WO2004003399A1 - Systeme d'entrainement pour vehicules - Google Patents

Systeme d'entrainement pour vehicules Download PDF

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Publication number
WO2004003399A1
WO2004003399A1 PCT/EP2003/006430 EP0306430W WO2004003399A1 WO 2004003399 A1 WO2004003399 A1 WO 2004003399A1 EP 0306430 W EP0306430 W EP 0306430W WO 2004003399 A1 WO2004003399 A1 WO 2004003399A1
Authority
WO
WIPO (PCT)
Prior art keywords
arrangement
clutch
assembly
drive system
region
Prior art date
Application number
PCT/EP2003/006430
Other languages
German (de)
English (en)
Inventor
Christoph Kleuker
Markus Heiartz
Guido Schmitt
Original Assignee
Zf Sachs 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
Priority claimed from DE10232440.9A external-priority patent/DE10232440B4/de
Application filed by Zf Sachs Ag filed Critical Zf Sachs Ag
Priority to AU2003279773A priority Critical patent/AU2003279773A1/en
Publication of WO2004003399A1 publication Critical patent/WO2004003399A1/fr

Links

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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/087—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs

Definitions

  • the present invention relates to a drive system for a vehicle, comprising an electric machine with a stator assembly and a rotatable coupling for common rotation with a drive member rotor assembly and a torque transfer arrangement, preferably friction clutch, hydrodynamic torque converter, hydrodynamic coupling, torsional vibration damper or the like, by means of an optional engageable and disengageable clutch assembly for torque transmission to the drive member coupled input area.
  • Such drive systems which can be used, for example, in hybrid vehicles, enable substantially complete decoupling of the drive train from a drive unit, that is, for example, an internal combustion engine.
  • the rotational energy in the rotating system areas of the drive train when the vehicle is traveling can be used essentially completely for propulsion of the vehicle in a driving state in which the vehicle is to roll on a slightly sloping road, for example, while the drive unit uncoupled from the drive train is brought into an idling state or possibly even turned off.
  • a drive system for a vehicle comprising an electric machine having a stator arrangement and a rotor arrangement which can be coupled for common rotation with a drive element and a torque transmission arrangement, preferably a friction clutch, hydrodynamic torque converter, hydrodynamic clutch, torsional vibration damper or the like by means of an optionally engageable and disengageable clutch assembly for torque transmission to the drive member coupled input area, wherein the clutch assembly comprises a relative to the rotor assembly held substantially non-rotatably and by an energy storage on an abutment to be acted upon pressure plate, wherein the force storage is supported with respect to the rotor assembly and the abutment assembly is connected or connectable with the input region of the torque transmission arrangement ode r / and forms a part thereof, a clutch disc assembly which is connected to the drive member or connectable and is clamped with the clutch engaged between the pressure plate and the abutment assembly for torque transmission.
  • the rotor assembly of the electric machine is functionally and also component integrated into the clutch assembly, namely, by forming that system area on which the energy storage is supported or supported.
  • this essentially corresponds to the function of Clutch housing.
  • This coupling housing is completely eliminated in the structure according to the invention or is replaced by the rotor assembly, so that a very small size can be realized in the axial direction.
  • the pressure plate has a ring-like pressure plate body arranged on a first axial side of a carrier region of the rotor arrangement and that a plurality of the carrier region of the rotor arrangement pass through from the pressure plate body Abstützabitesen goes out, which acts on the substantially arranged on the second axial side of the carrier region of the rotor assembly stored energy storage.
  • the energy accumulator is supported by a plurality of support members on the support area.
  • stator arrangement is substantially ring-shaped and that an actuating arrangement for the energy store is positioned substantially in the space area surrounded by the stator arrangement.
  • This annular space can thus accommodate a generally also ring-shaped actuator mechanism, so that it is housed in a range that is otherwise unusable for other components of the drive system in general.
  • the actuating arrangement comprises an actuator piston which acts on the energy accumulator via a bearing arrangement and which is displaceable in an actuator cylinder fixed relative to the stator arrangement.
  • the actuator cylinder have a cylinder space defined at least in part by a region of a carrier region of the stator arrangement. This can for example also be realized in that the cylinder space is formed like a ring and a cylinder space radially inward limiting cylinder wall is at least partially formed by the support portion of the stator assembly.
