DE102008042569A1 - Dual clutch system for use in utility vehicle, has actuation arrangement including pressurized air regulating arrangements for regulating actuation of coupling regions based on pressurized air existing in piston components - Google Patents

Abstract

The system (10) has an actuation arrangement (14) including pressurized air-slave cylinder/piston components (46, 52) in association to force-exerting arrangements (38, 48). The piston components generate actuating force acting against force of the force-exerting arrangements. The actuation arrangement includes pressurized air regulating arrangements for regulating the actuation of coupling regions (16, 18) based on pressurized air existing in the piston components. The coupling regions works together with the force-exerting arrangements.

Description

The The present invention relates to a dual clutch assembly comprising a first clutch portion having a first clutch disk assembly and a first pressure plate, a second coupling region with a second clutch disk assembly and a second pressure plate, an intermediate plate between the two clutch disc assemblies, a housing assembly connected to the intermediate bearing plate, wherein the first Pressure plate and the first clutch disc assembly on one first axial side of the intermediate plate are arranged and the second Pressure plate and the second clutch disc and the housing assembly are arranged on a second axial side of the intermediate plate, a first Kraftbeaufschlagungsanordnung, via which an actuating force on the first pressure plate is leitbar, wherein the first Kraftbeaufschlagungsanordnung axially overlaps the second coupling portion and the intermediate plate and a respect the housing arrangement abgestütztes first Kraftbeaufschlagungselement comprises, a second Kraftbeaufschlagungsanordnung, over which an actuating force on the second pressure plate is leitbar, wherein the second Kraftbeaufschlagungsanordnung a in terms of the housing arrangement supported second Kraftbeaufschlagungselement includes.

at Such dual clutch assemblies, wherein the coupling portions generally designed as dry running coupling areas There is a need to include the two coupling areas Execution of gear shifts for engaging and disengaging defined to operate coordinated. On this way it becomes possible a substantially traction-free switching between individual To reach the gear steps. To this tuning of the actuation operations at To achieve the two coupling areas, it is necessary information about to obtain the respective setting state and in feedback with this information then the operation to trigger the clutch or perform. These are in association with different at the operation itself Moving organs generally motion sensors available, the capture the movement or instantaneous positioning of these organs and provide appropriate signals.

It The object of the present invention is a dual clutch assembly provide, which in a simplified structure precise operation of the Clutch areas allows the same.

According to the invention this Task solved by a dual clutch assembly comprising a first clutch region with a first clutch disk assembly and a first pressure plate, a second clutch area with a second clutch disk assembly and a second pressure plate, an intermediate plate between the two clutch disc assemblies, one with the intermediate bearing plate connected housing arrangement, wherein the first pressure plate and the first clutch plate assembly are arranged on a first axial side of the intermediate plate and the second pressure plate and the second clutch disc and the housing arrangement are arranged on a second axial side of the intermediate plate, a first Kraftbeaufschlagungsanordnung, via which an actuating force on the first pressure plate is leitbar, wherein the first Kraftbeaufschlagungsanordnung axially overlaps the second coupling portion and the intermediate plate and a respect the housing arrangement abgestütztes first Kraftbeaufschlagungselement comprises, a second Kraftbeaufschlagungsanordnung, over which an actuating force on the second pressure plate is leitbar, wherein the second Kraftbeaufschlagungsanordnung a respect the housing arrangement abgestütztes second Kraftbeaufschlagungselement comprises, wherein at least one Kraftbeaufschlagungsanordnung of first Kraftbeaufschlagungsanordnung and second Kraftbeaufschlagungsanordnung a the assigned Coupling area in the direction of engagement or dislocation burdening Force with respect to the actuation path steadily increasing or steadily decreasing force characteristic generates, a Pressurized fluid actuator assembly, the at least in association with the at least one Kraftbeaufschlagungsanordnung a pressurized fluid slave cylinder / piston assembly for generating one of the force of this Kraftbeaufschlagungsanordnung counteracting Actuating force, wherein the pressurized fluid actuator assembly a fluid pressure regulating arrangement for controlling the actuation of the cooperating with the at least one Kraftbeaufschlagungsanordnung Clutch range based on the in this pressurized fluid slave cylinder / piston assembly prevailing fluid pressure.

