DE102020113605A1 - Clutch assembly, method for manufacturing a hydraulic actuation system for a clutch assembly and method for manufacturing a clutch assembly - Google Patents

Abstract

The invention relates to a clutch arrangement (1), in particular for coupling an electric motor (2) and / or an internal combustion engine (3) to the drive train (4) of a motor vehicle (5), in particular by means of a hybrid module, comprising a clutch (6) with at least a clutch disc (7) which is arranged radially and axially between a pressure plate (8) and a counter-plate (10) axially opposite the pressure plate (9), so that a relative axial offset of the clutch disc (7) and / or pressure plate (9 ) and / or counter plate (10) a frictional connection can be established between these components and a torque can thus be transmitted between the clutch disc (7) and the pressure plate (9) and counter plate (10), the clutch (6) having an actuation system (18) is operatively connected, by means of which the clutch (6) can be transferred to an engaged and / or disengaged operating state, the particular hydraulic actuation system (18) e has a piston (26) which can be axially displaced coaxially to the clutch rotation axis (32) and has a circular end face (31) which is mechanically connected to the clutch (6) in such a way that an axial displacement of the piston (26) actuates the clutch (6 ) causes.

Description

The present invention relates to a clutch arrangement, in particular for coupling an electric motor and / or an internal combustion engine to the drive train of a motor vehicle, in particular by means of a hybrid module, comprising a clutch with at least one clutch disc which is positioned radially and axially between a pressure plate and a counter plate axially opposite the pressure plate is arranged so that by a relative axial offset of the clutch disc and / or pressure plate and / or counter plate, a frictional connection can be established between these components and a torque can thus be transmitted between the clutch disc and the pressure plate and counter plate, the clutch being operatively connected to an actuation system, by means of which the clutch can be converted into an engaged and / or disengaged operating state. The invention also relates to a method for producing a hydraulic actuation system for a clutch arrangement. The invention also relates to a method for producing a clutch arrangement.

As from the EP 0 773 127 A1 , DE 100 18 926 A1 and US 2007/0175726 A1 is known, a first clutch arrangement can be arranged between the internal combustion engine and the electric motor in order to separate the internal combustion engine from the electric motor and the rest of the drive train of the hybrid vehicle. In the case of a purely electric drive, the first clutch arrangement is then also referred to as a separating clutch - it is opened and the internal combustion engine is switched off so that the drive torque of the hybrid vehicle is generated solely by the electric motor.

Such separating clutches are usually operated by means of a hydraulic release system. A hydraulic release system usually has a master cylinder that transmits the pressure generated on the master cylinder to the slave cylinder via a hydraulic pressure line. Occasionally the hydraulic pressure is also increased by means of a so-called Powerpacks provided, which consists of a hydraulic pump and a hydraulic pressure accumulator that can be acted upon by the hydraulic pump. By means of an axially displaceable piston and with the interposition of a clutch release bearing, the slave cylinder transmits the hydraulic pressure to a lever system, by means of which a frictional connection is established or released on the separating clutch. Fully hydraulic clutch systems, as they are usually used in hybrid modules, can, for example, be equipped with a central release mechanism, which is often also referred to as a Concentric Slave Cylinder (CSC). These clutch release systems based on a central release require a comparatively large, cylinder-ring-like installation space within a hybrid module.

The separating clutches required for hybridizing conventional drive trains also have to meet special requirements in terms of size and energy efficiency compared to conventional clutch systems. In particular, separating clutches for P2 hybrid modules must have a particularly low drag torque when they are open. When the vehicle is driven by the electric motor and the internal combustion engine is switched off, high differential speeds often occur for a long time in the disengaged clutch between the drive side and the output side of the clutch. Even small drag torques occurring in the clutch can quickly lead to inadmissibly high energy inputs due to the large differential speeds. If the energy input into the disengaged clutch is too high, this can lead to increased wear of the friction linings and thus to the premature failure of the clutch. High energy inputs into the disengaged clutch can also have a negative impact on the range that the vehicle can cover on one battery charge without the assistance of the combustion engine.

The object of the invention is therefore to provide a clutch arrangement which is as compact as possible.

This object is achieved by a clutch arrangement, in particular for coupling an electric motor and / or an internal combustion engine to the drive train of a motor vehicle, in particular by means of a hybrid module, comprising a clutch with at least one clutch disc which is located radially and axially between a pressure plate and one axially opposite the pressure plate Counter-plate is arranged so that a frictional connection between these components can be produced by a relative axial offset of the clutch disc and / or pressure plate and / or counter-plate and thus a torque can be transmitted between the clutch disc and the pressure plate and counter-plate, the clutch being operatively connected to an actuation system , by means of which the clutch can be transferred to an engaged and / or disengaged operating state, the particular hydraulic actuation system having a piston which can be displaced in the axial direction coaxially to the clutch axis of rotation n has a circular end face which is mechanically connected to the clutch in such a way that an axial displacement of the piston causes the clutch to be actuated.

This realizes the advantage of a particularly compact design of a clutch arrangement. The inventive The clutch arrangement is particularly suitable for hybridizing existing conventional drive trains that have, for example, a torque converter, a wet clutch or a wet double clutch. With the clutch arrangement according to the invention, the hydraulic oil supply that is usually already present in converter transmissions or wet clutch transmissions can be used in order to also supply the clutch actuation system and to implement a very compact and inexpensive clutch concept. As an alternative to the preferred hydraulic actuation of the clutch arrangements explained in detail below, mechanical, electromechanical, electrical and / or electromagnetic actuation methods are also conceivable in principle.

A general advantage of the piston with a circular end face is that only one translationally displaceable seal is required. Compared to the usual central release pistons (CSC pistons), which have a circular cross-section and require two translationally displaceable seals (one seal for the outer diameter and one for the inner diameter of the piston surface), the length on which the piston seals act is reduced considerable. Therefore, pistons with a circular cross-section have a significantly lower hysteresis and also less residual leakage than pistons with an annular cross-section.

First, the individual elements of the claimed subject matter of the invention are explained in the order in which they are named in the set of claims and particularly preferred embodiments of the subject matter of the invention are described below.

