WO2016173707A1 - Dispositif d'entraînement d'organes auxiliaires - Google Patents

Dispositif d'entraînement d'organes auxiliaires Download PDF

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Publication number
WO2016173707A1
WO2016173707A1 PCT/EP2016/000664 EP2016000664W WO2016173707A1 WO 2016173707 A1 WO2016173707 A1 WO 2016173707A1 EP 2016000664 W EP2016000664 W EP 2016000664W WO 2016173707 A1 WO2016173707 A1 WO 2016173707A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
oil pump
pump
control valve
drive device
Prior art date
Application number
PCT/EP2016/000664
Other languages
German (de)
English (en)
Inventor
Timm BRÖCKER
Tom MACHT
Original Assignee
Volkswagen Aktiengesellschaft
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volkswagen Aktiengesellschaft filed Critical Volkswagen Aktiengesellschaft
Priority to EP16719210.3A priority Critical patent/EP3289191B1/fr
Publication of WO2016173707A1 publication Critical patent/WO2016173707A1/fr

Links

Classifications

    • 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.
  • CONFIRMATION COPY 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.
  • 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 zucapsul 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 zuabel 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. In the upper speed range, the oil pump, which is not coupled to the vacuum pump, can take over the essential delivery component and, in particular, can be 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 Dauerlaufrich the vacuum pump is thereby increased.
  • FIG. 1 in a highly schematic representation of a
  • FIG. 2 is 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 is a schematic detail of the part of the hydraulic circuit of FIG. 2, wherein the flow through the first oil pump is blocked
  • Fig. 4 is a schematic representation of another
  • Fig. 5 is a schematic diagram of a delivery volume plotted on a
  • an accessory drive device 1 for a motor vehicle.
  • 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 in one meshing engagement with the internal toothing of the ring gear 7 and 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 a suction pipe 18 and a pressure pipe
  • the accessory drive device 1 further includes 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 is blocked by the control valve 20 and apparently.
  • the pressure line 19 of the second oil pump 13 is also lockable and apparently.
  • 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 19a is connected to an input of the control valve
  • the suction line 18 can be locked and apparently.
  • 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 by means of Control valve 20 locked.
  • 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 smaller than the spring force, the control valve 20 is disposed in the first position (FIG. 3). In the second position shown in Fig. 2 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 is disposed in the second position (FIG. 2). This results in the control depending on the oil pressure.
  • In the illustrated in Fig. 3 basic position or first position is a low oil pressure 21, wherein the spring force is sufficient to move the actuating piston in the first position.
  • an accessory drive device 22 is shown.
  • the accessory drive device 22 is similar to the Ancillary drive device 22 constructed, now the same reference numerals are used for substantially functionally identical parts.
  • 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 1 1 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 with 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 different delivery volume over the engine speed, ie the speed of the crankshaft 5 are plotted. 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 Vp umpe2 .
  • the minimum flow volume 32 adjusts itself when the planet carrier is 8, ie when the rotation speed n P i anete nxx equal to zero revolutions per minute and thus the first oil pump 12 is running at maximum speed.
  • the minimum delivery volume 33 results when the sun gear is, that is, when substantially only the second oil pump 13 is driven and the speed of the sun gear n Son ne 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 promotion to meet the need.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Details Of Gearings (AREA)
  • Rotary Pumps (AREA)
  • Structure Of Transmissions (AREA)

Abstract

La présente invention concerne un dispositif d'entraînement d'organes auxiliaires (1) comportant une boîte de vitesses à trains épicycloïdaux (2) et deux organes auxiliaires (3, 4), les deux organes auxiliaires (3, 4) pouvant être entraînés au moyen d'un entraînement par l'intermédiaire de la boîte de vitesses à trains épicycloïdaux (2). La consommation de carburant peut ainsi être réduite du fait que les deux organes auxiliaires (3, 4) sont conçus comme pompes à huile (12, 13).
PCT/EP2016/000664 2015-04-28 2016-04-27 Dispositif d'entraînement d'organes auxiliaires WO2016173707A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16719210.3A EP3289191B1 (fr) 2015-04-28 2016-04-27 Dispositif de propulsion des auxiliaires

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015005344.2 2015-04-28
DE102015005344.2A DE102015005344A1 (de) 2015-04-28 2015-04-28 Nebenaggregatsantriebsvorrichtung

