WO2019120382A1 - Unité de transmission de couple, unité d'entraînement électrique et transmission - Google Patents

Unité de transmission de couple, unité d'entraînement électrique et transmission Download PDF

Info

Publication number
WO2019120382A1
WO2019120382A1 PCT/DE2018/101023 DE2018101023W WO2019120382A1 WO 2019120382 A1 WO2019120382 A1 WO 2019120382A1 DE 2018101023 W DE2018101023 W DE 2018101023W WO 2019120382 A1 WO2019120382 A1 WO 2019120382A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
torque
transmission unit
axially
connecting part
Prior art date
Application number
PCT/DE2018/101023
Other languages
German (de)
English (en)
Inventor
Dirk Reimnitz
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112018006424.7T priority Critical patent/DE112018006424A5/de
Publication of WO2019120382A1 publication Critical patent/WO2019120382A1/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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/644—Hub construction
    • F16D13/646—Mounting of the discs on the hub
    • 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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • F16D13/683—Attachments of plates or lamellae to their supports for clutches with multiple lamellae
    • 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
    • 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
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
    • 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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D2013/642—Clutch-plates; Clutch-lamellae with resilient attachment of frictions rings or linings to their supporting discs or plates for allowing limited axial displacement of these rings or linings
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches

Definitions

  • the invention relates to a torque transmission unit for the frictional transmission of torque, in particular a clutch device for a drive train of a motor vehicle, an electric drive unit, in particular a hybrid module with the torque transfer unit according to the invention, and a drive train.
  • Multi-plate clutches as they are oil lubricated. This results in a greater power requirement for shifting the slats or the torque to be transmitted is smaller at the same operating force. Due to the relatively small diameter of the slats of the dry friction clutch and the associated high tangential forces, this is a relatively large proportion of losses.
  • Slats in multi-plate clutches are usually non-rotatably but axially displaceable to connect with adjacent coupling parts, which are assigned to the drive or output of the clutch. This torque transmitting positive locking
  • connection between the fins and the adjacent components of the coupling is usually realized by a toothing.
  • the slats of the drive and the lamellae of the output are axially spaced apart or ventilated.
  • the clutch is closed, the blades are pressed together so that the friction surfaces of the blades touch and torque can be transmitted by friction between the drive and the output associated slats.
  • the increase in the transmittable torque when closing the clutch and the reduction of the transmittable torque when opening the clutch is not abrupt. It comes during the engagement or closing of the clutch or the disengagement or opening of the clutch to a continuous torque build-up or torque reduction.
  • Coupling components one of the axial movement opposing frictional force. This frictional force is higher, the greater the tangential force caused by the transmitted moment at the connection point and the higher the coefficient of friction acting on the connection point.
  • the resulting tangential forces and the coefficients of friction at the connection point can usually only be slightly changed since they largely depend on the basic function of the coupling and the materials used
  • Reiblamellen and the material of the coupling component, in which the friction plate positively but limited axially displaceable engages are determined.
  • the axial forces counteracting frictional forces in the axially displaceable joints increase the clutch actuation force required for a particular transmissible torque.
  • the object of the present invention is to provide a torque transmission unit, an electric drive unit configured therewith and a drive train of a motor vehicle, which combine a long service life with low production costs and energy-efficient operation.
  • Electric drive unit is specified in dependent claim 9.
  • Rotation axis of said aggregates is oriented orthogonal to friction surfaces of lamellae of the coupling devices used.
  • the invention relates to a torque transmission unit for the frictional transmission of torque, wherein the torque transmission unit is configured in particular as a coupling device for a drive train of a motor vehicle.