Motor vehicles in the sense of this application are land vehicles that are moved by machine power without being tied to railroad tracks. A motor vehicle can be selected, for example, from the group of passenger cars (cars), trucks (trucks), small motorcycles, light motor vehicles, motorcycles, motor buses (KOM) or tractors.

A hybrid electric vehicle, also known as a Hybrid Electric Vehicle (HEV), is an electric vehicle that is driven by at least one electric motor and another energy converter and draws energy from its electrical storage unit (battery) as well as an additional fuel.

In the context of this application, the drive train of a motor vehicle is understood to mean all components that generate the power for driving the motor vehicle in the motor vehicle and transmit it to the road via the vehicle wheels.

In a hybrid module, structural and functional elements of a hybridized drive train can be spatially and / or structurally combined and preconfigured so that a hybrid module can be integrated into a drive train of a motor vehicle in a particularly simple manner. In particular, an electric motor and a clutch system, in particular with a disconnect clutch for engaging the electric motor in and / or disengaging the electric motor from the drive train, can be present in a hybrid module.

• P0: der Elektromotor ist vor der Brennkraftmaschine angeordnet und beispielsweise über einen Riemen mit der Brennkraftmaschine gekoppelt. Bei dieser Anordnung des Elektromotors wird dieser auch gelegentlich als Riemenstartergenerator (RSG) bezeichnet,
• P1: der Elektromotor ist direkt hinter der Brennkraftmaschine angeordnet. Die Anordnung des Elektromotors kann beispielsweise kurbelwellenfest vor der Anfahrkupplung erfolgen,
• P2: der Elektromotor ist zwischen einer häufig als K0 bezeichneten Trennkupplung und der Anfahrkupplung aber vor dem Fahrzeuggetriebe im Antriebsstrang angeordnet,
• P3: der Elektromotor ist im Fahrzeuggetriebe und/oder der Getriebeausgangswelle angeordnet,
• P4: der Elektromotor ist an einer bestehenden oder separaten Fahrzeugachse angeordnet und
• P5: der Elektromotor ist am oder im Fahrzeugrad angeordnet, beispielsweise als Radnabenmotor.

A hybrid module can be divided into the following categories P0-P4, depending on the point at which the electric motor engages in the drive train:

• P0: the electric motor is arranged in front of the internal combustion engine and, for example, coupled to the internal combustion engine via a belt. With this arrangement of the electric motor, it is sometimes referred to as a belt starter generator (RSG),
• P1: the electric motor is arranged directly behind the internal combustion engine. The arrangement of the electric motor can, for example, be fixed to the crankshaft in front of the starting clutch,
• P2: the electric motor is arranged between a separating clutch, often referred to as K0, and the starting clutch, but in front of the vehicle transmission in the drive train,
• P3: the electric motor is arranged in the vehicle transmission and / or the transmission output shaft,
• P4: the electric motor is arranged on an existing or separate vehicle axle and
• P5: the electric motor is arranged on or in the vehicle wheel, for example as a wheel hub motor.

The clutch arrangement according to the invention is preferably integrated as a separating clutch in a hybrid module, particularly preferably in a P2 hybrid module which is arranged within the drive train of a motor vehicle between the internal combustion engine and the vehicle transmission. Alternatively, it can also be preferred to arrange the clutch arrangement according to the invention in a P1 hybrid module. In purely electric driving, for example, the internal combustion engine is then disengaged by the clutch arrangement according to the invention.

The vehicle transmission is the transmission in the drive train of a motor vehicle that converts the engine speed to the drive speed.

An internal combustion engine, also often referred to as an internal combustion engine, converts chemical energy into mechanical work. For this purpose, an ignitable mixture of fuel and air is burned in the combustion chamber of the internal combustion engine. Internal combustion, i.e. the generation of combustion heat in the internal combustion engine, is characteristic of internal combustion engines. The thermal expansion of the resulting hot gas is used to move pistons (rotors in Wankel engines).

An electric motor is an electrical machine that converts electrical power into mechanical power. As a rule, current-carrying conductor coils in electric motors generate magnetic fields whose mutual forces of attraction and repulsion are converted into motion. An electric motor can in principle also be operated as a generator, so that mechanical power is converted into electrical power.

A clutch arrangement in the context of this invention comprises at least one clutch. A clutch arrangement can have further components, such as an actuation system, which can also be referred to as a release system, or mechanical connection elements for integrating and coupling the clutch, for example within a hybrid module.

The clutch, also referred to as a separating clutch, preferably has a clutch disc, a pressure plate and a counter-plate.

A clutch has the function of interrupting or closing a torque flow within a drive train of a motor vehicle at a defined position in a switchable manner. For example, by means of a clutch, a driving engine side in a drive train of a motor vehicle can be shiftably coupled or uncoupled from the transmission side and thus, for example, enable a gear change of the transmission while driving and thereby be able to operate the driving motor in a preferred speed / torque range. Clutches can in particular also be used to couple or disengage an electric motor and / or internal combustion engine in the drive train within a hybridized drive train. Such clutches are often referred to as separating clutches.

The clutch disc is the central connecting element of the clutch system. Together with the pressure plate and the counter plate of the clutch, it forms a switchable friction system. When the clutch is engaged, the clutch disc is force-locked between the pressure plate and the counter plate. The clutch disc can have friction linings via which the frictional engagement can be established.

The function of the pressure plate within the clutch is to press the clutch disc against the counter plate and thus to bring about a switchable frictional connection between the pressure plate, the clutch disc and the counter plate. The pressure plate is in particular operatively connected to an actuation system, by means of which the pressure plate can be moved against the clutch disc or away from it, in particular axially in a translatory manner. The pressure plate can have friction linings, via which the frictional engagement can be established.

The counter plate provides a counter bearing for the pressure plate and the clutch disc. The counter plate is in particular axially fixed. However, it is also possible for the counter plate to be moved in the axial direction against the pressure plate during coupling. For this purpose, the counter-plate can also be operatively connected to the actuation system. The counter plate can have friction linings via which the frictional engagement can be established.