  • the rotor assembly is not fixed, for example by screwing, coupled to the drive member, but is coupled as part of the clutch assembly only to the drive member when the clutch assembly is in an engaged state, it is proposed that the carrier area the rotor assembly is supported with respect to the carrier region of the stator assembly.
  • the input portion of the torque transmitting assembly may provide at least one friction surface for a friction clutch.
  • the input area comprises a primary side of a torsional vibration damper arrangement.
  • Fig. 1 is a partial longitudinal sectional view of a drive system according to a first embodiment
  • FIG. 2 shows the rotor arrangement provided in the drive system of FIG. 1 together with a pressure plate
  • Fig. 3 is an axial view of the rotor assembly of Fig. 2;
  • Fig. 4 is an axial view of the pressure plate of Fig. 2;
  • Fig. 5 is a view corresponding to FIG. 1 of an alternative ausgestaltet
  • FIG. 6 is a view corresponding to Figure 1 of the drive system according to the invention, which has a Torsionsschwingungsdämpferaniser.
  • FIG. 7 the system shown in Fig. 6 in conjunction with a
  • FIG. 8 shows a modification of the system shown in FIG.
  • an inventive drive system is generally designated by the reference numeral 10.
  • This drive system can generally be subdivided into three system areas.
  • a first system area is an electric machine 12 having a stator assembly, generally designated 14, and a rotor assembly, generally designated 16.
  • a second system area is a torque transmission arrangement, generally designated 18, which in the illustrated example is designed as a double clutch.
  • a so-called pulse start clutch 20 is provided, via which the dual clutch 18 for torque transmission to a drive shaft, not shown, for example, a crankshaft of an internal combustion engine, can be connected.
  • the torque transmission assembly 18, which, as already stated above, is designed here as a double clutch, is only symbolic of a variety of torque transmission arrangements, such.
  • Torque transmission assembly 18 is connected to a provided by an abutment plate 24 substantially output range of the pulse starting clutch 20.
  • the dual clutch or torque transmission assembly 18 then further includes two clutch portions 26, 28, each of which, in itself known manner, a pressure plate, a force accumulator or a Betreli whyskraftübertragungshebelan Aunt and a clutch disc comprises, which can be pressed by the pressure plate against the intermediate plate 22 to selectively transmit via one of the clutch discs torque on a transmission input shaft associated therewith or the like.
  • the electric machine 12 which can also be generally referred to as a crankshaft starter / generator, comprises in the region of the stator arrangement a stator interaction region 30 with a plurality of stator windings on a stator yoke formed by sheet metal plates or the like and a support region 32 which extends over a plate-like sealing flange 34, for example attached to an engine block.
  • a radially inner, approximately in the axial direction extending ring-like projection 36 of this support portion 32 of the stator assembly 14 overlaps in the direction of the axis of rotation A with a central cylindrical projection 38 of a support portion 40 of the rotor assembly 16.
  • the carrier region 40 of the rotor assembly 16 is supported with respect to the carrier region 32 of the stator assembly 14 in the radial direction and preferably in the axial direction.
  • the support portion 40 of the rotor assembly 16 carries a rotor interaction region 44 which may include a plurality of circumferentially successive permanent magnets on a yoke.
  • the rotor interaction region 44 may be firmly connected to the carrier region 40 by screwing, but may also be connected at least partially in the region of the yoke integral therewith.
  • the rotor assembly 16 thus forms with this abutment plate 24 is a structural unit.
  • FIG. 46 Between the radially inner region of the abutment plate 24 and the support portion 40 of the rotor assembly 16 is a generally designated 46 pressure plate.
  • the assembly of this pressure plate 46 with the rotor assembly 16 is illustrated in FIG. It can be seen that the pressure plate 46, which is shown once again in axial view in FIG. 4, has a ring-like pressure plate body 48 which is arranged on that side 50 of the carrier region 40 of the rotor assembly 16, that of the stator assembly 14 or also of the drive assembly turned away and thus the torque transmission assembly 18 and an axially subsequent gear facing is positioned. From the ring-like pressure plate body 48 are in the circumferential direction successively a plurality of ring-segment-like support projections 52 from.