  • the torque transmission unit comprises a plurality of friction elements, which are compressible for frictional transmission of the torque to a friction package, wherein at least one of the friction elements is disposed axially displaceable with respect to a further friction member and at least one friction member having the axial loading with a normal force for generating a frictional force configured to transmit the torque.
  • the friction element has at least one connecting part, which is fixed to the friction part and at least one form element, in particular a toothing, with the form-fitting connection of the torque a torque on a cooperating with the mold element component is transferable from the connecting part.
  • the connecting part is at least partially configured axially elastic, so that between the mold element of the connecting part and the friction part axially a translational relative movement is executable.
  • the friction member and the mold member of the connecting part are thus torsionally rigid, but axially elastically connected to each other.
  • the friction member may be, for example, a friction blade or a pressure plate of a Reibvers. The friction member is then annular
  • Friction surface on In the embodiment as a friction plate, it has axially on both sides friction surfaces for contact there contacting components, such as on counter blades or on a plate, such as a pressure plate or Counterpressure plate, on.
  • the further friction element on which the inventively designed friction element for transmitting torque comes to rest may be a blade or a plate, such as a pressure plate or counter-pressure plate.
  • the friction part can therefore be designed to
  • a plurality of friction elements in the form of a friction or disk set are present, wherein the fins and / or the pressure plate of the disk packs are designed according to the invention axially elastic.
  • the formula element as a toothing is the
  • Connecting part arranged displaceably on the toothing.
  • the form element for the positive transmission of the torque is arranged on a radial outside or inside of a respective friction element.
  • the connecting part is at least partially by axially elastic material
  • the connecting part comprises an extra component, such as a
  • the connecting part has at least one radially and / or tangentially extending connecting element, at the radial or tangential end portion of the connecting part is fixed to the friction part, wherein the connecting element is designed in the form of a rod or a leaf spring.
  • the rod-shaped connecting element is designed to and compressive forces to transmit the applied torque between the mold member and the friction member.
  • the rod-shaped connecting element can be designed to be relatively flat and / or in addition to a radial extension component also have a tangential extension component and consequently as a strut
  • a plurality of rod-shaped connecting parts are arranged between the shaping element for transmitting the torque and the friction part, in particular distributed uniformly over the circumference of the friction part.
  • Counter-rotation can be loaded with correspondingly lower compressive forces, so that despite the buckling load, the risk of a component failure is reduced.
  • the friction member may be formed at least partially by friction material in the region of the axial application of normal force, wherein the friction material has at least one axial recess in which the rod-shaped
  • Connecting element is substantially embedded in the friction material of the friction member, but in the circumferential direction between the rod-shaped connecting element and the friction material to avoid contact.
  • Embodiment allows a small radial extent of the friction element.
  • the connecting part has a disc spring area, which realizes the mechanical connection between the form element and the friction part.
  • this is thus formed substantially annular. It can the
  • Disc spring region in particular in sections, where it is fixed to the friction member, also have rod-shaped connecting elements, an increasing contribution to provide elasticity.
  • a spacer element can be arranged between the connecting part and the friction part, in order to realize an axial complaint of the two parts also in the area of the mechanical connection and, consequently, one
  • a fixing of the connecting part on the friction part at the radial boundary region of the friction part is realized, which radially to the mold element for
  • the connecting part may extend axially in regions on the radial side of the friction part, on which the connecting part takes over the transmission of the torque from the friction element or to the friction element.
  • the connecting part in the region in which it has the shape element for transmitting torque, in particular a toothing may have a significantly greater axial thickness than, for example, in the region of the mechanical fixation on the friction part.