A hydraulic actuation system, also known as a release system, usually has a master cylinder that transmits the pressure generated on the master cylinder to the slave cylinder via a hydraulic pressure line

Occasionally the hydraulic pressure is also increased by means of a so-called Powerpacks provided, which consists of a hydraulic pump and a hydraulic pressure accumulator that can be acted upon by the hydraulic pump. Here, a pressure chamber of the slave cylinder can also be hydraulically pressurized, for example, by a master cylinder controlled by a control unit by means of an electric motor, or by a hydraulic pump, possibly with the assistance of a pressure accumulator. A so-called power pack can be used in an advantageous manner, which switches several pressure circuits via a particularly central hydraulic pump and corresponding valves.

By means of an axially displaceable piston, the slave cylinder transmits the hydraulic pressure to a lever system which is operatively connected to the clutch, so that an axial displacement of the piston causes the clutch to be actuated.

According to an advantageous embodiment of the invention it can be provided that the piston is formed in two parts from a circular disk-shaped piston cover and an annular disk-shaped piston ring receiving the piston cover. The advantage of this configuration is that the piston cover is used to assemble the actuation system is detachable from the piston ring in order to be able to intervene in the interior of the actuation system for assembly purposes. This will be explained in more detail later on the basis of the exemplary embodiments.

According to a further preferred further development of the invention, it can also be provided that the actuation system has a sleeve-shaped component which is arranged coaxially with and non-rotatably with an intermediate shaft designed as a hollow shaft, and the piston is mounted axially displaceably with respect to the sleeve-shaped component. It can thereby be achieved that the actuation system can be designed to be particularly easy to assemble, which can be seen from the following descriptions of the exemplary embodiments.

• Element, das einen axial feststehenden Zylinder für das Betätigungssystem bildet,
• Element, das den Kolben axial führt und/oder spezielle Führungselemente (z.B einen Führungsring) abstützt,
• Element, das die Kupplungsanordnung mit der Zwischenwelle und/oder dem E-Motor verbindet und insbesondere auch Axialkräfte, Radialkräfte, und/oder Drehmoment überträgt,
• Element, das einen Formschluss mit der Zwischenwelle ausbildet..

The element described as a sleeve-shaped component is, within the meaning of this patent, a component or an assembly that can fulfill all or part of the following functions:

• Element that forms an axially fixed cylinder for the actuation system,
• Element that guides the piston axially and / or supports special guide elements (e.g. a guide ring),
• Element that connects the clutch arrangement with the intermediate shaft and / or the electric motor and in particular also transmits axial forces, radial forces and / or torque,
• Element that forms a form fit with the intermediate shaft.

The intermediate shaft can, for example, be mounted coaxially rotatably on a transmission input shaft. In principle, each component that is non-rotatably and coaxially connected to the sleeve-shaped component can be referred to as an intermediate shaft. It is of course also possible for the intermediate shaft and the sleeve-shaped component to be formed in one piece.

Furthermore, according to a likewise advantageous embodiment of the invention, it can be provided that the actuation system has a pressure chamber which can be acted upon by a hydraulic fluid and which runs axially in a circular shape between the piston and the sleeve-shaped component, so that hydraulic pressure application of the pressure chamber with respect to an axial offset of the piston causes the sleeve-shaped component. The advantageous effect of this embodiment is based on the fact that the actuation system can be coupled to a hydraulic system that is already present in the drive train.

According to a further particularly preferred embodiment of the invention, it can be provided that the actuation system has a screw designed as a hollow shaft with an external thread, which can be screwed into a corresponding internal thread of the intermediate shaft, the screw having a screw head that rests against the sleeve-shaped component and / or engages in this so that the sleeve-shaped component is fixed with respect to the intermediate shaft at least in one axial direction, whereby in particular the ease of assembly of the clutch arrangement can be further improved.

Furthermore, the invention can also be further developed in such a way that the clutch is supported on the actuating system which is designed to rotate with it.

1. a) Bereitstellen einer insbesondere als Hohlwelle ausgeführten Zwischenwelle,
2. b) Koaxiale Positionierung eines insbesondere hülsenförmigen Bauteils zur Zwischenwelle und Herstellen einer drehfesten Verbindung zwischen dem insbesondere hülsenförmigen Bauteil und der Zwischenwelle mittels Formschlusses, insbesondere mittels einer Verzahnung,
3. c) Einschrauben einer Schraube in die Zwischenwelle zur axialen Sicherung des insbesondere hülsenförmigen Bauteils gegenüber der Zwischenwelle,
4. d) axial verschiebbare koaxiale Positionierung eines Kolbens zum insbesondere hülsenförmigen Bauteil.

The object of the invention is further achieved by a method for producing a hydraulic actuation system for a clutch arrangement, in particular according to one of claims 1-6, comprising the following steps:

1. a) Provision of an intermediate shaft designed in particular as a hollow shaft,
2. b) Coaxial positioning of an in particular sleeve-shaped component to the intermediate shaft and production of a non-rotatable connection between the in particular sleeve-shaped component and the intermediate shaft by means of a form fit, in particular by means of a toothing,
3. c) screwing a screw into the intermediate shaft to axially secure the, in particular, sleeve-shaped component with respect to the intermediate shaft,
4. d) axially displaceable coaxial positioning of a piston relative to the particular sleeve-shaped component.

For the purposes of this patent, a toothing describes a torque-transmitting form-fitting connection contour.

In a first advantageous embodiment of the method, the piston is formed in one piece and is preferably operatively connected to the coupling by means of a bayonet connection, as a result of which a particularly assembly-friendly manufacturing method can be provided.

In an alternative embodiment of the invention, it can be provided that the piston has a piston ring and a piston cover closing the piston ring opening, the piston ring first being connected to the sleeve-shaped component and, after screwing in, the Screw the piston ring is closed with the piston cover.

