump is stationary and the second oil pump delivers. If the force due to the oil pressure is greater than the spring force, then the control valve is disposed in the second position, wherein the second oil pump is and promotes the first oil pump.

Die erste Ölpumpe ist in bevorzugter Ausgestaltung mit einem Sonnenrad gekoppelt und die zweite Ölpumpe ist mit einem Planetenträger gekoppelt. Der Antrieb ist mit einem Hohlrad gekoppelt. Der Antrieb ist durch eine Kurbelwelle des Kraftfahrzeugs gebildet. Die Kurbelwelle kann über ein Zwischenrad mit dem Hohlrad gekoppelt sein.The first oil pump is coupled in a preferred embodiment with a sun gear and the second oil pump is coupled to a planet carrier. The drive is coupled to a ring gear. The drive is formed by a crankshaft of the motor vehicle. The crankshaft may be coupled via an intermediate gear with the ring gear.

In einer Ausgestaltung ist eine der Ölpumpen mit einer Unterdruckpumpe gekoppelt. Die mit der Unterdruckpumpe gekoppelte Ölpumpe und die Unterdruckpumpe sind durch eine Tandempumpe gebildet. Dies hat den Vorteil, dass insbesondere im niedrigen Drehzahlbereich des Antriebs Unterdruck zur Verfügung gestellt werden kann. Im oberen Drehzahlbereich kann die nicht mit der Unterdruckpumpe gekoppelte Ölpumpe den wesentlichen Förderanteil übernehmen und insbesondere alleine betrieben werden. Weitere Vorteile bestehen gegenüber einer mittels eines separaten elektrischen Antriebs angetriebenen Unterdruckpumpe darin, dass die Ausgestaltung als Tandempumpe günstiger als der elektrische Antrieb ist, und die Leistungsaufnahme geringer als beim Einsatz einer konventionellen Unterdruckpumpe ist.In one embodiment, one of the oil pumps is coupled to a vacuum pump. The coupled with the vacuum pump oil pump and the vacuum pump are formed by a tandem pump. This has the advantage that, in particular in the low speed range of the drive negative pressure can be provided. At the top Speed range, the not coupled with the vacuum pump oil pump can take over the significant delivery share and in particular operated alone. Further advantages over a vacuum pump driven by a separate electric drive are that the design as a tandem pump is cheaper than the electric drive, and the power consumption is lower than when using a conventional vacuum pump.

Insbesondere kann die erste Ölpumpe mit der Unterdruckpumpe gekoppelt sein. Die mit der Unterdruckpumpe gekoppelte Ölpumpe ist funktional wirksam mit dem Sonnenrad gekoppelt. Die mit der Unterdruckpumpe gekoppelte Ölpumpe ist funktional wirksam mittels des Sonnenrads antreibbar. Die Unterdruckpumpe läuft mit der Drehzahl des Sonnenrads um, da die mit der Unterdruckpumpe gekoppelte Ölpumpe funktional wirksam mittels des Sonnenrads antreibbar ist und die Antriebe dieser Ölpumpe und der Unterdruckpumpe gekoppelt sind. Bei niedrigen Drehzahlen der Kurbelwelle steht der Planetenträger und die Unterdruckpumpe und die erste Ölpumpe fördern mit der entsprechenden maximalen Pumpendrehzahl in Abhängigkeit der jeweiligen Kurbelwellendrehzahl. Mit steigender Motordrehzahl sinkt die Drehzahl des Sonnenrads und es steigt die Drehzahl des Planetenträgers. Bei höheren Antriebsdrehzahlen wird die Pumpendrehzahl der ersten Ölpumpe und der Unterdruckpumpe reduziert und der Planetenträger treibt mit zunehmender Drehzahl die zweite Ölpumpe an. Die mit der Unterdruckpumpe gekoppelte, erste Ölpumpe und die Unterdruckpumpe weisen somit eine mit steigender Drehzahl des Antriebs sinkende Pumpendrehzahl auf. Im oberen Drehzahlbereich kann die mit der Unterdruckpumpe gekoppelte, erste Ölpumpe stehen oder nur mit geringer Drehzahl betrieben werden. Die Unterdruckpumpe wird mit der gleichen Drehzahl, wie die gekoppelte Ölpumpe angetrieben oder mittels einer Übersetzung mit einer proportionalen Drehzahl. Die Dauerlauffähigkeit der Unterdruckpumpe ist hierdurch erhöht.In particular, the first oil pump may be coupled to the vacuum pump. The oil pump coupled to the vacuum pump is operatively coupled to the sun gear. The coupled with the vacuum pump oil pump is functionally effective driven by the sun gear. The vacuum pump runs at the speed of the sun gear, since the oil pump coupled to the vacuum pump is functionally effective driven by means of the sun gear and the drives of this oil pump and the vacuum pump are coupled. At low speeds of the crankshaft is the planet carrier and the vacuum pump and the first oil pump promote with the corresponding maximum pump speed as a function of the respective crankshaft speed. As the engine speed increases, the speed of the sun gear decreases and the speed of the planet carrier increases. At higher drive speeds, the pump speed of the first oil pump and the vacuum pump is reduced and the planet carrier drives the second oil pump with increasing speed. The coupled with the vacuum pump, the first oil pump and the vacuum pump thus have a sinking with increasing speed of the drive pump speed. In the upper speed range, coupled with the vacuum pump, first oil pump can be stopped or operated only at low speed. The vacuum pump is driven at the same speed as the coupled oil pump or by means of a ratio with a proportional speed. The Dauerlauffähigkeit the vacuum pump is thereby increased.