  • This embodiment serves to reduce a surface pressure between the shaped element of the connecting part and the component to be connected thereto in a form-fitting manner, such as, for example, a complementarily shaped toothing of a plate carrier.
  • Connecting part and friction member and the friction member itself are configured such that at a certain axial load of the friction element, the elastic connection between the connecting part and the friction part allows a spring travel SF and the friction part itself allows a spring travel SB, the two spring travel in the following
  • the friction part can be deflected so elastically in relation to the connecting part, starting from its axial force-free basic position, that a movement takes place in a preferably in both axial directions. These elastic displacement of the friction member in an axial direction starting from the force-free basic position corresponds to the spring travel SF.
  • Each friction part in particular each friction plate, has a component or
  • Assembly stiffness in the axial direction which provides a spring action between the two opposing friction surfaces.
  • This rigidity may be due, for example, to the elasticity of the fin material (e.g., the friction lining) and / or to the waviness of individual parts installed in the fin or to the entire friction fin.
  • the spring travel, with which the axially furthest extending points of the opposing friction surfaces in the axial direction approach each other when the blade is axially compressed, is referred to as
  • Neighboring components at least equal to the distance between the axially furthest extending of the two opposing friction surfaces of the force-free friction plate. To ensure that the clutch definitely no longer transmits any significant drag torque to the friction plate, the neighboring components are pushed a little further apart. This additional way around which the
  • Spring travel SF can be realized, which corresponds to the sum of all pad suspension paths SB and all the air paths SL behind the lining plates.
  • friction elements or friction parts are meant that between the friction plate with the respective connecting part and the counter-plate are arranged and clamped and by means of which the contact pressure is transmitted from a friction contact to the axially next frictional contact.
  • the torque transmission unit may be arranged such that the friction member with at least one lying in the pressing direction behind lamella or at least one lying in contact pressing friction partner a series arrangement of friction elements having an axial elasticity, so that at a certain axial load of the friction element elastic
  • connection between connecting part and friction part allows a spring travel SF and at the same specific axial load, the series arrangement of friction elements even a spring travel SB2 allows, the spring travel in the following relationship are: SF> SB2.
  • the spring travel which provide the individual slats can thus be different in a clutch.
  • the friction plates which are arranged close to the counter plate, require less travel than the slats, which are arranged near the pressure plate.
  • the connecting part of the pressure plate requires the largest
  • Another aspect of the present invention is an electric drive unit, in particular a hybrid module for a motor vehicle for coupling a
  • This electric drive unit comprises an electric machine for generating a drive torque with a rotor which is rotatably mounted on a rotatable rotor carrier, and at least one torque transmission unit according to the invention as a coupling device with the torque from the electric machine and / or from an input side of the coupling device to a drive train is transferable.
  • the coupling device comprises a plurality of friction elements comprehensive friction package, which is at least partially disposed radially and axially within the space radially surrounding the rotor carrier, wherein the rotor carrier realizes on the radially inner side of the friction pack a non-rotatable mechanical connection to at least one of the friction elements of the friction pack for the purpose of transmitting torque.
  • the rotor carrier may comprise several parts, such as a part which serves to fix the rotor of the electric machine, as well as a part which extends in regions around the friction pack to its radially inner side.
  • Friction elements of the Reibaves a substantially hollow cylindrical
  • Disk carrier which extends on the radial outer side of the friction pack and thus in a gap between the rotor or rotor carrier and the friction pack.
  • the friction package comprises in particular as friction elements mutually arranged first fins and second fins.
  • a drive train for a motor vehicle with a drive machine, in particular with an internal combustion engine, is made available, which is designed as a coupling device according to the invention
  • the inventively designed coupling device can be here a disconnect coupling between