The dual-clutch arrangement according to the invention uses in at least one of the clutch areas the fact that there is a defined relationship between the actuating force generated by an actuating arrangement and the counterforce generated by the force application arrangement, which in turn is in defined relation to the operating state of the clutch area when the force generated by the force application arrangement has steadily rising or falling steadily, that is, has a clear relationship between the actuation force and the actuation state or the control state of a respective coupling region. This unique relationship can be exploited to provide information about the actuator by sensing the fluid pressure in a pressurized fluid slave cylinder / piston assembly stand of the clutch provide based on this information then defined to be able to influence the pressure conditions and thus to be able to actuate the clutch area accordingly.

The at least one Kraftbeaufschlagungsanordnung can a diaphragm spring-like Comprise biasing element. Alternatively or additionally, it may be provided that the at least one Kraftbeaufschlagungsanordnung at least a helical biasing spring element comprises.

Especially in combination of a diaphragm spring-like biasing element, for example only a comparatively small own strength supplies and more or less than power transmission lever serves, with a helical spring biasing element, it is easy possible, to provide a Kraftbeaufschlagungsanordnung that a steady Force curve between fully engaged and fully disengaged positioning has.

Further Is it possible, that the at least one Kraftbeaufschlagungsanordnung further at least another diaphragm spring-like biasing element comprises, for example in cooperation with a present as the main spring diaphragm spring-like Preload element again provides a steady force characteristic. You can do this the two diaphragm spring-like biasing elements are formed or be installed over that actuating mutually offset characteristics have, in summary then one over the entire actuation path steady course.

Around based on the prevailing fluid pressure conditions the control state of a To be able to influence the coupling range is further proposed that the pressurized fluid actuator assembly in association with the at least one pressurized fluid slave cylinder / piston assembly a pressurized fluid source, a connection between the source of pressurized fluid and a cylinder space of the at least one pressure fluid slave cylinder / piston assembly optionally producing and interrupting valve arrangement as well in the flow path between the valve assembly and the cylinder chamber a fluid pressure regulator includes.

there can be provided to achieve a very space-saving arrangement be that the pressurized fluid actuator assembly a radially outer first Pressure fluid slave cylinder / piston assembly in cooperation with the first Kraftbeaufschlagungsanordnung and a radially inner second pressurized fluid slave cylinder / piston assembly in cooperation comprising the second Kraftbeaufschlagungsanordnung.

In front especially when such a dual clutch assembly is used in commercial vehicles, it is particularly advantageous if the pressurized fluid is compressed air is. In commercial vehicles, compressed air is generally used, to different system areas, such. B. a parking brake, to press. This compressed air is provided by compressors, which in general be driven by a power take-off of an internal combustion engine, so no extra activities for generating or providing the pressure fluid then used Compressed air is required.

The The present invention will be described below with reference to the accompanying drawings Figures detailed. It shows:

1 a partial longitudinal sectional view of a dual clutch assembly;

2 Plotted on the Einrückweg required in a clutch of the normal-open type engaging force with steadily increasing course;

3 applied over the Ausrückweg the required in a normal-closed clutch release force with steady characteristic;

4 in principle, a compressed air supply system for the actuation of the two coupling portions of a dual clutch assembly.

The 1 shows in a partial longitudinal sectional view of a generally with 10 designated dual-clutch assembly, the essential system areas a double clutch 12 and an actuator assembly 14 includes. The double clutch 12 includes two coupling areas 16 . 18 , A first coupling region, which is generally to be positioned on the motor side, comprises a pressure plate 20 and a clutch disk assembly 22 , the radially outer friction region 24 between the pressure plate 20 and an intermediate plate 26 is positioned and clamped. The intermediate plate 26 in turn, by means of a connecting plate 28 or the like to a drive shaft, for example, the crankshaft of an internal combustion engine, are connected for rotation with this about a rotation axis A.

The second coupling area 18 includes a second pressure plate 30 and a second clutch disk assembly 32 , with their radially outer friction area 34 between the second pressure plate 30 and the intermediate plate 26 is positioned and clamped.

The two clutch disc assemblies 22 . 32 are connected to the two mutually coaxial input shafts of a double shaft gear, for example via splines or the like for common rotation about the axis of rotation A.

With the intermediate plate 26 is at the motor facing away or gear facing side to be positioned a housing 36 connected. The second clutch disk assembly 32 , the second pressure plate 30 and the case 36 lie on a gear facing to be positioned sides with respect to the intermediate plate 26 while the first clutch disk assembly 22 and the first pressure plate 20 on the motor facing to positio nierenden side of the intermediate plate 26 lie.