Publications (1)

Publication Number Publication Date
WO2016173707A1 true WO2016173707A1 (fr) 2016-11-03

Family

ID=55860781

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/000664 WO2016173707A1 (fr) 2015-04-28 2016-04-27 Dispositif d'entraînement d'organes auxiliaires

Country Status (3)

Country Link
EP (1) EP3289191B1 (fr)
DE (1) DE102015005344A1 (fr)
WO (1) WO2016173707A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018101082A1 (de) 2018-01-18 2019-07-18 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Antriebsanordnung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106813091A (zh) * 2017-03-15 2017-06-09 合肥海鲨智能科技有限责任公司 一种行星式齿轮油泵
DE102019203239A1 (de) * 2019-03-11 2020-09-17 Zf Friedrichshafen Ag Verfahren zur Versorgung von Verbrauchern eines Ölversorgungsystems für ein Fahrzeug-Getriebe mit Öl

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GB833273A (en) * 1956-10-18 1960-04-21 Ford Motor Co Constant speed drives
DE3814750A1 (de) * 1988-04-30 1989-02-02 Mtu Friedrichshafen Gmbh Einrichtung zum antrieb einer schmiermittelpumpe einer brennkraftmaschine
DE4200918C1 (fr) 1992-01-16 1993-03-11 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
US5512021A (en) * 1994-02-10 1996-04-30 Shash; Joseph L. Variable ratio transmission
JP2007263354A (ja) * 2006-03-30 2007-10-11 Univance Corp 自動車用変速装置
CN203098784U (zh) * 2013-02-04 2013-07-31 纳庆 汽车变速装置

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DE3622335C2 (de) * 1985-07-31 1995-11-23 Volkswagen Ag Antriebseinrichtung für Nebenaggregate einer Brennkraftmaschine
DE3921715A1 (de) * 1989-07-01 1991-01-10 Porsche Ag Vorrichtung zum antrieb zweier oelpumpen an einer hubkolben-brennkraftmaschine
DE4032590A1 (de) * 1990-10-13 1992-04-16 Porsche Ag Hubkolbenmotor mit zwei v-foermig angeordneten zylinderreihen
JPH10103074A (ja) * 1996-10-02 1998-04-21 Tochigi Fuji Ind Co Ltd 補機駆動装置
DE10329215A1 (de) * 2003-06-28 2005-01-13 Zf Friedrichshafen Ag Antriebsvorrichtung für eine Getriebe-Ölpumpe und Verfahren zum Betreiben derselben
JP2005207357A (ja) * 2004-01-26 2005-08-04 Honda Motor Co Ltd エンジンの可変容量流体ポンプ
DE102006030917B4 (de) * 2006-06-26 2018-08-16 Pierburg Gmbh Ölpumpen- und Vakuumpumpenmodul
DE102013219945B4 (de) * 2013-10-01 2022-03-24 Volkswagen Ag Anordnung für einen Verbrennungsmotor eines Kraftfahrzeuges umfassend eine erste Pumpe, eine Ausgleichswelle und eine zweite Pumpe sowie Verfahren zur Montage einer Ausgleichswelle in einem Gehäuse

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB833273A (en) * 1956-10-18 1960-04-21 Ford Motor Co Constant speed drives
DE3814750A1 (de) * 1988-04-30 1989-02-02 Mtu Friedrichshafen Gmbh Einrichtung zum antrieb einer schmiermittelpumpe einer brennkraftmaschine
DE4200918C1 (fr) 1992-01-16 1993-03-11 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
US5512021A (en) * 1994-02-10 1996-04-30 Shash; Joseph L. Variable ratio transmission
JP2007263354A (ja) * 2006-03-30 2007-10-11 Univance Corp 自動車用変速装置
CN203098784U (zh) * 2013-02-04 2013-07-31 纳庆 汽车变速装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018101082A1 (de) 2018-01-18 2019-07-18 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Antriebsanordnung
DE102018101082B4 (de) * 2018-01-18 2021-03-18 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Antriebsanordnung zum Antrieb von wenigstens drei Fluidpumpen

Also Published As

Publication number Publication date
EP3289191A1 (fr) 2018-03-07
DE102015005344A1 (de) 2016-11-03
EP3289191B1 (fr) 2019-10-02

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