  • a hybrid module Internal combustion engine and an electric drive, such as a hybrid module is arranged, and / or it may be part of a hybrid module, which is arranged between the internal combustion engine and a transmission.
  • the hybrid module may have a multiple coupling device with a plurality of coupling devices, which are designed according to the invention.
  • FIG. 1 a hybrid module according to the invention in partial section
  • FIG. 2 shows an enlarged view of the separating clutch illustrated in FIG. 1,
  • FIG. 3 a torque transmission unit according to the invention in perspective
  • Figure 4 executed as a pressure plate friction element in perspective
  • FIG. 5 shows a perspective view of a first embodiment of a friction element designed as a friction plate with a sectional view
  • FIG. 6 shows a second embodiment of a friction lamella
  • Friction elements in a perspective view with a sectional view and Figure 7 shows a third embodiment of a designed as a friction blade friction element in a perspective view with a sectional view.
  • the friction plates 32 and the pressure plates 33 usually comprise a friction member 40 as a base body, which forms the friction surfaces 34 and is thick enough to serve the coupling means 21, 25 as a thermal mass; and from a rotationally fixed but axially elastic connected to the friction member 40
  • the connecting part 50 engages over at least one forming element 51, such as e.g. a tooth contour, for the realization of a form-fitting
  • the connected to the illustrated stub shaft 90 of an internal combustion engine via a vibration damper 91 assembly of the clutch 100 comprises an axially fixed counter-pressure plate 103, a friction member 31 which is mounted with its axially elastic connection member 50 on the outer plate carrier 104 and a pressure plate 102, which also with its axially elastic
  • Connecting part 50 is connected to the outer disk carrier 104.
  • Output module of the separating clutch 100 has two with the Inner disk carrier 105 connected friction plates 32 which form the clutch plates 101 of the separating clutch 100.
  • One of these friction plates 32 is located between the counter-pressure plate 103 and the friction member 31 connected to the outer disk carrier 104.
  • the second of these friction disks 32 is located between the friction disk 32 connected to the outer disk carrier 104 and the pressure plate 102.
  • the inner disk carrier 105 connected friction plates 32 designed as lining lamellae whose lamellar body directly rotationally fixed positive but axially displaceable in the outer contour of the
  • Intervene inner disk carrier 105 any of these can be any of these.
  • Bellows lamellae alternatively or additionally be equipped with an axially elastically connected connecting part, as described with reference to Figure 2.
  • the actuation system of the disconnect clutch 106 is integrated in a partition wall 141, which is part of the housing 140.
  • the partition wall 141 also forms a bearing carrier 142, on which rolling bearings 143 are arranged, which support the intermediate shaft 130.
  • the rotor carriers 70 designed as the inner disk carrier are each one of them
  • FIG. 6 shows a second one shown on the right
  • the pressure plate 33 of the second coupling device 25 also has an axially elastically connected connecting part 50, see also the
  • the hybrid module 10 shown here comprises a plurality of coupling devices
  • the electric machine 60 comprises a stator 62 and on its radial inner side a rotor 61, which is arranged rotationally fixed on a rotor carrier 70.
  • the rotor carrier 70 has in the here illustrated embodiment, the special feature that it extends from the rotor 61 of the electric machine 60 to the radially inner sides 36 of the Reibvere 30 of the first clutch means 21 and the second clutch means 25.
  • the friction pack 30 of the first clutch device 21 is a first
  • External disk carrier 23 assigned, which can transmit from the first clutch means 21 torque to a first transmission input shaft 150.
  • Friction packet 30 of the second clutch device 25 is a second
  • Coupling device 25 can transmit to a second transmission input shaft 151.
  • the rotor carrier 70 is rotatably coupled to an intermediate shaft 130, which as
  • Input side 29 of the multiple clutch device 29 is used.
  • Coupling means 21, 25 and the outer disk carrier 23,27 torque are transmitted to the transmission input shafts 150,151.
  • the first coupling device 21 is assigned a first actuating system 22.
  • the second coupling device 25 is associated with a second actuating system 26. Due to the extension of the rotor carrier 70 to the radially inner side of the two coupling devices 21, 25, it is possible that the
  • Gap 80 between the two coupling devices 21, 25 and the rotor 61 of the electric machine 60 run. Because of that, the first
  • Outer disk carrier 23 has first radially extending passage openings 24, and the second outer disk carrier 27 second radially extending
