WO2017050402A1 - Système de fluide de travail pour un groupe motopropulseur de véhicule automobile - Google Patents

Système de fluide de travail pour un groupe motopropulseur de véhicule automobile Download PDF

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Publication number
WO2017050402A1
WO2017050402A1 PCT/EP2016/001136 EP2016001136W WO2017050402A1 WO 2017050402 A1 WO2017050402 A1 WO 2017050402A1 EP 2016001136 W EP2016001136 W EP 2016001136W WO 2017050402 A1 WO2017050402 A1 WO 2017050402A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
line
operating
electric motor
operating medium
Prior art date
Application number
PCT/EP2016/001136
Other languages
German (de)
English (en)
Inventor
Florian Holz
Thomas Krais
Markus Rossmeier
Original Assignee
Daimler Ag
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 Daimler Ag filed Critical Daimler Ag
Publication of WO2017050402A1 publication Critical patent/WO2017050402A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • F16H61/0025—Supply of control fluid; Pumps therefore
    • F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0435—Pressure control for supplying lubricant; Circuits or valves therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0441—Arrangements of pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves

Definitions

  • the invention relates to an operating system for a motor vehicle drive train.
  • a motor vehicle driveline comprising a dry sump pump arranged to provide a fluid pressure in a first fluid line, an auxiliary pump provided to provide fluid pressure in a second fluid line, and at least one electric motor provided for the dry sump pump and to drive the auxiliary pump at the same time, known.
  • the invention is in particular the object of providing a cost-effective and / or simple operating system for a motor vehicle drive train. It is achieved by an embodiment according to the invention according to claim 1. Further developments of the invention will become apparent from the dependent claims.
  • the invention is based on a resource system for a
  • a motor vehicle driveline having a dry sump pump arranged to provide an operating medium pressure in a first operating line, having an auxiliary pump arranged to provide an operating medium pressure in a second operating line, and having at least one electric motor provided thereon, the dry sump pump and the To drive auxiliary pump at the same time.
  • the resource system at least one
  • Has hydraulic section which is provided to automatically switch depressurized in a reversal of the direction of rotation of the electric motor, the second resource line.
  • a hydraulic section is provided to at a reversal of the direction of
  • Electric motor the second resource line to independently depressurize, can a constructionally simple design can be realized in mechanical and electrical terms.
  • By the dry sump pump and the additional pump are driven by an electric motor at the same time, can be dispensed with an additional electric motor. Overall, a cost effective and easy
  • Operating system can be realized for a motor vehicle powertrain.
  • the term "simultaneously driving” is to be understood as meaning that the dry sump pump and the auxiliary pump can only be driven together, in particular, it is not intended to decouple the auxiliary pump and / or the dry sump pump mechanically from the electric motor, for example by means of a clutch or
  • a "hydraulic section” is to be understood as meaning, in particular, a subsection of the operating system which is intended to assume a specific control and / or regulating function, as in this connection the independent pressureless switching of the second operating line.
  • the hydraulic section has a
  • Resource line which is intended to connect a departure and an input of the auxiliary pump with each other, and a in the operating line
  • the "input" and the "outlet” of the additional pump should be assigned in particular the positive direction of rotation of the electric motor, the assignment of "input”, "outlet” and “positive direction” is initially a pure name, which primarily serves a unique name If the electric motor is operated with the positive direction of rotation, the auxiliary pump sucks in operating medium via the input and discharges the operating medium via the outgoing air outlet Entrance from.
  • the hydraulic section preferably has a hydraulic rectifier for the dry sump pump, which has a control input connected to the auxiliary pump. This allows the different equipment pressures, which the
  • Rectifier can be used, whereby the dry sump pump in both
  • the rectifier can be structurally particularly simple design. By eliminating the need for electrical control costs can be kept low. In addition, a small space requirement can be achieved. Alternatively, another embodiment of the rectifier is conceivable. For example, the hydraulic