Es gibt nun eine Vielzahl von Möglichkeiten, die erfindungsgemäße Nebenaggregatsantriebsvorrichtung auszugestalten und weiterzubilden. Hierfür darf zunächst auf die dem Patentanspruch 1 nachgeordneten Patentansprüche verwiesen werden. Im Folgenden wird nun eine bevorzugte Ausgestaltung der Erfindung anhand der Zeichnung und der dazugehörigen Beschreibung näher erläutert. In der Zeichnung zeigt:

Fig. 1
in einer stark schematischen Darstellung eine Nebenaggregatsantriebsvorrichtung mit einem Planetengetriebe und zwei Nebenaggregaten in Form einer ersten Ölpumpe und einer zweiten Ölpumpe,
Fig. 2
in einer schematischen Detaildarstellung ein Teil eines Ölkreislaufes mit den beiden Ölpumpen und einem Steuerventil, wobei der Durchfluss durch die zweite Ölpumpe gesperrt ist,
Fig. 3
in einer schematischen Detaildarstellung das Teil des Hydraulikkreislaufes aus Fig. 2, wobei der Durchfluss durch die erste Ölpumpe gesperrt ist,
Fig. 4
in einer schematischen Darstellung eine weitere Nebenaggregatsantriebsvorrichtung mit einem Planetengetriebe, zwei Ölpumpen und einer Unterdruckpumpe, und
Fig. 5
in einem schematischen Diagramm ein Fördervolumen aufgetragen über einer Motordrehzahl.
There are now a variety of ways to design and further develop the accessory drive device according to the invention. For this purpose, reference may first be made to the claims subordinate to claim 1. In the following, a preferred embodiment of the invention will now be explained in more detail with reference to the drawing and the associated description. In the drawing shows:
Fig. 1
in a highly schematic representation of an accessory drive device with a planetary gear and two ancillaries in the form of a first oil pump and a second oil pump,
Fig. 2
in a schematic detail of a part of an oil circuit with the two oil pumps and a control valve, wherein the flow is blocked by the second oil pump,
Fig. 3
in a schematic detail of the part of the hydraulic circuit Fig. 2 wherein the flow through the first oil pump is blocked,
Fig. 4
in a schematic representation of another accessory drive device with a planetary gear, two oil pumps and a vacuum pump, and
Fig. 5
in a schematic diagram, a delivery volume plotted against an engine speed.

In Fig. 1 ist eine Nebenaggregatsantriebsvorrichtung 1 für ein Kraftfahrzeug dargestellt. Die Nebenaggregatsantriebsvorrichtung 1 weist ein Planetengetriebe 2 auf. Ferner sind zwei Nebenaggregate 3, 4 vorgesehen. Die beiden Nebenaggregate 3, 4 sind mittels eines Antriebs (nicht näher dargestellt) über das Planetengetriebe 2 antreibbar. Der Antrieb ist insbesondere als Verbrennungsmotor des Kraftfahrzeuges ausgebildet. Mittels des Verbrennungsmotors wird eine Kurbelwelle 5 mit einem Drehmoment M angetrieben. Die Kurbelwelle 5 ist in einem Gehäuse 6 gelagert.In Fig. 1 an accessory drive device 1 for a motor vehicle is shown. The accessory drive device 1 has a planetary gear 2. Furthermore, two ancillaries 3, 4 are provided. The two auxiliary units 3, 4 are by means of a drive (not shown in detail) via the planetary gear 2 drivable. The drive is designed in particular as an internal combustion engine of the motor vehicle. By means of the internal combustion engine, a crankshaft 5 is driven with a torque M. The crankshaft 5 is mounted in a housing 6.