1. a) Bereitstellung eines hydraulischen Betätigungssystems, insbesondere gebildet in einem Verfahren nach Anspruch 7, mit einem hülsenförmigen Bauteil,
2. b) Bereitstellung einer Kupplung, mit wenigstens einer Kupplungsscheibe, welche radial und axial zwischen einer Anpressplatte und einer der Anpressplatte axial gegenüberliegenden Gegenplatte, wobei die Gegenplatte mit einem Kupplungsdeckel verbunden ist,
3. c) Anbindung der Kupplung an das hydraulische Betätigungssystem, indem eine drehfeste Verbindung zwischen dem Kupplungsdeckel und dem hülsförmigen Bauteil hergestellt wird, welche bevorzugt als Nietverbindung ausgebildet ist

Finally, the object of the invention is also achieved by a method for producing a clutch arrangement, in particular a clutch arrangement according to one of claims 1-6, comprising the following steps:

1. a) Provision of a hydraulic actuation system, in particular formed in a method according to claim 7, with a sleeve-shaped component,
2. b) Provision of a clutch with at least one clutch disc which is radially and axially positioned between a pressure plate and a counter plate axially opposite the pressure plate, the counter plate being connected to a clutch cover,
3. c) Connection of the clutch to the hydraulic actuation system by producing a non-rotatable connection between the clutch cover and the sleeve-shaped component, which connection is preferably designed as a riveted connection

The invention is explained in more detail below with reference to figures without restricting the general inventive concept.

• 1 eine erste Ausführungsform einer erfindungsgemäßen Kupplungsanordnung in einer schematischen Querschnittsansicht,
• 2 eine zweite Ausführungsform einer erfindungsgemäßen Kupplungsanordnung in einer schematischen Querschnittsansicht,
• 3 eine dritte Ausführungsform einer erfindungsgemäßen Kupplungsanordnung in einer schematischen Querschnittsansicht
• 4 eine vierte Ausführungsform einer erfindungsgemäßen Kupplungsanordnung in einer schematischen Querschnittsansicht,
• 5 eine perspektivische Detail-Teilschnittansicht einer Bajonettverbindung aus 4, und
• 6 ein Kraftfahrzeug mit einer erfindungsgemäßen Kupplungsanordnung in einer schematischen Blockschaltansicht.

Show it:

• 1 a first embodiment of a clutch arrangement according to the invention in a schematic cross-sectional view,
• 2 a second embodiment of a clutch arrangement according to the invention in a schematic cross-sectional view,
• 3 a third embodiment of a clutch arrangement according to the invention in a schematic cross-sectional view
• 4th a fourth embodiment of a clutch arrangement according to the invention in a schematic cross-sectional view,
• 5 a perspective detail partial sectional view of a bayonet connection from 4th , and
• 6th a motor vehicle with a clutch arrangement according to the invention in a schematic block diagram.

The figure shows a first embodiment of a coupling arrangement 1 , especially for coupling an electric motor 2 and / or an internal combustion engine 3 with the drive train 4th of a motor vehicle 5 , in particular by means of a hybrid module, as it is in the 5 is shown.

The clutch assembly 1 includes a clutch 6th with at least one clutch disc 7th which radially and axially between a pressure plate 8th and one of the pressure plate 8th axially opposite counter plate 10 is arranged so that by a relative axial offset of the clutch disc 7th and pressure plate 8th against the counter plate 10 a frictional connection can be established between these components and thus a torque between the clutch disc 7th and the pressure plate 8th as well as counter plate 10 is transferable.

The coupling 6th is with an actuation system 18th operatively connected, by means of which the clutch 6th can be converted into an engaged and / or disengaged operating state. The hydraulic actuation system 18th has a coaxial to the coupling rotation axis 32 axially displaceable piston 26th with a circular face 31 on which mechanically so with the clutch 6th connected is that an axial displacement of the piston 26th actuation of the clutch 6th causes. The coupling 6th is on the rotating actuation system 18th supported.

In the illustrated embodiment of the 1 is the piston 26th in two parts from a circular disk-shaped piston cover 33 and one the piston cover 33 receiving annular disc-shaped piston ring 34 educated.

Of the 1 it is also easy to see that the actuation system 18th an intermediate shaft designed as a hollow shaft 20th and one coaxial with the intermediate shaft 20th arranged sleeve-shaped component 24 has, which rotatably with the intermediate shaft 20th connected, the piston 26th axially displaceable on the sleeve-shaped component 24 is stored

Like in the 1 also shown, the actuation system 18th one with a hydraulic fluid 35 pressurizable pressure space 36 on, which is circular axially between the piston 26th and the components located axially behind it, so that hydraulic pressure is applied to the pressure chamber 36 an axial offset of the piston 26th compared to the sleeve-shaped component 24 causes.

The actuation system 18th has a screw designed as a hollow shaft 25th with an external thread, which in a corresponding internal thread of the intermediate shaft 20th can be screwed in, the screw 25th a screw head 37 possesses, which is so on the sleeve-shaped component 24 rests and / or engages in this that the sleeve-shaped component 24 opposite the intermediate shaft 20th is fixed in at least one axial direction.

In the 1 is the internal combustion engine 3 indicated by an unspecified crankshaft flange. The torque of the Internal combustion engine 3 is on a torsional vibration damper 16 , which is designed as a two-mass flywheel (DMF) in the embodiment shown. Via the secondary side 15th of the torsional vibration damper 16 that has a spline 44 with the clutch disc 7th the clutch 6th connected, the torque is applied to the clutch 6th transferred and from there with the clutch closed 6th to the electric motor 2 , forwarded.

As already described above, the clutch is supported 6th on their operating system 18th off that firmly with the intermediate shaft 20th connected is. The intermediate shaft 20th is fixed to the rotor arm 21 connected or, as shown in this illustrated embodiment, in one piece with the rotor arm 21 executed. The intermediate shaft 20th is thus non-rotatably with the rotor of the electric motor 2 connected and is supported by the angular contact ball bearings 22nd together with the electric motor 2 on the partition wall fixed to the housing 23 supported.

Thus also the clutch 6th and its operating system 18th both fixed to the intermediate shaft 20th connected by the angular contact ball bearings 22nd rotatably mounted, axially and radially supported and centered. The torque of the electric motor 2 regardless of whether it is exclusively from the electric motor 2 or from the one with him through the closed clutch 6th connected internal combustion engine 3 was generated by an unillustrated main torque transmission member 58 on the gearbox 19th transfer. The main torque transmission element 58 is with its drive side with the rotor of the electric motor 2 connected and with its output side to a unit that absorbs the torque of the drive module, for example the gearbox 19th .