  • Rectifier also have four check valves, which can be dispensed with a control line between the auxiliary pump and the rectifier.
  • an electrically controllable rectifier is conceivable.
  • the resource system for supplying an automatic transmission with resources is provided.
  • the operating system which is provided to the supply of an automatic transmission with resources, a main pump, wherein the main pump is driven by a prime mover of the motor vehicle drive train and a main supply of the automatic transmission is used with resources.
  • the auxiliary pump can advantageously only be operated if one
  • Supply of the automatic transmission with resources through the main pump can not or can not be sufficient.
  • a motor vehicle driveline comprising a dry sump pump arranged to provide a fluid pressure in a first fluid line, an auxiliary pump provided to provide fluid pressure in a second fluid line, and at least one electric motor provided for the dry sump pump and driving the auxiliary pump at the same time, and having at least one hydraulic section having a service line, which is intended to connect an outlet and an inlet of the auxiliary pump with each other, and having a valve disposed in the operating medium solenoid valve.
  • FIG. 1 shows an operating system for a motor vehicle drive train, with a
  • Dry sump pump an additional pump and at least one
  • Hydraulic section which is intended to automatically depressurize the second operating medium line at a reversal of the direction of rotation of the electric motor
  • At least one hydraulic section having a service line, which is intended to connect an outlet and an input of a booster pump with each other, and the one in the operating line
  • solenoid valve which is provided for the depressurization of the operating medium line.
  • Figure 1 shows an embodiment of an operating system for a
  • the motor vehicle drive train not shown in detail comprises, for example, a drive machine and an automatic transmission connected to the drive machine.
  • the automatic transmission includes, for example, a gear set and gear shift elements for switching different gears or gears.
  • the drive train may have a clutch that is connected upstream of the automatic transmission. It is also conceivable that the drive train another
  • the operating system comprises at least one control circuit 22a, which is provided for driving, for example, the clutch and the transmission shift elements, and at least one lubrication and / or cooling circuit 23a, which is provided for example for lubricating and / or cooling the clutch and / or the gear set.
  • the resource system further includes a dry sump 24a, a dry sump pump 10a, a suction space 25a and an auxiliary pump 12a. Under the dry sump 24a is a collection area for equipment in particular from the lubrication and
  • the dry sump 24a is located in the space of the transmission gears.
  • the dry sump pump 0a serves the
  • the suction chamber 25a is used for storing the operating medium, which can be supplied to the control circuit 22a and the lubricating and / or cooling circuit 23a.
  • the suction space 25a is the gear space surrounding the electro-hydraulic transmission control block.
  • the intake chamber 25a may also be another subspace of the automatic transmission.
  • the resource is preferably an oil.
  • the operating system preferably comprises at least one control valve 26a, which is provided to derive at least one control pressure for the at least one control circuit 22a from an operating medium pressure. Furthermore, the operating system preferably has at least one control valve 27a, which is provided to derive from an operating medium pressure a lubricating and / or cooling pressure for the lubricating and / or cooling circuit 23a.
  • the operating medium pressure, from which the control pressure is derived is provided depending on the operating situation of the main pump, not shown, of the main pump and the auxiliary pump or only by the auxiliary pump 12a.
  • the fluid pressure from which the lubrication and / or cooling pressure is derived may be the control pressure, the fluid pressure provided by the booster pump 12a, and / or the main pump, or other fluid pressure.
  • a combination in which lubricating and / or cooling pressure is derived from the at least one control pressure 26a and the operating medium pressure provided by the dry sump pump 10a is also conceivable.
  • the operating system has a second operating line 13a, which for the supply of the control circuit 22a and the lubricating and / or cooling circuit 23a with resources and a first resource line 11a for the return of Operating means are provided from the dry sump 24a in the suction chamber 25a.
  • the resource line 1 1 a is connected to the dry sump pump 10a.
  • Resource pressure in the resource line 11a is provided by the dry sump pump 10a.