Das Planetengetriebe 2 weist ein Hohlrad 7, einen Planetenträger 8 mit mehreren Planetenrädern (nicht näher dargestellt) und ein Sonnenrad 9 auf. Die Planetenräder sind an dem Planetenträger 8 drehbar gelagert. Die Planetenräder stehen nun zum einen im kämmenden Eingriff mit der Innenverzahnung des Hohlrads 7 und zum anderen im kämmenden Eingriff mit der Außenverzahnung des Sonnenrades 9.The planetary gear 2 has a ring gear 7, a planet carrier 8 with a plurality of planetary gears (not shown in detail) and a sun gear 9. The planet gears are rotatably mounted on the planet carrier 8. The planet gears are now on the one hand in meshing engagement with the internal toothing of the ring gear 7 and on the other in meshing engagement with the external toothing of the sun gear. 9

In bevorzugter Ausgestaltung ist die Kurbelwelle 5 drehfest mit dem Hohlrad 7 verbunden. Die Kurbelwelle 5 treibt das Hohlrad 7 an. Das Hohlrad 7 bildet das Antriebsglied (nicht näher bezeichnet) des Planetengetriebes 2. Das erste Nebenaggregat 3 ist über eine Welle 10 mit dem Sonnenrad 9 drehfest verbunden. Konzentrisch zu der Welle 10 ist eine Hohlwelle 11 angeordnet, wobei die Hohlwelle 11 das zweite Nebenaggregat 4 mit dem Planetenträger 8 drehfest verbindet. Der Planetenträger 8 treibt das zweite Nebenaggregat 4 an.In a preferred embodiment, the crankshaft 5 is rotatably connected to the ring gear 7. The crankshaft 5 drives the ring gear 7. The ring gear 7 forms the drive member (unspecified) of the planetary gear 2. The first auxiliary unit 3 is rotatably connected via a shaft 10 with the sun gear 9. Concentric with the shaft 10, a hollow shaft 11 is arranged, wherein the hollow shaft 11 rotatably connects the second auxiliary unit 4 with the planet carrier 8. The planet carrier 8 drives the second auxiliary unit 4.

Die beiden Nebenaggregate 3, 4 sind als Ölpumpen 12, 13 ausgebildet. Das erste Nebenaggregat 3 ist durch eine erste Ölpumpe 12 und das zweite Nebenaggregat 4 ist durch eine zweite Ölpumpe 13 gebildet.The two ancillaries 3, 4 are designed as oil pumps 12, 13. The first auxiliary unit 3 is formed by a first oil pump 12 and the second auxiliary unit 4 is formed by a second oil pump 13.

Dies hat den Vorteil, dass die mechanische Antriebsleistung zur Förderung des Öls reduziert werden kann. Das Fördervolumen kann an den Bedarf des Verbrennungsmotors durch die Drehzahlvariabilität des Planetengetriebes 2 angepasst werden. Mit Hilfe des Planetengetriebes 2 werden die beiden Ölpumpen 12, 13 angetrieben. In Abhängigkeit von der Standübersetzung des Planetengetriebes 2 und der Eingangsdrehzahl der Kurbelwelle 5 können beide Ölpumpen 12, 13 in Abhängigkeit voneinander drehzahlvariabel betrieben werden.This has the advantage that the mechanical drive power for conveying the oil can be reduced. The delivery volume can be adapted to the needs of the internal combustion engine by the speed variability of the planetary gear 2. With the help of the planetary gear 2, the two oil pumps 12, 13 are driven. Depending on the state ratio of the planetary gear 2 and the input speed of the crankshaft 5, both oil pumps 12, 13 are operated variable in number depending on each other.

Wenn die erste Ölpumpe 12 steht, dreht die zweite Ölpumpe 13 mit maximal möglicher Drehzahl. Wenn die erste Ölpumpe 12 mit maximaler Drehzahl dreht, steht die zweite Ölpumpe 13. Durch eine entsprechende Wahl der geometrischen Fördervolumina kann eine Anpassung des Gesamtfördervolumenstroms an den aktuellen Ölbedarf, unabhängig von der Eingangsdrehzahl der Kurbelwelle 5 vorgenommen werden.When the first oil pump 12 is stopped, the second oil pump 13 rotates at the maximum possible speed. When the first oil pump 12 rotates at maximum speed, is the second oil pump 13. By an appropriate choice of geometric delivery volumes, an adjustment of the total delivery volume flow to the current oil demand, regardless of the input speed of the crankshaft 5 are made.

Die beiden Ölpumpen 12, 13 können baugleich ausgebildet sein. In alternativer Ausgestaltung sind die Ölpumpen 12, 13 unterschiedlich ausgebildet. Die Ölpumpe 12 und/oder die Ölpumpe 13 können beispielsweise als Zahnradpumpen oder als Flügelzellenpumpen ausgebildet sein.The two oil pumps 12, 13 may be of identical construction. In an alternative embodiment, the oil pumps 12, 13 are formed differently. The oil pump 12 and / or the oil pump 13 may be formed, for example, as gear pumps or as vane pumps.