In the embodiment of 1 is the main torque transmission element 58 indicated by two disc hubs of a double clutch, not shown. Therefore, two transmission input shafts are suitable for a double clutch 42 pictured.

The torque can always be transmitted in both directions via the path described here. For example, the electric motor can 2 Transferring torque to the internal combustion engine (e.g. to start the internal combustion engine) and it is also possible to transfer torque from the gearbox to one or both drive motors (e.g. to recuperate or to use the engine drag torque as an engine braking function).

The hydraulic actuation system 18th is on that of the gearbox 19th groundbreaking end of the intermediate shaft 20th attached. There is also a sleeve-like component 24 of the actuation system 18th on the intermediate shaft 20th plugged on, and rotatably fixed to the intermediate shaft by a [form-fitting connection contour in the form of a spline] 20th tied together. In addition, the sleeve-shaped component is 24 axially on the intermediate shaft 20th fixed. The intermediate shaft, which is designed as a hollow shaft, has for this purpose 20th at her of transmission 19th The pioneering end on the inner diameter has a threaded section into which a screw 25th is screwed in, the head of which is on the axial gearbox 19th remote end of the intermediate shaft 20th protrudes radially outward and axially on the sleeve-shaped component 24 of the actuation system 18th supports.

Through this screw 25th becomes the sleeve-shaped component 24 axially against an unspecified recess of the intermediate shaft 20th pressed and so axially on the intermediate shaft 20th fixed. The actuation system 18th is not only used for the clutch 6th to open and close, but also as a fastening element on which all axially fixed components of the coupling 6th be attached directly or indirectly. The counter plate 10 the clutch 6th is directly with the sleeve-shaped component 24 of the actuating element 18th tied together.

On the other hand, there is the sleeve-shaped component 24 also as the hydraulic cylinder of the actuation system 18th executed. For this purpose, the sleeve-shaped component 24 at his from the transmission 19th leading end to two radially outwardly open circumferential grooves in which a piston seal 38 and a guide ring 39 for the piston 26th are inserted. Via this area of the sleeve-shaped component, which is designed as a hydraulic cylinder 24 is a piston ring designed as a sheet metal part 34 put over, which is extended radially outward and in a pressure piece 45 passes that on the pressure plate 8th is applied. Becomes the pressure of the hydraulic fluid 35 in the printing room 36 of the hydraulic cylinder is increased, this is increased by the hydraulic fluid 35 axially from the sleeve-shaped component 24 pushed away. The piston 26th moves away from the intermediate shaft 20th and the transmission 10 in the axial direction and presses the pressure plate 8th against the clutch disc 7th , making the clutch disc 7th between the pressure plate 8th and the counter plate 10 is frictionally clamped. This allows torque from the clutch 6th are transmitted by a frictional connection on the friction surfaces between the linings of the clutch disc 7th and the friction surfaces of the pressure plate 8th as well as the counter plate 10 arises.

The hydraulic fluid 35 is in this case on the intermediate shaft 20th attached rotating actuation system 18th through a longitudinal hole 41 in the transmission input shaft 42 fed into the hydraulic cylinder. This is in the gearbox 19th a rotary feedthrough for the hydraulic fluid 35 present (not shown) through which the hydraulic fluid 35 from a system providing the hydraulic pressure (e.g. a pump, a piston, a pressure accumulator or a power pack) into the rotatably mounted transmission input shaft and from there into the intermediate shaft rotatably mounted at differential speed 20th can be directed. Such a rotary feedthrough is found in most gearboxes 19th with torque converter or wet double clutch already available or can easily be added accordingly.

The transmission input shaft 42 (in the case of double clutch transmissions as in the illustrated embodiment of 1 the inner transmission input shaft 42 ) is in the intermediate shaft 20th stored. The hydraulic fluid 35 , which through the longitudinal hole 41 in the transmission input shaft 42 flows, steps on the gearbox 19th facing away from the end face of the transmission input shaft 42 and so enters the intermediate shaft, which is also designed as a hollow shaft 20th . The screw 25th , which is the sleeve-shaped component 24 axially on the intermediate shaft 20th fixed, also has a central longitudinal bore, so that the hydraulic fluid 35 through the screw 25th through into the pressure chamber 36 can flow. So that the hydraulic fluid 35 cannot escape at an unwanted point between these components is not just a piston seal 38 between the sleeve-shaped component 24 and the piston 26th provided, but also a seal 52 between the sleeve-shaped component 24 and the intermediate shaft 20th . Furthermore, there is between the intermediate shaft, which sometimes rotates at different speeds 20th and transmission input shaft 42 a mechanical seal 40 available.

The static seal 52 between the sleeve-shaped component 24 and the intermediate shaft 20th is with the in 1 The embodiment shown is designed as an O-ring, which is inserted into a groove in the sleeve-shaped component 24 is inserted and on a cylindrical outer surface of the intermediate shaft 20th works. This seal 52 must provide a high and reliable sealing effect, since hydraulic fluid leaks 35 at this point would lead to hydraulic fluid 35 in the housing of the coupling 6th and the torsional vibration damper 16 would arrive. In order to have the option of running these two components dry, which is the most energy-efficient variant for both components, the actuation system must 18th the clutch 6th be designed so that there is no leakage into the housing of these two components.

The seal 40 between the intermediate shaft 20th and the transmission input shaft 42 is designed as a mechanical seal. In the exemplary embodiment shown, the sliding ring is located in a circumferential groove on the transmission input shaft 42 and acts on an inner cylindrical jacket surface in the intermediate shaft 20th . The mechanical seal 40 has the advantage that it can seal high pressure differences such as those between the hydraulic fluid 35 in the printing room 36 of the actuation system 18th and the interior of the housing of the electric motor 2 occur and at the same time the rotary movement between the intermediate shaft 20th and the transmission input shaft 42 allows. The mechanical seal 40 However, in practice it is not completely leak-free and for the necessary service life of the seal 40 to enable and no high drag torque on the seal 40 a slight leakage is even necessary to cause. Because the leakage that occurs on the mechanical seal 40 occurs, but between the intermediate shaft 20th and the transmission input shaft 42 passes through into the electric motor housing, in which the oil-cooled electric motor is located 2 and the wet main torque transmission element is located, a small leakage at this point is not a problem if the same hydraulic fluid is used 35 as the hydraulic fluid of the actuation system 18th and as a coolant for the electric motor 2 and the main torque transmitting element perishes. With a suitable oil, this is usually the technically best and most economical solution.