  • the operating medium line 13a is connected to the auxiliary pump 12a and to a main pump (not shown) driven by the engine
  • the resource line 11a leads in the illustrated embodiment in the suction chamber 25a. In principle, other embodiments are conceivable.
  • the operating system includes an electric motor 14a provided to drive the dry sump pump 10a and the auxiliary pump 12a simultaneously.
  • Electric motor 14a comprises an output shaft 28a, to which the dry sump pump 10a and the auxiliary pump 12a are connected.
  • the dry sump pump 10a and the auxiliary pump 12a are firmly connected to the output shaft 28a.
  • a unit which is intended to separate a mechanical connection between the output shaft 28a, the dry sump pump 10a and the auxiliary pump 12a, such as a clutch or a freewheel, is dispensed with. Basically, that can
  • the electric motor 14a is provided for reversing the direction of rotation.
  • Operating system comprises a hydraulic section 15a, which is provided to independently depressurize the second operating line 33a when the direction of rotation of the electric motor 14a reverses.
  • the dry sump pump 10 a and the auxiliary pump 12 a are arranged in the hydraulic section 15 a.
  • the two operating lines 11a, 13a directly adjoin the hydraulic section 15a.
  • the hydraulic section 15a comprises a suction line 29a for the dry sump pump 10a and a suction line 30a for the auxiliary pump 12a.
  • the suction lines 29a, 30a each have a suction filter 31a, 32a.
  • the auxiliary pump 12a includes a
  • Input 18a which is connected to the suction line 30a, and an outlet 17a.
  • the hydraulic section 15a has a service line 33a, which is connected to the outlet 17a of the auxiliary pump 12a. Does the electric motor 14a a positive
  • the auxiliary pump 12a sucks on the suction line 30a resources and provides their resource pressure at the outlet 17a ready. If the electric motor 14a has a negative direction of rotation, the auxiliary pump 12a sucks in operating means via the outlet 17a and discharges it via the inlet 18a.
  • the hydraulic section 15a has a service line 16a which is provided to connect the outlet 17a and the inlet 18a of the auxiliary pump 12a to one another. Furthermore, the hydraulic section 15a has a non-return valve 19a arranged in the operating line 16a, which is intended to open or close in dependence on a direction of rotation of the electric motor 14a.
  • Power line 16a connects the outlet 17a and the inlet 18a of the
  • the check valve 19a has an opening direction which corresponds to an increase in pressure at the inlet 18a. If the electric motor 14a is operated with the positive direction of rotation, the auxiliary pump 12a builds up a pressure at the outlet 17a. The check valve 19a is closed when the electric motor 14a is operated in the positive direction of rotation. The auxiliary pump 12a promotes resources from the
  • Booster pump 12a on a negative pressure at the outlet 17a.
  • the check valve 19a is opened, 34a is closed when the electric motor 14a with the negative
  • the auxiliary pump 12a conveys the operating medium via the operating line 16a from the outlet 17a to the inlet 18a.
  • Operating medium pressure in the operating line 33a, which is followed by the second operating line 13a, depends in particular on flow resistances
  • the hydraulic section 15a has a further non-return valve 34a, which prevents the operating medium from flowing back from the operating line 13a into the operating line 33a adjoining the outlet 17a.
  • Check valve 34a has a spring element 39a, which defines a minimum pressure which is necessary for opening the further check valve 34a. If the electric motor 14a operated with the negative direction of rotation, which is on the
  • Check valve 34 a applied operating medium pressure is less than the minimum pressure required to open the check valve 34 a.
  • the hydraulic section 15a has a hydraulic rectifier 20a.
  • the dry sump pump 10a has an inlet 35a and an outlet 36a.
  • the dry sump pump 10a sucks the operating medium via the inlet 35a and discharges the operating medium via the outlet 36a.
  • the electric motor 14a is operated in the negative rotational direction, the dry sump pump 10a sucks the operating medium via the outlet 36a and discharges the operating medium via the inlet 35a.
  • the rectifier 20a connects the input 35a of the dry sump pump 10a to the suction line 29a and the outlet 36a to the service line 1a when the electric motor 14a is operated in the positive direction of rotation. When the electric motor 14a is operated in the negative rotational direction, the rectifier 20a connects the outlet 36a of the dry sump pump 10a to the suction pipe 29a and the inlet 35a to the service pipe 11a.
  • the rectifier 20a includes a 4/2-way valve 37a.