Die beiden Ölpumpen 12, 13 weisen jeweils einen Rotor auf, wobei der Rotor mit der entsprechenden Welle 10 beziehungsweise der Hohlwelle 11 verbunden ist. Die beiden Ölpumpen 12, 13 fördern Öl aus einem gemeinsamen Ölsumpf 14. Das Öl wird dabei aus dem Ölsumpf 14 über die beiden Ölpumpen 12, 13 zu dem Verbrennungsmotor 15 gefördert. Jeder der Ölpumpen 12, 13 ist dabei eine Saugleitung 16, 18 und eine Druckleitung 17, 19 zugeordnet. Der Ölpumpe 12 ist eine Saugleitung 16 und eine Druckleitung 17 zugeordnet. Der Ölpumpe 13 ist eine Saugleitung 18 und eine Druckleitung 19 zugeordnet.The two oil pumps 12, 13 each have a rotor, wherein the rotor with the corresponding shaft 10 and the hollow shaft 11 is connected. The two oil pumps 12, 13 promote oil from a common oil sump 14. The oil is thereby conveyed from the oil sump 14 via the two oil pumps 12, 13 to the internal combustion engine 15. Each of the oil pumps 12, 13 is a suction line 16, 18 and a pressure line 17, 19 assigned. The oil pump 12 is associated with a suction line 16 and a pressure line 17. The oil pump 13 is associated with a suction line 18 and a pressure line 19.

Wie in Fig. 2 und 3 dargestellt ist, weist die Nebenaggregatsantriebsvorrichtung 1 ferner ein Steuerventil 20 auf. Das Steuerventil 20 weist mehrere nicht näher bezeichnete Anschlüsse auf. Mittels des Steuerventils 20 ist ein erster Druckleitungsabschnitt 17a mit einem zweiten Druckleitungsabschnitt 17b der Druckleitung 17 verbindbar beziehungsweise diese beiden Druckleitungsabschnitte 17a, 17b sind mittels des Steuerventils 20 voneinander trennbar.As in FIGS. 2 and 3 is shown, the accessory drive device 1 further comprises a control valve 20. The control valve 20 has a plurality of unspecified ports. A first pressure line section 17a can be connected to a second pressure line section 17b of the pressure line 17 by means of the control valve 20, or these two pressure line sections 17a, 17b can be separated from one another by means of the control valve 20.

Die Druckleitung 17 der ersten Ölpumpe 12 ist mittels des Steuerventils 20 sperrbar und öffenbar.The pressure line 17 of the first oil pump 12 can be blocked and opened by means of the control valve 20.

Mittels des Steuerventils 20 ist ferner die Druckleitung 19 der zweiten Ölpumpe 13 sperrbar und öffenbar. Die Druckleitung 19 weist zwei Druckleitungsabschnitte 19a und 19b auf, wobei die beiden Druckleitungsabschnitte 19a, 19b mittels des Steuerventils 20 verbindbar und trennbar sind. Der Druckleitungsabschnitt 19a ist mit einem Eingang des Steuerventils 20 und der Druckleitungsabschnitt 19b ist mit einem Ausgang des Steuerventils 20 verbunden.By means of the control valve 20 is also the pressure line 19 of the second oil pump 13 can be locked and opened. The pressure line 19 has two pressure line sections 19a and 19b, wherein the two pressure line sections 19a, 19b are connectable and separable by means of the control valve 20. The pressure line section 19 a is connected to an input of the control valve 20 and the pressure line section 19 b is connected to an output of the control valve 20.

Ferner ist mittels des Steuerventils 20 die Saugleitung 18 sperrbar und öffenbar. Die Saugleitung 18 weist zwei Saugleitungsabschnitte 18a, 18b auf, wobei die beiden Saugleitungsabschnitte 18a, 18b mittels des Steuerventils 20 verbindbar und voneinander trennbar sind.Further, by means of the control valve 20, the suction line 18 can be locked and opened. The suction line 18 has two Saugleitungsabschnitte 18a, 18b, wherein the two Saugleitungsabschnitte 18a, 18b connected by means of the control valve 20 and are separable from each other.

In der in Fig. 2 dargestellten Stellung des Steuerventils 20 sind die Druckleitung 18 und die Saugleitung 19 der zweiten Ölpumpe 13 gesperrt. Da die Druckleitung 19 und die Saugleitung 18 gesperrt sind, steht die zweite Ölpumpe 13. In dieser zweiten Stellung des Steuerventils 20 ist die Druckleitung 17 der ersten Ölpumpe 12 geöffnet. Die erste Ölpumpe 12 läuft mit maximaler Drehzahl und maximalen Fördervolumen.In the in Fig. 2 illustrated position of the control valve 20, the pressure line 18 and the suction line 19 of the second oil pump 13 are locked. Since the pressure line 19 and the suction line 18 are locked, is the second oil pump 13. In this second position of the control valve 20, the pressure line 17 of the first oil pump 12 is opened. The first oil pump 12 runs at maximum speed and maximum delivery volume.

In der in Fig. 3 dargestellten ersten Stellung des Steuerventils 20 sind sowohl die Saugleitung 18 als auch die Druckleitung 19 der zweiten Ölpumpe 13 mittels des Steuerventils 20 geöffnet. Die Druckleitung 17 der ersten Ölpumpe 12 ist mittels des Steuerventils 20 gesperrt. Hierdurch ist die erste Ölpumpe 12 gebremst und die zweite Ölpumpe 13 dreht und fördert.In the in Fig. 3 shown first position of the control valve 20, both the suction line 18 and the pressure line 19 of the second oil pump 13 are opened by means of the control valve 20. The pressure line 17 of the first oil pump 12 is blocked by means of the control valve 20. As a result, the first oil pump 12 is braked and the second oil pump 13 rotates and delivers.