The main components of the clutch 6th are as already mentioned - the counter plate 10 who have favourited clutch disc 7th , the pressure plate 8th and the leaf springs 46 . This will now be explained in more detail. The counter plate 10 forms the axially fixed friction surface of the clutch 6th off and is over the clutch cover 29 and the sleeve-shaped component 24 of the actuation system 18th axially and non-rotatably with the intermediate shaft 20th and the electric motor 2 tied together. The clutch disc 7th is via a spline 44 with the torsional vibration damper 16 connected and can with its one end face forming a friction surface on the counter plate 10 issue. On the counter plate 10 opposite side of the clutch disc 7th is the pressure plate 8th arranged. The pressure plate 8th is non-rotatable but axially displaceable to a limited extent with the clutch cover 29 and / or the counter plate 10 connected and can through the actuation system 18th for the purpose of torque transmission against the clutch disc 7th be pressed. This non-rotatable but axially displaceable connection between the pressure plate 8th and the axially fixed coupling components such as the counter plate 10 and clutch cover 29 is sensibly implemented using elastic elements. In the in 1 The embodiment shown are therefore leaf springs 46 between the pressure plate 8th and the clutch cover 29 arranged. It makes sense to distribute several leaf springs or leaf spring packages around the circumference and one end of each leaf spring 46 on the pressure plate 8th and the other end on the clutch cover 29 attached. Instead of the leaf springs 46 The leaf springs can be arranged behind the friction surface as seen in the axial direction 46 can also be placed radially outside or inside the friction surface.

The coupling 6th and the actuation system 18th can be installed in the drive module housing before the two systems are installed 53 or in the unspecified motor housing of the electric motor 2 be connected to a testable sub-assembly. For this purpose, in the embodiment of 2 a mounting interface between the coupling 6th and the actuation system 18th intended. This assembly interface is a riveted connection 47 executed, which through a corresponding opening in the pressure piece 45 is attainable. Other connection methods such as screwing or welding are also possible as an alternative.

To the sub-assembly from coupling 6th and actuation system 18th with the electric motor 2 or the intermediate shaft 20th to connect, the sleeve-shaped component 24 on a spline contour 57 the intermediate shaft 20th attached and against an axial stop on the intermediate shaft 20th pushed. Then we the screw 25th with the central hole through which the actuation system operates 18th the hydraulic fluid 35 can flow into the intermediate shaft 20th screwed in and the sleeve-shaped component 24 so permanently axially against the stop on the intermediate shaft 20th pressed. So that this screw 25th that can be mounted and tightened is the piston 26th designed in two parts and has a piston ring 34 with an opening through a piston cover 33 is lockable. The piston ring 34 points on its face 31 one from a piston cap 33 lockable opening through which the screw 25th and the necessary tools to tighten the screw 25th can be inserted through. If the screw 25th is tightened and the tool has been removed, this opening will be in the piston ring 34 through the piston cover 33 sealed pressure-tight.

For this purpose, in the exemplary embodiments shown, a thread and a sealing surface are provided on the edge of the opening, so that the piston cover 33 into the opening of the piston ring 34 can be screwed in and sealed pressure-tight. A seal is required to ensure tightness 43 between the piston cover 33 and the piston ring 34 arranged.

In the embodiment of 1 is an axially pressed flat gasket 43 between the piston cover 33 and the piston ring 34 intended. When the piston cover 33 is mounted, forms the assembly of pistons 26th and piston cover 33 in interaction with the sleeve-shaped component 24 and the intermediate shaft 20th and transmission input shaft 42 a closed pressure chamber into which the hydraulic fluid 35 can be introduced to the piston 26th to move axially.

3 shows an embodiment of the clutch assembly 1 with an actuation system 18th with a concentrically arranged rotating piston 26th , which is particularly suitable for installation spaces in which there is very little axial space radially on the inside. Because the basic principle of operation of the clutch 6th and the clutch actuation system 18th at the in 3 The version shown is identical to that of the 1 and 2 only the details that differ are described below.

The connection between the intermediate shaft 20th and the sleeve-shaped component 24 of the actuation system 18th is here via a Hirth serration 48 realized. The Hirth coupling 48 is on the face of the intermediate shaft 20th from the screw 25th on the intermediate shaft 20th axially braced and enables a backlash-free connection with the sleeve-shaped component 24 . The Hirth toothing 48 is an axially very short form-fitting connection that can transmit high torques. Another reason for the short axial construction of this embodiment of the actuation system 18th is that the cylindrical surface of the piston 26th on which the piston seal 38 slides along, radially above the through the angular contact ball bearings 22nd the intermediate shaft 20th resulting axial constriction was arranged.

4th Figure 3 shows another embodiment of a clutch actuation system 18th where the piston 26th is made particularly short in the axial direction. The piston 26th can be made particularly short in the embodiment of the invention shown, since the piston seal 38 and the guide ring 39 were not arranged axially one behind the other, as in the previous exemplary embodiments, but radially one above the other by placing them on two different cylindrical surfaces with different diameters of the piston 26th works. The other reason for the short design is that the piston is made in one piece 26th does not have to have a resealable opening and therefore a two-part construction of the piston 26th as is not necessary in the previous exemplary embodiments.

The piston 26th is in the embodiment of 4th with the tension element 50 the clutch 6th via a bayonet connection 51 tied together. This allows the whole piston 26th for the assembly or disassembly of the tension element 50 be separated and from the sleeve-shaped component 24 subtracted from. Became the piston 26th removed, the central fastening screw 25th inside the intermediate shaft 20th easily reach. If the screw 25th has been tightened, you can see the plunger 16 back onto the sleeve-shaped component 24 and over the bayonet connection 51 the power transmission of the piston 26th on the tension element 50 enable.