  • a recess 54 is provided in the carrier region 40 of the rotor assembly 16, so that a support region 56 of these projections 52 is positioned on the other axial side 58 of the carrier region 40. It can still be seen in FIG. 4 that at several circumferential positions the pressure plate 46 can have radial fastening projections, in which, for example, by means of a leaf spring arrangement or the like the pressure plate 46 is coupled for common rotation with the abutment ring 24 and / or the carrier region 40 of the rotor assembly 16, wherein such serving as coupling members leaf springs can then also provide the release force for the pressure plate 46 at the same time.
  • a force accumulator 62 constructed in the manner of a diaphragm spring is likewise provided on the side 58 of the carrier region 40 of the rotor arrangement 16 facing the drive unit or the stator arrangement 14.
  • the energy accumulator 62 acts on the support regions 46 of the projections 52.
  • the energy accumulator 62 is held on the carrier region 40 by a plurality of spacer bolts or the like.
  • a radially inner region 68 of the energy storage device 62 is acted upon by a hereinafter described in more detail operating mechanism 70 for performing engagement or disengaging operations via a bearing assembly 72.
  • This actuating mechanism 70 comprises an annular piston 74, which dips into an annular cylinder chamber 76.
  • This annular cylinder space 76 is at a Ring cylinder member 78 is provided and limited by wall portions 80, 82 radially outward or radially inward. These two wall regions 80, 82 may be integrally formed on a component, but may of course also be formed on different components and then joined together.
  • the annular cylinder element 78 is provided on the carrier region 32 of the stator assembly 14 or by screwing and surrounds the axial projection 36 with the least possible space, so that sufficient space is provided radially outside of the actuating mechanism 70 to provide mounting screws for the support portion 32 of the stator assembly 14 to be able to.
  • the piston 74 guided in a sealed manner with respect to the walls 80, 82 is displaced in the axial direction so that it axially displaces the force accumulator 62 in its radially inner region 86 via the bearing 72 in a corresponding manner.
  • the radially outer region 64 then moves in the opposite axial direction and allows the pressure plate 46 to move away from the abutment ring 24.
  • a generally designated 84 clutch disk assembly of the pulse starting clutch 20 has a ring-shaped and composed for example of a plurality of components lining carrier 86 which carries friction linings 88 in its radially outer region. These friction linings 88 are clamped with coupled pulse starting clutch 20 between the pressure plate 46 and the abutment ring 24, so that a generated by Reibkraftschi uss torque transmission coupling. Radially inside, the friction lining carrier 86 is clamped between a spacer 92 and a clamping sleeve 94, which are firmly connected to the drive shaft by fastening screws 90 or the like, the clamping force being generated by means of a clamping screw 96. In order to obtain a positive coupling in addition to a frictional engagement, the connection between the friction lining carrier 86 and the spacer 92 can be effected by a serration or the like.
  • a very small axial drive system 10 is obtained. It is also important that the actuation can take place from the side of the drive assembly, ie no actuators have to be guided through transmission input shafts or the like, for example. It is only necessary, from the motor side, so for example through the plate 34 through, supply and discharge lines for the pressurized fluid ready.
  • this clutch assembly 20 it is possible, for example, for starting an internal combustion engine first by the electric machine 12 with disengaged clutch assembly 20, for example, the engaged clutch held double clutch 18 driven gear to rotate until a sufficient speed or sufficient rotational energy is present. It is then spontaneously engaged, the clutch assembly 20, and the mass moment of inertia of the already rotating mass, the drive unit is driven to rotate. When the vehicle is moving, rotating energy can be stored in this rotating system area with the drive unit disconnected, which can either contribute to the longer propulsion of the vehicle, or can also be used in this phase to restart the briefly disconnected drive unit.
  • a modified embodiment is shown in which, especially in the region of the actuator mechanism, a change is present.
  • the cylinder element 78 which in turn in turn defines an annular working chamber 76 for receiving the annular piston 74, is constructed so that the wall 82 bounding the working space 76 radially inwardly by the axial projection 36 of the support portion 32 of the stator assembly 14 is.
  • the radially outwardly delimiting wall 80 is in turn provided by a separate component with respect to which in the region of the working chamber 76 on the one hand and radially outwardly by a bellows-like arrangement on the other hand the Ring piston 74 is sealed. It therefore eliminates here in the embodiment according to FIG. 1 additional radially inwardly bounding wall, so that, which is also clearly visible in Fig. 5, the actuator mechanism 70 has a smaller radial size.