Wenn das Steuerventil 20 von der zweiten Stellung (Fig. 2) in die erste Stellung (Fig. 3) bewegt wird, werden die Saugleitung 18 und die Druckleitung 19 der vorher als Bremse arbeitenden, zweiten Ölpumpe 13 freigegeben und die Druckleitung 17 der ersten Ölpumpe 12 wird verschlossen. Die zweite Ölpumpe 13 beginnt zu fördern, wobei die erste Ölpumpe 12 langsamer dreht.When the control valve 20 from the second position ( Fig. 2 ) in the first position ( Fig. 3 ), the suction line 18 and the pressure line 19 of the previously working as a brake, second oil pump 13 are released and the pressure line 17 of the first oil pump 12 is closed. The second oil pump 13 starts to deliver, with the first oil pump 12 rotating more slowly.

Ist das Steuerventil 20 in der in Fig. 3 dargestellten Endlage angelangt, steht die erste Ölpumpe 12 und nur die zweite Ölpumpe 13 dreht sich.Is the control valve 20 in the in Fig. 3 arrived reached end position, the first oil pump 12 and only the second oil pump 13 is rotating.

Das Steuerventil 20 ist druckbetätigt, wobei der am Ausgang bzw. in den Druckleitungsabschnitten 17b, 19b der beiden Ölpumpen 12, 13 anliegende Öldruck auf das Steuerventil 20 über eine Steuerleitung 21 zurückgeführt ist. Das Steuerventil 20 ist federbelastet, wobei, wenn die Kraft aufgrund des Öldrucks kleiner als die Federkraft ist, das Steuerventil 20 in der ersten Stellung (Fig. 3) angeordnet ist. In der in Fig. 2 dargestellten zweiten Stellung liegt ein hoher Öldruck an der Steuerleitung 21 an, so dass die Feder komprimiert ist. Wenn die Kraft aufgrund des Öldrucks größer als die Federkraft ist, ist das Steuerventil 20 in der zweiten Stellung (Fig. 2) angeordnet. Hierdurch ergibt sich die Regelung in Abhängigkeit von dem Öldruck. In der in Fig. 3 dargestellten Grundstellung oder ersten Stellung liegt ein niedriger Öldruck 21 an, wobei die Federkraft ausreichend ist, den Stellkolben in die erste Stellung zu verschieben.The control valve 20 is pressure-actuated, the oil pressure applied at the outlet or in the pressure line sections 17b, 19b of the two oil pumps 12, 13 being fed back to the control valve 20 via a control line 21. The control valve 20 is spring-loaded, and when the force due to the oil pressure is less than the spring force, the control valve 20 in the first position ( Fig. 3 ) is arranged. In the in Fig. 2 shown second position is a high oil pressure to the control line 21, so that the spring is compressed. When the force due to the oil pressure is greater than the spring force, the control valve 20 in the second position ( Fig. 2 ) arranged. This results in the control depending on the oil pressure. In the in Fig. 3 illustrated basic position or first position is a low oil pressure 21, wherein the spring force is sufficient to move the actuator piston in the first position.

Aufgrund der Übersetzung des Planetengetriebes 2 können sich so unterschiedliche Förderniveaus der Ölpumpen 12, 13 einstellen. Es sind so zwei Druckniveaus erzielbar. Die zur Ölversorgung benötigte Antriebsleistung ist bedarfsgerecht reduzierbar, ohne dass die Kurbelwellendrehzahl verändert wird. Hierdurch kann der zur Ölversorgung nötige Kraftstoffverbrauch vermindert werden.Due to the translation of the planetary gear 2 so different delivery levels of the oil pumps 12, 13 can be adjusted. There are two levels of pressure achievable. The drive power required for the oil supply can be reduced as needed without changing the crankshaft speed. As a result, the fuel consumption necessary for oil supply can be reduced.

Es ist möglich, die Drehrichtung einer der beiden Ölpumpen 12, 13 oder beider Ölpumpen 12, 13 umzukehren, um die entsprechende Ölpumpe 12, 13 zum Absaugen des Öls aus dem Verbrennungsmotor zu nutzen.It is possible to reverse the direction of rotation of one of the two oil pumps 12, 13 or both oil pumps 12, 13 to use the corresponding oil pump 12, 13 for sucking the oil from the internal combustion engine.