  • Coupling means 21, 25 heated air can flow out through the through holes 24,28 radially outward and can be axially discharged laterally. This provides a significant contribution to preventing overheating of the electric machine 60.
  • this embodiment allows that actuation system for the second
  • Coupling device 25 to be positioned in the area between the rotor carrier 70 and intermediate shaft 130, where the second actuating system 26 with a ring 46, the will be explained in more detail with reference to Figure 4, is mechanically coupled.
  • a plurality of passage elements 72 are arranged running radially outward, which engage through radial recesses 71 in the rotor carrier 70 and act there axially on the pressure plate 33 of the second coupling device 25.
  • a dirt deflector 152 is disposed on the rotor support 70 on an axial end side in order to prevent the penetration of dirt particles.
  • Figures 2 and 3 show differently designed multi-plate clutches.
  • the variant of Figure 2 is similar to the separating clutch 100 of Figure 1. However, it has elastic connection parts 50 on all slats. In the lining slats, the elastic connection of the connecting parts 50 is laid inside the friction plate 32 in order to save radial space. The core of the friction plate 32 and
  • Bellows lamella which is arranged between the linings, is similar in structure as described below for the lamellae with a metallic friction surface.
  • Figure 3 shows a sectioned multi-plate clutch in a perspective view.
  • the counter-pressure plate 35 is rotationally fixed and axially fixed to the inner disk carrier 38.
  • the axial support is effected by a securing ring 39.
  • a rotationally fixed but axially movably connected to the outer disk carrier friction plate 32 and a rotatably but axially movably connected to the inner disk carrier 38 friction member 31 are alternately arranged.
  • the pressure plate 33 is arranged, which is just like the slats or friction elements 31 without covering by an elastic connecting part 50 via the mold member 51 is connected to the inner disk carrier 38.
  • the elastic connection part 50 of the pressure plate 33 mainly comprises an axially elastic, but in the circumferential direction rigid component.
  • this is a plate spring-like component or a cup spring portion 53, which has a toothing 120 at its inner radial boundary and is connected in an outer radial boundary region 43 with the friction part 40 of the pressure plate 33 by means of rivet 57. Since the cup spring portion 53 rests only radially on the outside of the pressure plate 33, may be formed as a toothed inner region shaped molding element 51 elastically to the body of the pressure plate 33 toward or away be relocated. This axial pivoting movement is made possible by the
  • Fixations 55 are decoupled to the friction member 40 and pressure plate body by releases 59 and configured only as elastic torsion arms
  • Connecting elements 52 are connected to the rest of the plate spring portion 53.
  • the connecting elements 52 are arranged in a tangential direction, so that the axial displacement of the die element 51 or the teeth (for example by axial pivoting) is easily possible, but forces in the tangential direction, as they occur in the transmission of the clutch torque, can be transmitted safely.
  • the torque which is introduced into the friction surface 34 of the pressure plate 33 is thus introduced into the connecting elements 52 in the form of a tangential force via the rivet connections 57.
  • the mutually from the riveting 57 outgoing connecting elements 52 then transmit this force by tensile and compressive forces in the body of the disc spring portion 53, which then transmits the torque via the mold member 51 to the inner disk carrier 38.
  • this coupling device via an actuating system, which is connected via the pressure pot 58 shown with the pressure plate 33.
  • an actuating element with power or distance transmission and / or an energy storage such as a Flebelfeder or a
  • Disc spring can be used.
  • the pressure pot 58 introduces an axial force into the body of the pressure plate 33, without burdening the axially elastic portion of the plate spring-like plate spring portion 53 or connecting part 50, so that the plate spring portion 53 can continue to move axially.
  • the pressure pot 58 is supported with projections on the pressure plate 33, which by the releases 59 in the
  • Disc spring area 53 connect with the pressure plate 33, also serve as
  • FIG. 4 shows a further pressure plate 33 with a friction part 40 and a
  • Coupling device 25 can be seen, the introduction of the contact force of radially inside.
  • a plurality of circumferentially spaced receptacles 44 are formed on the body of the pressure plate 33, in which elongated transmission elements 45, which are referred to in Figure 1 as Natural Bachs institute 72 and e.g. can be designed as pins or rods can invest.