  • FIGS. 6 and 7 Another drive system 10 according to the invention is shown in FIGS. 6 and 7. It can be seen in FIG. 6 that essential system areas, namely the electric machine 12 and the pulse starting clutch 20 with the associated components, such as actuating mechanism 70, are formed as described in FIGS. 1 to 5. Reference is therefore made to the preceding explanations.
  • a torsional vibration damper arrangement generally designated 100, is now provided as a torque transmission arrangement.
  • a primary side 102 thereof is connected radially on the outside of the rotor assembly 16 and thus forms a structural unit with this.
  • the primary side 102 essentially has two respective cover disk elements 106, 108 providing components 107, 109, wherein the cover plate member 106 providing component 107 is extended radially outwardly and is connected to one of the rotor assembly 16 and on the other the abutment for the pulse starting clutch 20th or provides a corresponding abutment friction surface. Between these two cover disk elements 106, 108 providing components 107, 109 engages the secondary side 104 to be assigned central disk element 110 a.
  • a damper spring arrangement 118 In a working space 116 filled, for example, with a viscous medium, there is a damper spring arrangement 118, the individual springs of which cooperate with the cover disk elements 106, 108 on the one hand and the central disk element 110 on the other hand for transmitting torque while enabling relative rotation of the primary side 102 with respect to the secondary side 104.
  • a radially inner cylindrical projection 112 of the cover plate element 106 providing component 107 is mounted, for example with the interposition of a bearing bushing on a corresponding axial extension 114 of the central disk element 110.
  • This projection 114 further forms an axial toothing 120, which with an input shaft 122 of the recognizable in Fig. 7 automatic transmission 124 in Rotary drive intervention is or can be brought.
  • a mass portion 126 is coupled to the center disk member 112, so that by adjusting the mass ratio between the primary side 102 and the secondary side 104 and provided by the damper spring assembly 118 spring force, the vibration damping behavior of the Torsionsschwingungsdämpferan Aunt 110 can be influenced. Furthermore, it can be provided that the central disk element 110 drives a plurality of planet wheels 128, which are rotatably supported on the primary side 102, for rotation in order to generate an additional damping contribution here.
  • FIGS. 6 and 7 therefore show a system in which an input shaft 122 of a stepped automatic transmission 24 is connected to the output side of the pulse starting clutch 20 in a torque-transmitting manner without the interposition of a hydrodynamic torque converter using the torsional vibration damper arrangement 100.
  • a very space-saving design of a drive system is made possible in which the functionality of the pulse starting clutch 20 explained at the outset nevertheless remains intact.
  • FIG. 6 A modification of the system shown in FIG. 6 is shown in FIG.
  • the central disk element 110 is attributable to the primary side 102 of the torsional vibration damper arrangement, while the two components 107, 109 providing the cover disk elements 106, 108, which in turn can be fixed radially externally by welding or the like, can be attributed to the secondary side 104 are.
  • the central disk element 110 is now with its cylindrical projection 114, for example, with an intermediate arrangement of a plain bearing bush or the like, mounted on a cylindrical projection 112 of the cover plate member 106 providing component 107, which now carries the internal teeth 120 for coupling the transmission input shaft.
  • the connection to the pulse starting clutch 20 is provided by a, for example, annular disk-like coupling element 130.
  • the torsional vibration damper assembly shown there can be connected in the region of its secondary side to a conventional friction clutch or a pressure plate assembly therefor, for example, the mass portion 126 shown in FIG Flywheel or abutment assembly could be used for a pressure plate and insofar, for example, could take over the function of the intermediate plate 22 described above with reference to Figures 1 to 5.
  • the energy accumulator 62 used in the pulse starting clutch 20 should have a very steep characteristic, so that comparatively high engagement forces can be generated which ensure that a completely rigid coupling occurs in the region even when torque fluctuations occur Clutch is present that However, low holding forces are required even after a comparatively small Ausgurweg by correspondingly high drop in the counterforce provided by the power storage. This relieves the pressure between the actuator mechanism 70 and this energy storage 62 effective bearing 72, since this in the state in which the pulse starting clutch 20 is kept disengaged, only lower forces must be transmitted.