In Fig. 3 ist eine Nebenaggregatsantriebsvorrichtung 22 dargestellt. Die Nebenaggregatsantriebsvorrichtung 22 ist ähnlich wie die Nebenaggregatsantriebsvorrichtung 22 aufgebaut, wobei nun für im Wesentlichen funktional gleiche Teile gleiche Bezugszeichen verwendet werden.In Fig. 3 an accessory drive device 22 is shown. The accessory drive device 22 is constructed similar to the accessory drive device 22, with like reference numerals now being used for parts that are substantially functionally identical.

Die Nebenaggregatsantriebsvorrichtung 22 weist ebenfalls ein Planetengetriebe 2 und zwei Nebenaggregate 3, 4 in Form von Ölpumpen 12, 13 auf. Das Planetengetriebe 2 weist ein Hohlrad 7, einen Planetenträger 8 sowie ein Sonnenrad 9 auf. Das Hohlrad 5 ist funktional wirksam über die Kurbelwelle 5 antreibbar. Die Kurbelwelle 5 ist dabei über einen Modulantrieb 23 mit dem Hohlrad 7 gekoppelt. Der Modulantrieb 23 besteht im Wesentlichen aus einem drehfest an der Kurbelwelle 5 angeordneten Zahnrad 24, einem Zwischenrad 25 sowie einem weiteren Zahnrad 26, wobei das Zahnrad 26 insbesondere drehfest an einer Hohlwelle 27 angeordnet ist. Über die Hohlwelle 27 wird das Hohlrad 7 angetrieben. Das Sonnenrad 9 treibt über eine erste Pumpenwelle 28 die erste Ölpumpe 12 an. Der Planetenträger 8 treibt über eine zweite Pumpenwelle 29 die zweite Ölpumpe 13 an.The ancillary drive device 22 also has a planetary gear 2 and two ancillaries 3, 4 in the form of oil pumps 12, 13. The planetary gear 2 has a ring gear 7, a planet carrier 8 and a sun gear 9. The ring gear 5 is functionally effective via the crankshaft 5 driven. The crankshaft 5 is coupled via a module drive 23 with the ring gear 7. The module drive 23 consists essentially of a non-rotatably mounted on the crankshaft 5 gear 24, an intermediate 25 and a further gear 26, wherein the gear 26 in particular rotatably on a hollow shaft 27 is arranged. About the hollow shaft 27, the ring gear 7 is driven. The sun gear 9 drives the first oil pump 12 via a first pump shaft 28. The planet carrier 8 drives the second oil pump 13 via a second pump shaft 29.

In der hier dargestellten bevorzugten Ausgestaltung ist nun eine der Ölpumpen 12, 13, nämlich insbesondere die erste Ölpumpe 12 funktional wirksam antriebstechnisch mit einer Unterdruckpumpe 30 gekoppelt. Die Unterdruckpumpe 30 ist über eine Zwischenwelle 31 funktional wirksam mit der Pumpenwelle 28 gekoppelt. Die Unterdruckpumpe 30 kann beispielsweise zur Versorgung eines Bremskraftverstärkers oder dgl. dienen. Die mit der Unterdruckpumpe 30 gekoppelte, erste Ölpumpe 12 und die Unterdruckpumpe 30 sind funktional wirksam mittels des Sonnenrads 9 antreibbar.In the preferred embodiment shown here, one of the oil pumps 12, 13, namely, in particular, the first oil pump 12 is operatively coupled in terms of drive technology to a vacuum pump 30. The vacuum pump 30 is operatively coupled to the pump shaft 28 via an intermediate shaft 31. The vacuum pump 30 may serve, for example, to supply a brake booster or the like. The coupled to the vacuum pump 30, first oil pump 12 and the vacuum pump 30 are functionally effective by means of the sun gear 9 drivable.

Die erste Ölpumpe 11 und die Unterdruckpumpe 30 werden mit der gleichen Pumpendrehzahl betrieben. Die Pumpendrehzahl der zweiten Ölpumpe 13 unterscheidet sich insbesondere von der Drehzahl ersten Ölpumpe 12 und somit auch von Drehzahl der Unterdruckpumpe 30. Die mit der Unterdruckpumpe 30 gekoppelte, erste Ölpumpe 12 und die Unterdruckpumpe 30 weisen eine mit steigender Drehzahl des Antriebs sinkende Pumpendrehzahl auf. Die zweite Ölpumpe 13 weist eine mit steigender Drehzahl des Antriebs steigende Pumpendrehzahl auf. Im Bereich der maximalen Drehzahl des Antriebs ist es denkbar, dass die erste Ölpumpe 12 und die Unterdruckpumpe im Wesentlichen stehen und die zweite Ölpumpe 13 alleine betrieben wird. Im niedrigen Drehzahlbereich wird hauptsächlich mittels der ersten Ölpumpe 12 gefördert und dabei auch die Unterdruckpumpe 30 angetrieben, da insbesondere im niedrigen Drehzahlbereich Pumpenleistung der Unterdruckpumpe 30 erforderlich ist. Es wird vorzugsweise die Nebenaggregatsantriebsvorrichtung 22 derart betrieben, dass die Unterdruckpumpe 30 bei hohen Drehzahlen nicht oder nur mit geringer Drehzahl umläuft. Dies erhöht die Dauerlauffähigkeit der Unterdruckpumpe 30 und dient der Verbrauchsminderung.The first oil pump 11 and the vacuum pump 30 are operated at the same pump speed. The pump speed of the second oil pump 13 differs in particular from the speed of the first oil pump 12 and thus also the speed of the vacuum pump 30. The coupled to the vacuum pump 30, the first oil pump 12 and the vacuum pump 30 have a sinking with increasing speed of the drive pump speed. The second oil pump 13 has an increasing pump speed with increasing speed of the drive. In the range of the maximum speed of the drive, it is conceivable that the first oil pump 12 and the vacuum pump are substantially and the second oil pump 13 is operated alone. In the low speed range is promoted mainly by means of the first oil pump 12 and thereby the vacuum pump 30 is driven, as in particular in the low speed range pumping capacity of the vacuum pump 30 is required. Preferably, the accessory drive device 22 is operated such that the vacuum pump 30 does not or only at low speed rotates at high speeds. This increases the endurance capability of the vacuum pump 30 and serves the consumption reduction.