  • This elongated transmission elements 45 which are referred to in Figure 1 as Natural Bachs institute 72 and e.g. can be designed as pins or rods can invest.
  • Transmission elements 45 or passage elements 72 protrude through recesses 71 or elongated holes of the rotor carrier 70 (see FIG. 1) and are fastened in a ring 46 connected to the engagement bearing.
  • the actuation system can thus exert force on the pressure plate 33 via the elongated transmission elements 45 and displace it.
  • the rotation of the pressure plate 33 is limited only by the toothing or the mold member 51 between the cup spring portion 53 and the rotor carrier 70.
  • the plate spring region 53 is recessed in the region of the elongated transmission element 45 so that it can move freely axially.
  • Transmission element 45 is used. At the second connection position no pin is shown, so that the receptacle for the pin in the resting on the bearing ring 46 can be seen and thus the contact point 44 on the body of the friction member 40 of the pressure plate 33 is visible.
  • a plurality of circumferentially distributed transmission elements 45 are fixedly connected to the ring 46.
  • Figure 5 shows a friction plate 32 with a friction member 40 and an axially elastically connected connecting member 50 in a perspective view with a
  • the connecting part 50 which forms the fastening region, comprises an annular toothing body, from which obliquely outward connecting elements 52 emerge as struts or spoke-like attachment pockets.
  • Connecting elements 52 and Anbindelaschen are radially on the outer
  • Form elements 51 are recessed in the friction material 41 of the friction member 40 in axial recesses 42 of the blade. As a result, all parts which form the axially elastic region of the connecting part 50 lie below the friction surface 34 and thus do not hinder the frictional contact with the neighboring blade.
  • the axial recesses 42, in which the connecting elements 52 and Anbindelaschen lie are designed as inclined slots in the friction surfaces 34 which extend from the radially inner edge to the radially outer edge. As a result, these slots or axial recesses 42 can also contribute to the cooling of the clutch, since air can flow through from radially inward to radially outward or vice versa, even when the clutch is closed. As a result, the friction plate 32 and the friction surfaces 34 are cooled particularly well. Another positive effect of these axial recesses 42 is that dirt, like him
  • the axial recesses 42 should always be significantly wider and deeper than required for the connecting elements 52 and their movement. The additional space prevents dirt particles between the
  • Connecting elements 52 and the friction material 41 are clamped. If the connecting elements 52 would pinch or press dirt particles, more and more dirt would settle next to the connecting element 52 and hinder their movement over time. To prevent the accumulation of dirt it is makes sense, the bearing surfaces for the fixations 55 between the
  • connection part 50 When the connection part 50 is not with
  • Fastening elements 52 is fixed, but for example with torsion or a plate spring-like ring body, the described here
  • the side of the friction plate 32 or pressure plate 33, to which no connecting part 50 is attached, can also be equipped with radial and / or tangential grooves. The more dirt or heat is dissipated elsewhere, the less concentrated on the axial recesses 42, in which the
  • Connecting elements 52 are arranged and the lower the risk that the connecting elements 52 are impaired.
  • the connecting part 50 which forms the fixation 55, touches the friction part 40 only at the riveting points, so that the toothing body and the fixing part 50
  • Connecting elements 52 can move axially relative to the friction member 40 elastically. This can be realized by the shape of the axial recesses 42.
  • the embodiment of Figure 6 shows a friction plate 32, which is similar to the embodiment of Figure 5. However, at the points where the connecting elements 52 merge into the mold elements 51 and the toothed body, respectively
  • the spacing mechanism is formed by corrugated springs 73.
  • These corrugated springs 73 are based on the extensions 37 of Friction 40 off. As a result, the corrugated springs 73 can exert force on the lamellae without impairing the axially elastic connection region 50.
  • the tooth width of the connecting part 50 of the embodiment shown in Figure 7 has been significantly increased.
  • Gearing has been formed.
  • the shaped element 51 on the connecting cable 50 thus forms a region of greater width 54.
  • the toothing body and the connecting elements 52 may also be made of different thickness starting materials and then assembled into an assembly. This makes it possible, for example, to produce the toothing of thick sheet metal in order to obtain broad tooth flanks and to produce the connecting elements 52 from thinner spring steel sheet in order to ensure sufficient elasticity.