Abstract

L'invention concerne un système d'entraînement pour un véhicule, ce système comprenant les éléments suivants : un moteur électrique (12) doté d'un ensemble stator (14) et d'un ensemble rotor (16) s'accouplant à l'organe d'entraînement pour une rotation synchronisée ; un ensemble de transmission de couple (18), de préférence un embrayage à friction, un convertisseur de couple hydrodynamique, un coupleur hydrodynamique, un amortisseur de vibrations torsionnelles ou un organe analogue, cet ensemble de transmission comportant une zone d'entrée (22) pouvant être couplée à l'organe d'entraînement au moyen d'un dispositif d'embrayage (20) sélectivement embrayable ou débrayable pour transmettre le couple. Le dispositif d'embrayage (20) comporte les éléments suivants: une plaque de pression (46), sensiblement maintenue de façon à ne pas tourner relativement à l'ensemble rotor (16) et soumise à l'action d'un accumulateur d'énergie (62) pour se déplacer contre un ensemble butée (24). L'accumulateur d'énergie (62) est en appui relativement à l'ensemble rotor (16) et l'ensemble butée (24) est ou peut être relié à la zone d'entrée (22) de l'ensemble de transmission de couple et/ou constitue une partie de celui-ci. Le dispositif d'embrayage comprend également un ensemble disques d'embrayage (84), qui est ou peut être couplé à l'organe de transmission et qui, lorsque le dispositif d'embrayage (20) est embrayé, est serré entre la plaque de pression (46) et l'ensemble butée (24) pour transmettre le couple.
PCT/EP2003/006430 2002-06-28 2003-06-18 Systeme d'entrainement pour vehicules WO2004003399A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003279773A AU2003279773A1 (en) 2002-06-28 2003-06-18 Propulsion system for a vehicle

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10229143.8 2002-06-28
DE10229143 2002-06-28
DE10232440.9A DE10232440B4 (de) 2002-06-28 2002-07-17 Antriebssystem für ein Fahrzeug
DE10232440.9 2002-07-17

Publications (1)

Publication Number Publication Date
WO2004003399A1 true WO2004003399A1 (fr) 2004-01-08

Family

ID=30001490

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/006430 WO2004003399A1 (fr) 2002-06-28 2003-06-18 Systeme d'entrainement pour vehicules

Country Status (2)

Country Link
AU (1) AU2003279773A1 (fr)
WO (1) WO2004003399A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102574454A (zh) * 2009-11-19 2012-07-11 爱信艾达株式会社 车辆用驱动装置
WO2018001662A1 (fr) * 2016-06-30 2018-01-04 Zf Friedrichshafen Ag Dispositif de transmission de couple
WO2018145690A1 (fr) * 2017-02-10 2018-08-16 Schaeffler Technologies AG & Co. KG Dispositif d'actionnement conçu pour un embrayage et procédé de production
FR3086714A1 (fr) * 2018-10-01 2020-04-03 Valeo Embrayages Dispositif de transmission pour vehicule hybride

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999022955A1 (fr) * 1997-11-04 1999-05-14 Magneti Marelli S.P.A Systeme de propulsion hybride pour un vehicule moteur
FR2804185A1 (fr) * 2000-01-25 2001-07-27 Valeo Embrayage a friction comportant un plateau de reaction portant un rotor d'une machine electrique tournante, notamment pour vehicule automobile
FR2808572A1 (fr) * 2000-05-02 2001-11-09 Peugeot Citroen Automobiles Sa Dispositif d'actionnement d'un embrayage de vehicule automobile

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999022955A1 (fr) * 1997-11-04 1999-05-14 Magneti Marelli S.P.A Systeme de propulsion hybride pour un vehicule moteur
FR2804185A1 (fr) * 2000-01-25 2001-07-27 Valeo Embrayage a friction comportant un plateau de reaction portant un rotor d'une machine electrique tournante, notamment pour vehicule automobile
FR2808572A1 (fr) * 2000-05-02 2001-11-09 Peugeot Citroen Automobiles Sa Dispositif d'actionnement d'un embrayage de vehicule automobile

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102574454A (zh) * 2009-11-19 2012-07-11 爱信艾达株式会社 车辆用驱动装置
WO2018001662A1 (fr) * 2016-06-30 2018-01-04 Zf Friedrichshafen Ag Dispositif de transmission de couple
US10995818B2 (en) 2016-06-30 2021-05-04 Zf Friedrichshafen Ag Torque-transmission device
WO2018145690A1 (fr) * 2017-02-10 2018-08-16 Schaeffler Technologies AG & Co. KG Dispositif d'actionnement conçu pour un embrayage et procédé de production
CN110268179A (zh) * 2017-02-10 2019-09-20 舍弗勒技术股份两合公司 用于离合器的操纵装置和制造方法
CN110268179B (zh) * 2017-02-10 2021-10-08 舍弗勒技术股份两合公司 用于离合器的操纵装置和制造方法
FR3086714A1 (fr) * 2018-10-01 2020-04-03 Valeo Embrayages Dispositif de transmission pour vehicule hybride

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