In Fig. 5 sind unterschiedliche Fördervolumen über der Motordrehzahl, d.h. der Drehzahl der Kurbelwelle 5 aufgetragen. Es ist ein maximales Fördervolumen 32, ein minimales Fördervolumen 33 sowie eine Bedarfskennlinie 34 eines Verbrennungsmotors dargestellt. Das Gesamtfördervolumen V̇Ges ergibt sich aus der Summe der Fördervolumina der ersten Ölpumpe 12 V̇Pumpe1 und der zweiten Ölpumpe 13 V̇Pumpe2. Das minimale Fördervolumen 32 stellt sich ein, wenn der Planetenträger 8 steht, d.h. wenn die Drehzahl nPlanetenträger gleich null Umdrehungen pro Minute ist und somit die erste Ölpumpe 12 mit maximaler Drehzahl läuft. Das minimale Fördervolumen 33 ergibt sich, wenn das Sonnenrad steht, d.h. wenn im Wesentlichen nur die zweite Ölpumpe 13 angetrieben wird und die Drehzahl des Sonnenrades nSonne gleich null Umdrehungen pro Minute ist.In Fig. 5 are different delivery volume above the engine speed, ie the speed of the crankshaft 5 applied. It is a maximum delivery volume 32, a minimum delivery volume 33 and a demand curve 34 of an internal combustion engine shown. The total delivery volume V̇ Ges results from the sum of the delivery volumes of the first oil pump 12 V̇ Pumpe1 and the second oil pump 13 V̇ Pumpe2 . The minimum delivery volume 32 adjusts itself when the planet carrier 8 is stationary, ie when the rotational speed n planet carrier is equal to zero revolutions per minute and thus the first oil pump 12 is running at maximum rotational speed. The minimum delivery volume 33 results when the sun gear is stationary, ie when substantially only the second oil pump 13 is driven and the speed of the sun gear n sun is equal to zero revolutions per minute.

Gut ersichtlich ist, dass die Bedarfskennlinie 34 zwischen dem maximalen Fördervolumen 32 und dem minimalen Fördervolumen 33 für alle dargestellten Motordrehzahlen liegt. Bei hohen Motordrehzahlen liegt dabei die Bedarfskennlinie 34 näher an dem minimalen Fördervolumen 33, wobei so durch Anpassung des Gesamtfördervolumens V̇Ges an die Bedarfskennlinie 34 die erste Ölpumpe 12 nur wenig oder gar nicht fördern muss, um den Bedarf zu decken.It can be clearly seen that the demand curve 34 lies between the maximum delivery volume 32 and the minimum delivery volume 33 for all illustrated engine speeds. At high engine speeds while the demand curve 34 is closer to the minimum delivery volume 33, so by adjusting the total delivery volume V̇ Ges to the demand curve 34, the first oil pump 12 has little or no need to promote to meet the demand.

BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS

11
NebenaggregatsantriebsvorrichtungAccessory drive device
22
Planetengetriebeplanetary gear
33
Nebenaggregataccessory
44
Nebenaggregataccessory
55
Kurbelwellecrankshaft
66
Gehäusecasing
77
Hohlradring gear
88th
Planetenträgerplanet carrier
99
Sonnenradsun
1010
Wellewave
1111
Hohlwellehollow shaft
1212
Ölpumpeoil pump
1313
Ölpumpeoil pump
1414
Ölsumpfoil sump
1515
Verbrennungsmotorinternal combustion engine
1616
Saugleitungsuction
1717
Druckleitungpressure line
17a17a
DruckleitungsabschnittPressure line section
17b17b
DruckleitungsabschnittPressure line section
1818
Saugleitungsuction
18a18a
Saugleitungsabschnittsuction line
18b18b
Saugleitungsabschnittsuction line
1919
Druckleitungpressure line
19a19a
DruckleitungsabschnittPressure line section
19b19b
DruckleitungsabschnittPressure line section
2020
Steuerventilcontrol valve
2121
Steuerleitungcontrol line
2222
NebenaggregatsantriebsvorrichtungAccessory drive device
2323
Modulantriebmodule drive
2424
Zahnradgear
2525
Zwischenradidler
2626
Zahnradgear
2727
Hohlwellehollow shaft
2828
Pumpenwellepump shaft
2929
Pumpenwellepump shaft
3030
UnterdruckpumpeVacuum pump
3131
Zwischenwelleintermediate shaft
3232
maximales Fördervolumenmaximum delivery volume
3333
minimales Fördervolumenminimal delivery volume
3434
BedarfskennlinieDemand curve