Abstract

L'invention concerne une unité de transmission de couple, une unité d'entraînement électrique et une transmission. L'unité de transmission de couple (1) comprend une pluralité d'éléments de friction (31) qui peuvent être comprimer en un paquet de friction (30) pour la transmission par friction du couple. Au moins un des éléments de friction (31) est disposé de manière à pouvoir se déplacer axialement par rapport à un autre élément de friction (31) et comporte au moins un élément de friction (40) qui est conçu pour être soumis axialement à une force normale pour générer une force de friction pour transmettre le couple, et l'élément de friction (31) comporte au moins un élément de liaison (50) qui est fixée à l'élément de friction (40) et au moins un élément moulé (51), en particulier une denture, permettant de transmettre par complémentarité de formes un couple de l'élément de liaison (50) à un composant coopérant avec l'élément moulé (51). L'élément de liaison (50) est conçu pour être au moins en partie axialement élastique de sorte qu'un mouvement de translation relatif puisse être effectué axialement entre l'élément moulé (51) de l'élément de liaison (50) et l'élément de friction (40). L'unité de transmission de couple et l'unité d'entraînement électrique équipée de celle-ci sont des moyens de transmission et de génération de couple qui allie une durabilité élevée à un faible coût de fabrication et à un fonctionnement économe en énergie.
PCT/DE2018/101023 2017-12-18 2018-12-14 Unité de transmission de couple, unité d'entraînement électrique et transmission WO2019120382A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112018006424.7T DE112018006424A5 (de) 2017-12-18 2018-12-14 Drehmomentübertragungseinheit, elektrische Antriebseinheit und Antriebsstrang

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017130350.2 2017-12-18
DE102017130350.2A DE102017130350A1 (de) 2017-12-18 2017-12-18 Drehmomentübertragungseinheit, elektrische Antriebseinheit und Antriebsstrang

Publications (1)

Publication Number Publication Date
WO2019120382A1 true WO2019120382A1 (fr) 2019-06-27

Family

ID=64901263

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2018/101023 WO2019120382A1 (fr) 2017-12-18 2018-12-14 Unité de transmission de couple, unité d'entraînement électrique et transmission

Country Status (2)

Country Link
DE (2) DE102017130350A1 (fr)
WO (1) WO2019120382A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113939666A (zh) * 2019-07-10 2022-01-14 舍弗勒技术股份两合公司 多盘式离合器盘
CN115210484A (zh) * 2020-05-11 2022-10-18 舍弗勒技术股份两合公司 具有用于将两个子盘接合到从动轴上的彼此独立地作用的弹簧板单元的多盘式离合器装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019127238A1 (de) 2019-04-10 2020-10-15 Schaeffler Technologies AG & Co. KG Lamellenkupplung, insbesondere für einen Hybrid-Antriebsstrang
DE102019112566A1 (de) 2019-04-10 2020-10-15 Schaeffler Technologies AG & Co. KG Lamellenkupplung, insbesondere trockene Lamellenkupplung, insbesondere für hybriden Antriebsstrang
DE102019118972A1 (de) * 2019-07-12 2021-01-14 Schaeffler Technologies AG & Co. KG Lamellenkupplung mit einer Rotationsachse für einen Antriebsstrang

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2333308A (en) * 1940-06-17 1943-11-02 George I Goodwin Clutch plate
US2738864A (en) * 1951-08-18 1956-03-20 Borg Warner Clutch belleville spring type
DE3320977C1 (de) * 1983-06-10 1984-12-20 Prodan Antriebselemente GmbH, 7033 Herrenberg Lamellenkupplung
US20030234150A1 (en) * 2002-06-19 2003-12-25 Zf Sachs Ag Clutch disk arrangement for a multiple-disk clutch
WO2015144108A1 (fr) * 2014-03-27 2015-10-01 Schaeffler Technologies AG & Co. KG Système de multiplication pour un embrayage à friction multidisque
WO2015144170A2 (fr) * 2014-03-27 2015-10-01 Schaeffler Technologies AG & Co. KG Embrayage à disques multiples