In the 5 Figure 3 is a cutaway perspective view of the bayonet joint 51 shown, on the basis of which the mode of operation is explained in more detail. The one in the 5 Bayonet connection shown 51 between pistons 26th and tension element 50 enables, as described above, simple assembly and disassembly of the piston 26th . This can be done when the clutch 6th and the rest of the actuation system 18th already connected to the hybrid module and on the intermediate shaft 20th is screwed.

The upper figure a the 5 shows the bayonet connection 51 in a hinged operating position and the lower figure b of 5 in the mounting position.

The piston 26th is carried out in a first assembly step, which is shown in the figure below 5 is shown on the sleeve-shaped component 24 placed and pushed into its axially rear end position. The bayonet contour of the piston is thereby 26th aligned so that it passes through the bayonet contour of the tension element 50 can be pushed through. The in 5 b embodiment shown this means that the eyelets 54 of the piston 26th aligned in the circumferential direction so that they are in front of the gaps between the hooks 55 of the tension element 50 are located. The piston 26th can then be pushed into its rear end position, which is good from the synopsis of 4th with 5 becomes apparent.

The tension element 50 is then pulled forward. In the 5 this corresponds to a movement of the tension element 50 along the coupling rotation axis 32 to the left. The one in the 4th shown pressed clutch 6th will be opened. To the tension element 50 Pull it forward for assembly, for example between the outer fastening straps 56 on the outer diameter of the annular section of the tension element 50 be packed.

When the tension element 50 was pulled forward until the tips of the hooks 55 axially in front of the area of the piston 26th attached eyelets 54 is located, the piston 26th twisted in the circumferential direction until the eyelets 54 in the axial direction directly in front of the heel 55 of the tension element 50 are located. Then the tension element 50 on the piston 26th be dropped off; be discontinued; be deducted; be dismissed. The hook 55 of the tension element 50 reach into the eyelets 54 on the piston 26th and thus enable the axial power transmission between pistons 26th and tension element 50 and at the same time prevent unwanted rotation of the piston 26th and thus an unintentional unhooking of the bayonet contour. This operating state of the bayonet connection 51 is in figure a the 5 reproduced.

The tension element can be used for dismantling 50 be pulled forward again so that the plunger 26th twisted and from the sleeve-shaped component 24 can be deducted.

1. a) Bereitstellen einer insbesondere als Hohlwelle ausgeführten Zwischenwelle 20,
2. b) Koaxiale Positionierung eines insbesondere hülsenförmigen Bauteils 24 zur Zwischenwelle 20 und Herstellen einer drehfesten Verbindung zwischen dem insbesondere hülsenförmigen Bauteil 24 und der Zwischenwelle 20 mittels einer Verzahnung 48, 57,
3. c) Einschrauben einer Schraube 25 in die Zwischenwelle 20 zur axialen Sicherung des insbesondere hülsenförmigen Bauteils 24 gegenüber der Zwischenwelle 20,
4. d) axial verschiebbare koaxiale Positionierung eines Kolbens 26 zum insbesondere hülsenförmigen Bauteil 24,
5. e) Verschließen der Ringöffnung des Kolbenrings 34 mit einem Kolbendeckel 33.

In summary, a method for manufacturing a hydraulic actuation system 18th for a clutch assembly 1 , thus include the following steps:

1. a) Provision of an intermediate shaft designed in particular as a hollow shaft 20th ,
2. b) Coaxial positioning of a particularly sleeve-shaped component 24 to the intermediate shaft 20th and producing a non-rotatable connection between the, in particular, sleeve-shaped component 24 and the intermediate shaft 20th by means of a toothing 48 , 57 ,
3. c) screwing in a screw 25th in the intermediate shaft 20th for axially securing the, in particular, sleeve-shaped component 24 opposite the intermediate shaft 20th ,
4. d) axially displaceable coaxial positioning of a piston 26th to the particular sleeve-shaped component 24 ,
5. e) closing the ring opening of the piston ring 34 with a piston cap 33 .

The piston 26th can be formed in one piece in a first embodiment of the manufacturing process and preferably by means of a bayonet connection 51 with the clutch 6th are operatively connected, as in the embodiment of 4th and 5 is shown.

Alternatively, in a second embodiment of the manufacturing method, the piston 26th a piston ring 34 and a piston cover which closes the piston ring opening 33 have, first of all the piston ring 34 with the sleeve-shaped component 24 is connected and after screwing in the screw 25th the piston ring 34 with the piston cover 33 is locked. This has been done in the embodiments of 1-3 shown.

1. a) Bereitstellung eines hydraulischen Betätigungssystems 18, insbesondere gebildet in einem Verfahren nach Anspruch 7, mit einem hülsenförmigen Bauteil 24,
2. b) Bereitstellung einer Kupplung 6, mit wenigstens einer Kupplungsscheibe 7, welche radial und axial zwischen einer Anpressplatte 8 und einer der Anpressplatte 9 axial gegenüberliegenden Gegenplatte 10, wobei die Gegenplatte 10 mit einem Kupplungsdeckel 29 verbunden ist,
3. c) Anbindung der Kupplung 6 an das hydraulische Betätigungssystem 18, indem eine drehfeste Verbindung zwischen dem Kupplungsdeckel 29 und dem hülsförmigen Bauteil 14 hergestellt wird, welche bevorzugt als Nietverbindung 47 ausgebildet ist

Furthermore, a method for producing a clutch arrangement was described in the exemplary embodiments, which comprises the following steps:

1. a) Provision of a hydraulic actuation system 18th , in particular formed in a method according to claim 7, with a sleeve-shaped component 24 ,
2. b) Provision of a coupling 6th , with at least one clutch disc 7th which radially and axially between a pressure plate 8th and one of the pressure plate 9 axially opposite counterplate 10 , the counter plate 10 with a clutch cover 29 connected is,
3. c) Connection of the coupling 6th to the hydraulic actuation system 18th by creating a non-rotatable connection between the clutch cover 29 and the sleeve-shaped component 14 is produced, which is preferably a riveted connection 47 is trained

The directions of axial, radial, tangential and circumferential direction refer to the axis of rotation around which the motors and the coupling rotate.