Claims (9)

  1. An auxiliary unit drive device (1, 22) having a planetary gear (2), with two auxiliary units (3, 4) wherein the two auxiliary units (3, 4) can be driven by means of a drive via the planetary gear (2), wherein the two auxiliary units (3, 4) are designed as oil pumps (12, 13), characterized in that the two oil pumps (12, 13) are adjustable or controllable by means of a control valve (20), wherein the first oil pump (12) is stationary in a first position of the control valve (20) and the second oil pump delivers, wherein the first oil pump (12) delivers in a second position of the control valve (20) and the second oil pump (13) is stationary, wherein a total delivery value can be adapted to the needs.
  2. The auxiliary unit drive device according to Claim 1, characterized in that by means of the control valve (20) the pressure line (17, 19) and/or the suction line (18) of the first oil pump (12) or the second oil pump (13) can be closed and opened.
  3. The auxiliary unit drive device according to any one of the preceding claims, characterized in that the control valve (20) can be pressure-operated, wherein the oil pressure applied to the output of the two oil pumps (12, 13) is returned to the control valve (20) via a control line (21).
  4. The auxiliary unit drive device according to any one of the preceding claims, characterized in that the control valve (20) is spring-loaded, wherein if the force due to the oil pressure is less than the spring force, the control valve (20) is arranged in the first position, wherein, if the force due to the oil pressure is greater than the spring force, the control valve (20) is arranged in the second position.
  5. The auxiliary unit drive device according to any one of the preceding claims, characterized in that the first oil pump (12) is coupled with a sun wheel (9), the second oil pump (13) is coupled with a planetary carrier (8) and the drive is coupled with a hollow wheel (7).
  6. The auxiliary unit drive device according to any one of the preceding claims, characterized in that the drive is formed by a crank shaft (5) of a motor vehicle.
  7. The auxiliary unit drive device according to any one of the preceding claims, characterized in that one of the oil pumps (12) is coupled with a vacuum pump (30).
  8. The auxiliary unit drive device according to any one of the preceding claims, characterized in that the oil pump (12) coupled with the vacuum pump (30) and the vacuum pump (30) have a pump speed decreasing with increasing speed of the drive.
  9. The auxiliary unit drive device according to any one of the preceding claims, characterized in that the oil pump (12) coupled with the vacuum pump (30) can be functionally effectively driven by means of the sun wheel (9).
EP16719210.3A 2015-04-28 2016-04-27 Auxiliaries driving device Active EP3289191B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015005344.2A DE102015005344A1 (en) 2015-04-28 2015-04-28 Accessory drive device
PCT/EP2016/000664 WO2016173707A1 (en) 2015-04-28 2016-04-27 Auxiliary unit drive device

Publications (2)

Publication Number Publication Date
EP3289191A1 EP3289191A1 (en) 2018-03-07
EP3289191B1 true EP3289191B1 (en) 2019-10-02

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EP16719210.3A Active EP3289191B1 (en) 2015-04-28 2016-04-27 Auxiliaries driving device

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EP (1) EP3289191B1 (en)
DE (1) DE102015005344A1 (en)
WO (1) WO2016173707A1 (en)

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CN106813091A (en) * 2017-03-15 2017-06-09 合肥海鲨智能科技有限责任公司 A kind of planetary gear oil pump
DE102018101082B4 (en) 2018-01-18 2021-03-18 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Drive arrangement for driving at least three fluid pumps
DE102019203239A1 (en) * 2019-03-11 2020-09-17 Zf Friedrichshafen Ag Method for supplying consumers of an oil supply system for a vehicle transmission with oil

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DE3921715A1 (en) * 1989-07-01 1991-01-10 Porsche Ag DEVICE FOR DRIVING TWO OIL PUMPS ON A PISTON PISTON INTERNAL COMBUSTION ENGINE
DE4032590A1 (en) * 1990-10-13 1992-04-16 Porsche Ag PISTON PISTON ENGINE WITH TWO V-SHAPED CYLINDER ROWS
DE4200918C1 (en) 1992-01-16 1993-03-11 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
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EP3289191A1 (en) 2018-03-07
WO2016173707A1 (en) 2016-11-03

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