A first Kraftbeaufschlagungsanordnung 38 for the first coupling area 26 includes an actuating ring 40 that's outside the case 28 is positioned. A majority of with the actuating ring 38 on the one hand and the first pressure plate 20 on the other hand axially fixed, bolt-like actuators 42 passes through corresponding openings in the housing 36 or the intermediate plate 26 to make sure that the first pressure plate 20 together with the actuating ring 40 axially with respect to the intermediate plate 26 is movable. A as Kraftbeaufschlagungselement the first Kraftbeaufschlagungsanordnung 38 effective diaphragm spring 44 is on the outside of the case 36 with respect to this and radially further outward with respect to the actuating ring 40 supported. By a first compressed air slave cylinder / piston assembly 46 may be the radially inner end portion of the first diaphragm spring 44 axially moved or loaded, thus also taking advantage of the first diaphragm spring through this 44 provided leverage the actuator ring 40 and with this the first pressure plate 20 to move. It should be noted here that in its radially outer region, the first diaphragm spring 44 with the actuating ring 40 axially fixedly coupled in both directions, for example by providing one of the outer circumference of the first diaphragm spring 44 receiving inner circumferential groove on the actuating ring 40 ,

A second Kraftbeaufschlagungsanordnung 48 for the second coupling region 18 comprises a diaphragm spring acting as a second force-applying element 50 , the radially outside the second pressure plate 30 loaded, radially further inwardly on the inside of the housing with respect to this axially supported and held and in its radially inner end region by a second compressed-air slave cylinder / piston assembly 52 the compressed air actuator assembly 14 axially resilient. This second diaphragm spring 50 or the second Kraftbeaufschlagungsanordnung 48 can be designed such that they basically an engagement force on the second pressure plate 30 exerts, so that the second coupling area 18 is generally of the normal-closed type and by exerting a disengagement force by means of the second compressed air slave cylinder / piston assembly 52 and corresponding movement of the radially inner ends of the diaphragm spring tongues of the second diaphragm spring 50 towards the intermediate plate 26 to the second clutch area 18 can be adjusted in the direction of disengagement. For this purpose, the second pressure plate 30 For example, be associated with tangential leaf springs, on the one hand their rotational coupling to the housing 36 or the intermediate plate 26 realize, on the other hand, a release force for the pressure plate 30 produce.

One recognizes in the 1 in that in association with the second Kraftbeaufschlagungsanordnung 48 or the diaphragm spring 50 the same one or more distributed over the circumference helical compression springs 54 are provided. These support the diaphragm spring 50 in the generation of an engagement force, by their radially outer region in the direction of the second pressure plate 30 to squeeze. Depending on the design, it may be provided that the diaphragm spring 50 itself provides essentially no or only a small engagement force, so primarily the function of transmitting the actuation force of the actuator assembly 14 on the first coupling area 18 takes over, while the engagement force primarily by the helical compression springs 54 is delivered. By this characteristic or even when superimposing the diaphragm spring characteristic with the helical compression spring characteristic, a force-displacement diagram is obtainable, as in the 3 is shown. There is above the Ausrückweg between a fully engaged position e and a fully disengaged position a of the second coupling portion 18 the applied release force shown, which ultimately in Ausrückweg or a respective actuation position by the Kraftbeaufschlagungsanordnung 48 self-provided engagement force. The characteristic curve K1 therefore essentially also corresponds to the force characteristic curve of the force application arrangement 48 that, like this one 3 clearly shows, between the positions e and a steadily increasing. Thus, there is a clear connection between one through the Kraftbeaufschlagungsanordnung 48 generated engagement force or the oppositely acting release force and the positioning in Ausrückweg.

It should be noted here that a corresponding relationship can also be realized for a clutch or a coupling region of the normal-open type, as described with reference to FIG 2 is shown. Also there is above the actuation, here the Einrückweg, the engagement force applied, which by the actuator assembly 14 for example, in association with the first Kraftbe aufschlagungsanordnung 38 is to be delivered and thus by the first Kraftbeaufschlagungsanordnung 38 for example, provided and effective in the direction of disengagement equivalent force. Again, this force characteristic could be achieved by superimposing a diaphragm spring characteristic and a helical compression spring characteristic or substantially by a helical compression spring characteristic alone when the diaphragm spring 44 again essentially only a lever functionality should meet. It should be noted that in the 2 and 3 The characteristics shown, for example, are also obtainable by the superposition of the characteristic of two diaphragm springs, which are mutually supporting and shaped or installed so that they have mutually shifted characteristic curves over the respective actuating path.