The invention is not limited to the embodiments shown in the figures. The above description is therefore not to be regarded as restrictive, but rather as explanatory. The following claims are to be understood in such a way that a named feature is present in at least one embodiment of the invention. This does not exclude the presence of further features. If the patent claims and the above description define “first” and “second” features, this designation serves to distinguish between two similar features without defining an order of precedence.

List of reference symbols

1

Clutch assembly

2

Electric motor

3

Internal combustion engine

4th

Powertrain

5

Motor vehicle

6th

coupling

7th

Clutch disc

8th

Pressure plate

10

Counter plate

15th

Secondary side

16

Torsional vibration damper

17th

Liaison

18th

Actuation system

19th

transmission

20th

Intermediate shaft

21

Rotor arm

22nd

Angular contact ball bearings

23

Partition

24

sleeve-shaped component

25th

screw

26th

Pistons

29

Clutch cover

31

Face

32

Coupling rotation axis

33

Piston cover

34

Piston ring

35

Hydraulic fluid

36

Printing room

37

Screw head

38

Piston seal

39

Guide ring

40

Mechanical seal

41

Longitudinal bore

42

Transmission input shaft

43

poetry

44

Splines

45

Pressure piece

46

Leaf springs

47

Riveted connection

48

Hirth serration

49

O-ring

50

Tension element

51

Bayonet connection

52

poetry

53

Hybrid module housing

54

Eyelets

55

hook

56

Tabs

57

Gearing

58

Main torque transmission element

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• EP 0773127 A1 [0002]
• DE 10018926 A1 [0002]
• US 2007/0175726 A1 [0002]

Claims (10)

Clutch arrangement (1), in particular for coupling an electric motor (2) and / or an internal combustion engine (3) to the drive train (4) of a motor vehicle (5), in particular by means of a hybrid module, comprising a clutch (6) with at least one clutch disc (7) ), which is arranged radially and axially between a pressure plate (8) and a counter-plate (10) axially opposite the pressure plate (8), so that a relative axial offset of the clutch disc (7) and / or pressure plate (8) and / or Counterplate (10) a frictional connection can be produced between these components and a torque can thus be transmitted between the clutch disc (7) and the pressure plate (8) and counterplate (10), the clutch (6) being operatively connected to an actuation system (18) by means of the clutch (6) of which can be transferred into an engaged and / or disengaged operating state, characterized in that the, in particular, hydraulic actuation system (18) has a coaxially to the coupling rotation axis (32) axially displaceable piston (26) with a circular end face (31) which is mechanically connected to the coupling (6) so that an axial displacement of the piston (26) actuation of the coupling (6) causes. Coupling arrangement (1), according to Claim 1 , characterized in that the piston (26) is formed in two parts from a circular disk-shaped piston cover (33) and an annular disk-shaped piston ring (34) receiving the piston cover (33). Clutch arrangement (1) according to one of the preceding claims, characterized in that the actuation system (18) has a sleeve-shaped component (24) which is arranged coaxially with and non-rotatably with an intermediate shaft (20) designed as a hollow shaft, and the piston (26) ) is mounted axially displaceably with respect to the sleeve-shaped component (24). Clutch arrangement (1) according to one of the preceding claims, characterized in that the actuation system (18) has a pressure chamber (36) which can be acted upon by a hydraulic fluid (35) and which is circular axially between the piston (26) and the sleeve-shaped component (24) runs, so that hydraulic pressurization of the pressure chamber (36) causes an axial offset of the piston (26) with respect to the sleeve-shaped component (24). Coupling arrangement (1) according to one of the preceding claims, characterized in that the actuation system (18) has a screw (25) designed as a hollow shaft with an external thread which can be screwed into a corresponding internal thread of the intermediate shaft (20), the screw ( 25) has a screw head (37) which rests against and / or engages the sleeve-shaped component (24) in such a way that the sleeve-shaped component (24) is fixed with respect to the intermediate shaft (20) at least in one axial direction. Clutch arrangement (1) according to one of the preceding claims, characterized in that the clutch (6) is supported on the actuating system (18) which is designed to rotate with it. Method for producing a hydraulic actuation system (18) for a clutch arrangement (1), in particular according to one of the preceding claims, comprising the following steps: a) Provision of an intermediate shaft (20) designed in particular as a hollow shaft, b) Coaxial positioning of an in particular sleeve-shaped component (24) to the intermediate shaft (20) and production of a non-rotatable connection between the in particular sleeve-shaped component (24) and the intermediate shaft (20) by means of a form fit, in particular by means of a toothing (48, 57), c) screwing a screw (25) into the intermediate shaft (20) for axially securing the, in particular, sleeve-shaped component (24) with respect to the intermediate shaft (20), d) axially displaceable coaxial positioning of a piston (26) in relation to the, in particular, sleeve-shaped component (24), e) closing the ring opening of the piston ring (34) with a piston cover (33). Procedure according to Claim 7 , characterized in that the piston (26) is formed in one piece and is preferably operatively connected to the coupling (6) by means of a bayonet connection (51). Procedure according to Claim 7 , characterized in that the piston (26) has a piston ring (34) and a piston cover (33) closing the piston ring opening, the piston ring (34) first being connected to the sleeve-shaped component (24) and after screwing in the screw (25 ) the piston ring (34) is closed with the piston cover (33). A method for producing a clutch assembly (1), in particular a clutch assembly (1) according to one of the Claims 1 - 6th , comprising the following steps: a) providing a hydraulic actuation system (18), in particular formed in a method according to Claim 7 , with a sleeve-shaped component (24), b) Provision of a clutch (6), with at least one clutch disc (7), which radially and axially between a pressure plate (8) and a counter-plate (10) axially opposite the pressure plate (9), the counter-plate (10) having a clutch cover (29) is connected, c) connection of the clutch (6) to the hydraulic actuation system (18) by establishing a non-rotatable connection between the clutch cover (29) and the sleeve-shaped component (14), which is preferably designed as a riveted connection (47) is

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