  • the 4/2-way valve 37a comprises a first switching position, in which the input 35a is connected to the suction line 29a and the outlet 36a to the service line 1a, and a second
  • the 4/2-way valve 37a is pressure-controlled. It includes a control volume not shown in detail and a
  • Control volume counteracting spring element 39a If the control volume is acted upon by an operating medium pressure which is greater than a spring force provided by the spring element 39a, the 4/2-way valve 37a is switched to the first switching position. If the control volume 38a depressurized, the 4/2-way valve 37a is switched to the second switching position.
  • the rectifier 20a comprises a control input 21a, which is connected to the auxiliary pump 12a.
  • the hydraulic section 15a comprises a control line 40a, which connects the outlet 17a of the auxiliary pump 12a to the control input 21a of the rectifier 20a. If the electric motor 14a is operated with the positive direction of rotation, the rectifier 20a is switched into the first switching position by the operating medium pressure.
  • the dry sump pump 10a provides a resource pressure in the first resource line 11a.
  • the Booster pump 12a provides a fluid pressure in second fluid line 13a. If the electric motor 14a is operated with the negative direction of rotation, the further check valve 34a is closed and the rectifier 20a is switched to the second switching position. The dry sump pump 10a continues to provide
  • Embodiment has. The following descriptions are essentially limited to the differences between the exemplary embodiments, wherein reference can be made to the description of the embodiment of FIG. 1 with regard to components, features and functions that remain the same. To distinguish the embodiments, the letter a in the reference numerals of
  • Embodiment in Figure 1 replaced by the letter b in the reference numerals of the embodiment of Figure 2.
  • Figure 2 shows an operating system for a motor vehicle powertrain, with a dry sump pump 10b, which is intended to provide an operating medium pressure in a first resource line 1 1 b, with an auxiliary pump 12 b, which is intended to provide an operating medium pressure in a second operating line 13 b, and with an electric motor 14b provided for
  • the operating system comprises a hydraulic section 15b having a service line 6b provided to connect an outlet 17b and an inlet 18b of the auxiliary pump 12b.
  • the hydraulic section 15b has a solenoid valve 41b arranged in the operating line 16b. If the solenoid valve 41b is opened, the inlet 18b and the outlet 17b of the auxiliary pump 12b are hydraulically connected to each other via the operating medium line 16b.
  • the powertrain includes a control and regulating unit 42b, which is provided to control the electric motor 14b and the solenoid valve 41b.
  • Control unit 42b comprises at least one electronic control unit.
  • the control unit comprises a processor unit and a memory unit as well as a memory unit stored operating program.
  • the control and / or regulating unit 42b may comprise a plurality of interconnected control units, which are preferably provided to communicate with each other via a bus system, such as, in particular, a CAN bus system. Is the solenoid valve 41 b open, promotes the
  • Booster pump 12b the resource through the resource line 16b back to the input 18b.
  • the hydraulic section 15b has an outlet 17b of the
  • Booster pump connected to the operating line 33b, which is largely depressurized when the solenoid valve 41 b is open.
  • the hydraulic section 15b has analogous to that
  • a further check valve 34b which opens when the auxiliary pump 12b builds up a working fluid pressure.
  • a rectifier for the dry sump pump 10b and the reversal of the direction of rotation of the electric motor 14b can be omitted in this embodiment.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système de fluide de travail pour un groupe motopropulseur de véhicule automobile, comprenant une pompe à carter sec (10a) conçue pour établir une pression de fluide de travail dans une première conduite de fluide de travail (11a), une pompe auxiliaire (12a) conçue pour établir une pression de fluide de travail dans une deuxième conduite de fluide de travail (13a), au moins un moteur électrique (14a) conçu pour entraîner simultanément la pompe à carter sec (10a) et la pompe auxiliaire (12a), ainsi qu'au moins une section hydraulique (15a) conçue pour connecter la deuxième conduite de fluide de travail (13a) indépendamment sans pression en cas d'inversion du sens de rotation du moteur électrique (14a).
PCT/EP2016/001136 2015-09-22 2016-07-02 Système de fluide de travail pour un groupe motopropulseur de véhicule automobile WO2017050402A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015012345.9A DE102015012345B4 (de) 2015-09-22 2015-09-22 Betriebsmittelsystem für einen Kraftfahrzeugantriebsstrang
DE102015012345.9 2015-09-22