With this clear relationship between the actuation path, the actuation force to be generated or in a respective positioning of the considered Kraftbeaufschlagungsanordnung 38 or 48 generated force in the direction of disengagement or in the direction of engagement, it becomes possible, a coupling region with such a force application arrangement 38 respectively. 48 in terms of its operation, taking into account the case of a respective compressed air slave cylinder / piston assembly 46 respectively. 52 existing air pressure in a respective cylinder chamber 56 respectively. 58 to regulate. A defined actuation position between the fully retracted positioning e and the fully disengaged positioning a requires a certain by the Kraftbeaufschlagungsanordnung 38 or 48 generated force and thus one by the associated compressed air slave cylinder / piston assembly 46 respectively. 52 generated counterforce and therefore one in each cylinder space 56 respectively. 58 prevailing air pressure. The setting or adjustment of a certain air pressure therefore also has the setting or adjustment of a certain operating position of the associated coupling range result. It can thus be dispensed with the use of displacement sensors, for example, in the field of actuator assembly 14 be provided, for example, to the respective positioning of a piston 60 respectively. 62 the compressed air slave cylinder / piston assemblies 46 respectively. 52 capture.

With reference to the 4 an example of a compressed air supply system is explained below, with which such a control or setting of an operating position can be achieved.

One recognizes there an internal combustion engine 76 , which also the entrance area of the double clutch 12 with their two only shown here in principle coupling ranges drives. A general with 78 designated and by the internal combustion engine 76 Powered compressor generates compressed air in an air tank 80 can be stored. The in the air tank 80 stored compressed air can be used in other compressed air consuming systems 82 be used. A pressure relief valve 84 ensures that the air pressure in the air tank 80 can not rise above a certain level. A check valve 86 ensures that even when the system is at a standstill, the compressed air in the air tank 80 is included and not, for example, again via the compressor 78 escapes.

Each pneumatic slave cylinder / piston assembly is a control valve 88 respectively. 90 assigned. These are under the control of a drive device 92 which is from a power supply 94 is fed. A pressure sensor 96 supplies a pressure signal to the drive device 92 indicating the pressure in the area of the air tank 80 , ie indexed in the high pressure side of the system.

Through the two control valves 88 . 90 can that in the air tank 80 stored air pressure can optionally be applied to the cylinder. For example, by this appropriate clocked control of the control valves 88 . 90 a correspondingly reduced pressure in the cylinder can be adjusted. Furthermore, throttles 94 be provided, which realize a corresponding pressure reduction.

It also recognizes in association with the switching valve 88 one under the control of the drive device 92 standing pressure regulator 98 in the conduction path between the switching valve 88 and for example the cylinder space 56 the compressed air slave cylinder / piston assembly 46 , In association with an actuating position to be respectively set, for example, the first coupling region 16 , so gives the drive device 92 to the pressure regulator 98 a signal indicative of a set pressure in the cylinder space 56 leading line represents, which target pressure on the characteristic described above is clearly related to a set operating position to be set. The pressure regulator regulates the in the line 100 and thus of course in the associated cylinder chamber 56 prevailing pressure so that it is in the range of the target pressure, whereby the associated clutch area 16 gets into the target operating position.

It should be noted that the principles of the present invention may of course be found in differently designed double clutches application or not necessarily be provided in both coupling areas. It is also natural that the setting of such a force characteristic of each considered Kraftbeaufschlagungsanordnung can be reached by other combinations of springs or basically other spring elements. It is also conceivable to use a diaphragm spring, the characteristic curve is chosen so that it is ensured that over the service life time a respective vertex region of the characteristic is not reached, so that it is further ensured that there is always a clear relationship between the spring force and operating position can. To ensure this even better, a wear compensation arrangement can be provided in Abstützweg or force transmission path of a respective Kraftbeaufschlagungsanordnung to ensure that even when wear occurs, for example, the friction linings of a clutch disc Kraftbeaufschlagungsanordnung or that assembly thereof, which relevant to the characteristic Provides force over the service life remains in a constant Positonierung and, for example, no relaxation caused by the wear can occur. It should also be noted that, especially when used in commercial vehicles, the use of compressed air as a fluid for actuation is advantageous since compressed air is generally provided there by compressors. Of course, other media, ie in particular liquids, are used, the pressure to be sensed accordingly and then set under the specification of a certain target pressure.