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2333308A (en) * 1940-06-17 1943-11-02 George I Goodwin Clutch plate
US2738864A (en) * 1951-08-18 1956-03-20 Borg Warner Clutch belleville spring type
DE3320977C1 (de) * 1983-06-10 1984-12-20 Prodan Antriebselemente GmbH, 7033 Herrenberg Lamellenkupplung
US20030234150A1 (en) * 2002-06-19 2003-12-25 Zf Sachs Ag Clutch disk arrangement for a multiple-disk clutch
WO2015144108A1 (fr) * 2014-03-27 2015-10-01 Schaeffler Technologies AG & Co. KG Système de multiplication pour un embrayage à friction multidisque
WO2015144170A2 (fr) * 2014-03-27 2015-10-01 Schaeffler Technologies AG & Co. KG Embrayage à disques multiples

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113939666A (zh) * 2019-07-10 2022-01-14 舍弗勒技术股份两合公司 多盘式离合器盘
CN113939666B (zh) * 2019-07-10 2024-02-27 舍弗勒技术股份两合公司 多盘式离合器盘
CN115210484A (zh) * 2020-05-11 2022-10-18 舍弗勒技术股份两合公司 具有用于将两个子盘接合到从动轴上的彼此独立地作用的弹簧板单元的多盘式离合器装置
CN115210484B (zh) * 2020-05-11 2024-02-27 舍弗勒技术股份两合公司 具有用于将两个子盘接合到从动轴上的彼此独立地作用的弹簧板单元的多盘式离合器装置

Also Published As

Publication number Publication date
DE112018006424A5 (de) 2020-09-17
DE102017130350A1 (de) 2019-06-19

Similar Documents

Publication Publication Date Title
WO2019120382A1 (fr) Unité de transmission de couple, unité d'entraînement électrique et transmission
EP3123042B1 (fr) Embrayage à disques multiples
EP1298339B1 (fr) Arrangement d'accouplement multiple, notamment embrayage double
EP3655274B1 (fr) Module hybride
DE102009057353A1 (de) Lamellenkupplung mit einer Federeinrichtung
EP1134447A2 (fr) Configuration de double embrayage
WO2014012542A1 (fr) Embrayage double
EP3728889B1 (fr) Unité de transmission de couple et chaîne cinématique
EP3655277A1 (fr) Module hybride
DE102017130348A1 (de) Kupplungseinrichtung, Mehrfachkupplungseinrichtung, elektrische Antriebseinheit und Antriebsanordnung für ein Kraftfahrzeug
DE102014219521A1 (de) Raumsparende Radiale Doppelkupplung
EP3123043B1 (fr) Double embrayage à disques multiples
DE19848582A1 (de) Selbstverstärkende Reibungskupplung
EP3655279A1 (fr) Module hybride
DE102018119970A1 (de) Reibkupplung mit Anti-Klapper-Dämpfer
WO2018091022A1 (fr) Dispositif de transmission de couple
DE102017130853B4 (de) Kupplungseinrichtung
DE102015211601A1 (de) Reibkupplung mit einer Rotationsachse zum lösbaren Verbinden einer Abtriebswelle mit einem Verbraucher
WO2019210902A1 (fr) Dispositif d'embrayage a friction, module hybride et dispositif d'entrainement pour un vehicule automobile
EP1719930A2 (fr) Ensemble de disque d'embrayage pour embrayages multiples, en particulier embrayage à deux disques
DE102017130272A1 (de) Hybridmodul
EP3655275B1 (fr) Module hybride
EP3874174B1 (fr) Embrayage à friction
DE102016222891B4 (de) Drehmomentübertragungseinrichtung
DE102014207341A1 (de) Mehrscheibenkupplung

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18826936

Country of ref document: EP

Kind code of ref document: A1

REG Reference to national code

Ref country code: DE

Ref legal event code: R225

Ref document number: 112018006424

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18826936

Country of ref document: EP

Kind code of ref document: A1