Publications (1)

Publication Number Publication Date
WO2017050402A1 true WO2017050402A1 (fr) 2017-03-30

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Application Number Title Priority Date Filing Date
PCT/EP2016/001136 WO2017050402A1 (fr) 2015-09-22 2016-07-02 Système de fluide de travail pour un groupe motopropulseur de véhicule automobile

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DE (1) DE102015012345B4 (fr)
WO (1) WO2017050402A1 (fr)

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NL2018732B1 (en) * 2017-04-18 2018-10-29 Punch Powertrain Nv a hydraulic system for a vehicle, a vehicle transmission, and method for operating a vehicle transmission
WO2018192989A1 (fr) * 2017-04-18 2018-10-25 Punch Powertrain N.V. Système hydraulique pour véhicule, transmission de véhicule et procédé de fonctionnement d'une transmission de véhicule
DE102017113057A1 (de) * 2017-06-14 2018-12-20 Schaeffler Technologies AG & Co. KG Integrierbares Kühlmittelfördermodul sowie Getriebe mit Kühlmittelfördermodul
DE102018002168A1 (de) 2018-03-16 2019-09-19 Daimler Ag Verfahren zum Betrieb eines automatischen Kraftfahrzeuggetriebes in einem Notlauf
DE102019204858A1 (de) * 2019-04-04 2020-10-08 Magna Pt B.V. & Co. Kg Hydraulisches System und Verfahren zur Ansteuerung desselben
DE102022100573B3 (de) * 2022-01-12 2023-05-17 Schaeffler Technologies AG & Co. KG Hydrauliksystem mit Hoch- und Trockensumpf
DE102022209441A1 (de) 2022-09-09 2024-03-14 Zf Friedrichshafen Ag Pumpensystem für einen elektrischen Achsantrieb

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EP1420185A2 (fr) * 2002-11-18 2004-05-19 ZF Sachs AG Transmission pour véhicule automobile comprenant une pompe d'alimentation d'un système d'embrayage en fluide sous pression
US20090321209A1 (en) * 2007-03-07 2009-12-31 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic arrangement for controlling a twin-clutch transmission of a motor vehicle
US20130206533A1 (en) * 2010-02-05 2013-08-15 Ricardo, Inc. Hydraulic control system for a dual clutch transmission

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DE10327406A1 (de) 2003-06-18 2005-02-03 Zf Friedrichshafen Ag Hydrauliksystem für ein Lastschaltgetriebe und Verfahren zum Betreiben des Hydraliksystems
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DE102012220742A1 (de) 2012-11-14 2014-05-15 Zf Friedrichshafen Ag Anordnung zum Antrieb von Ölpumpen
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EP1420185A2 (fr) * 2002-11-18 2004-05-19 ZF Sachs AG Transmission pour véhicule automobile comprenant une pompe d'alimentation d'un système d'embrayage en fluide sous pression
US20090321209A1 (en) * 2007-03-07 2009-12-31 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic arrangement for controlling a twin-clutch transmission of a motor vehicle
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Publication number Publication date
DE102015012345A1 (de) 2017-03-23
DE102015012345B4 (de) 2022-01-20

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