Claims (7)

Double clutch arrangement comprising: - a first clutch area ( 16 ) with a first clutch disk assembly ( 22 ) and a first pressure plate ( 20 ), - a second coupling region ( 18 ) with a second clutch disk assembly ( 32 ) and a second pressure plate ( 30 ), - an intermediate plate ( 26 ) between the two clutch disc assemblies ( 22 . 32 ), - one with the intermediate bearing plate ( 26 ) connected housing arrangement ( 36 ), wherein the first pressure plate ( 20 ) and the first clutch disk assembly ( 22 ) on a first axial side of the intermediate plate ( 26 ) are arranged and the second pressure plate ( 30 ) and the second clutch disc ( 32 ) and the housing arrangement ( 36 ) on a second axial side of the intermediate plate ( 26 ) are arranged, - a first Kraftbeaufschlagungsanordnung ( 38 ), via which an actuating force on the first pressure plate ( 20 ), wherein the first load application arrangement ( 38 ) the second coupling region ( 18 ) and the intermediate plate ( 26 ) axially engages and with respect to the housing assembly ( 36 ) supported first Kraftbeaufschlagungselement ( 44 ), - a second Kraftbeaufschlagungsanordnung ( 48 ), via which an actuating force on the second pressure plate ( 30 ) is controllable, wherein the second Kraftbeaufschlagungsanordnung ( 48 ) with respect to the housing assembly ( 36 ) supported second Kraftbeaufschlagungselement ( 30 ), wherein at least one force application arrangement ( 36 . 48 ) of the first Kraftbeaufschlagungsanordnung ( 38 ) and second Kraftbeaufschlagungsanordnung ( 48 ) one the associated coupling region ( 16 . 18 ) in the direction of engagement or disengagement generates stressing force with respect to the actuating travel steadily increasing or steadily decreasing force characteristic, - a pressurized fluid actuator assembly ( 14 ), at least in association with the at least one force application arrangement ( 38 . 48 ) a pressurized fluid slave cylinder / piston assembly ( 46 . 52 ) for generating one of the force of this Kraftbeaufschlagungsanordnung ( 38 . 48 ) counteracting actuating force, wherein the pressurized fluid actuating arrangement ( 14 ) a fluid pressure regulating arrangement ( 92 . 98 ) for controlling the operation of the at least one Kraftbeaufschlagungsanordnung ( 38 . 48 ) cooperating coupling region ( 16 . 18 ) based on the in this pressurized fluid slave cylinder / piston assembly ( 46 . 52 ) prevailing fluid pressure. Double clutch arrangement according to claim 1, characterized in that the at least one force application arrangement ( 38 . 48 ) a diaphragm spring-like biasing element ( 44 . 50 ). Dual clutch arrangement according to claim 1 or 2, characterized in that the at least one force application arrangement ( 48 ) at least one helical spring biasing element ( 54 ). Double clutch arrangement according to claim 2, characterized characterized in that the at least one Kraftbeaufschla arrangement Furthermore, at least one further diaphragm spring-like biasing spring element includes. Dual clutch arrangement according to one of claims 1 to 4, characterized in that the pressure fluid actuating arrangement ( 14 ) in association with the at least one pressurized fluid slave cylinder / piston assembly ( 46 . 52 ) a pressurized fluid source ( 78 . 80 ), a connection between the source of pressurized fluid ( 78 . 80 ) and a cylinder space ( 56 . 58 ) the at least one pressurized fluid slave cylinder / piston assembly ( 46 . 52 ) optionally producing and interrupting valve arrangement ( 88 . 90 ) as well as in the flow path between the valve arrangement ( 88 . 90 ) and the cylinder space ( 56 . 58 ) a fluid pressure regulator ( 98 ). Double clutch arrangement according to one of Claims 1 to 5, characterized in that the pressure fluid actuating arrangement ( 14 ) a radially outer first pressure fluid slave cylinder / piston assembly ( 46 ) in co-operation with the first Kraftbeaufschlagungsanordnung ( 38 ) and a radially inner second pressure fluid slave cylinder / piston assembly ( 52 ) in conjunction with the second Kraftbeaufschlagungsanordnung ( 48 ). Double clutch arrangement according to one of claims 1 to 6, characterized in that the pressurized fluid is compressed air.