DE102017002057A1 - Coupling device and drive train with such a coupling device - Google Patents

Abstract

The present invention relates to a coupling device with a coupling (4), an urging element (34) for acting on the coupling (4) with a closing force (36) for closing the coupling (4) and a spring device (38) for generating a spring force (50 ) which can be applied or applied to the loading element (34) while generating the closing force (36), wherein the spring force (50) of the spring device (38) can be transferred hydraulically to the loading element (34). Moreover, the present invention relates to a drive train with such a coupling device.

Description

The present invention relates to a coupling device for a power train with a clutch, an urging member for biasing the clutch with a closing force for closing the clutch and a spring means for generating a spring force, which is applied or applied to generate the closing force on the biasing member. Moreover, the present invention relates to a drive train for a motor vehicle with such a coupling device.

Coupling devices with a clutch, in particular a multi-disc clutch, are known from the prior art, wherein the clutch is associated with a loading element for acting on the clutch with a closing force for closing the clutch. In addition, a spring device for generating a spring force or restoring force is provided, which can be applied to the biasing element while generating the closing force acting on the clutch via the biasing element. Thus, the known coupling devices are coupling devices with a normally closed due to the closing force coupling. In order to transfer the normally closed clutch from its closed position to the open position, the actuating element is usually associated with an actuating element, by means of which a force can be applied by overcoming the closing force on the biasing member to transfer the clutch in an open position. If the application of the actuating force to the loading element is ended, the spring device, via its spring force and the resulting closing force, effects a renewed transfer of the coupling into its closed position. Since the closing force for closing the clutch must be relatively high in order to allow a safe closing of the clutch and holding the clutch in the closed position, usually also the spring device must be dimensioned correspondingly large or rigid, so that together with the Coupling and the biasing element in a coupling receiving space between the drive unit and transmission arranged spring means makes a relatively large space required. Thus, the known coupling devices in drive trains, in which the coupling receiving space between the drive unit and the transmission is relatively small dimensions, only with design restrictions or not usable.

It is therefore an object of the present invention to develop a coupling device of the generic type such that it is space-optimized and particularly flexible in drive trains for motor vehicles, especially in drive trains with a relatively small clutch receiving space, usable. In addition, the present invention has the object to provide a drive train with such an advantageous coupling device.

This object is achieved by the features specified in the patent claims 1 and 11, respectively. Advantageous embodiments of the invention are the subject of the dependent claims.

The coupling device according to the invention has a coupling. The coupling may be, for example, a multi-plate clutch having an input-side and an output-side plate carrier, between which a plate set of input-side and output-side plates is arranged. The coupling device further comprises an urging member for urging the clutch with a closing force for closing the clutch, wherein the urging member could also be referred to as a power transmission element. Moreover, a spring device is provided. The spring device may for example be formed by one or more spring elements, wherein the single spring element may be formed for example by a plate spring or coil spring. Basically, however, here any elastic or resiliently formed element comes into question. The spring device of the one or more spring elements is used to generate a spring force, which could also be referred to as restoring force of the spring device. In this case, the spring device is arranged such that the spring force can be applied or applied to generate the closing force on the loading element. In conjunction with the loading element and the spring device, the clutch thus forms a normally closed clutch. The spring force of the spring device is hydraulically, so for example via a corresponding hydraulic device, transferable from the spring device to the biasing element. While in conventional coupling devices with a normally closed clutch, the spring device or its spring force acts mostly directly on the biasing member, so that the spring means is arranged together with the clutch and the urging member in a coupling receiving space, the spring force of the spring means in the coupling device according to the invention hydraulically transmit the biasing element, whereby the spring means can be arranged particularly flexible within a drive train, in particular outside the clutch receiving space, while the spring force of the spring means save space hydraulically transferable to the loading element. Thus, a coupling device is provided which allows a flexible arrangement within a drive train and - especially in drive trains with relatively small clutch receiving space between the drive unit and transmission - space is optimized.

In an advantageous embodiment of the coupling device according to the invention, the spring force can be applied or applied to a displaceable first piston by increasing a hydraulic pressure in a first chamber associated with the first piston, the first chamber being in flow communication with a second chamber associated with a displaceable second piston that interacts with the urging element. Thus, in this embodiment, the spring force is transmitted hydraulically via the hydraulic medium in the first chamber, the flow connection and the second chamber to the second piston, which leads to its displacement and thus to applying the spring force to the biasing element, which in turn the closing force on the Clutch applies, whereby the closing force could correspond to the spring force. Analogously, the hydraulic medium acts as a force transmission element or medium.

In a further advantageous embodiment of the coupling device according to the invention, the first chamber is connected to the second chamber via at least one elongate line or hydraulic line in order to produce the aforementioned flow connection between the first and the second chamber. The elongated line may preferably extend at least in certain sections in a housing wall, optionally a transmission housing wall, a clutch housing wall or a drive housing wall. Alternatively or additionally, the elongate line may also extend at least in sections within a clutch hub and / or the wall of a support tube for such a clutch hub. Depending on the design and arrangement of the coupling, a portion of the line can also be designed as a rotary feedthrough. In any case, allows an elongated conduit whose flow cross section is preferably less than the flow cross section of the first and second chambers, a space-saving transfer of the spring force of the spring means on the biasing member.

In a particularly advantageous embodiment of the coupling device according to the invention, the first chamber and / or the second chamber is fixed. If the first or / and second chamber is designed to be stationary, it does not rotate with other components of the coupling device about an axis of rotation, so that no centrifugal forces act on the hydraulic medium within the first and / or second chamber, which necessitate measures for a so-called centrifugal oil compensation would. Thus, the structure of the coupling device is thereby simplified. In this embodiment, it is preferred that the first and / or second chamber is each formed within a fixed housing which bounds the first and / or second chamber, respectively.

In principle, the first and / or second chamber may be formed as simple cylindrical chambers. In a further advantageous embodiment of the coupling device according to the invention, however, the first chamber is designed as an annular chamber in order to simplify the interaction with an actuating element described in more detail below. Alternatively or additionally, the second chamber is designed as an annular chamber to arrange this particularly simple and space-saving in the vicinity of the biasing element for acting on the clutch and to be able to apply the spring force uniformly on the biasing element. At least in the case of the second chamber designed as an annular chamber and the second piston associated with the second chamber is preferably designed as an annular piston. The formation of the first piston as an annular piston, which is associated with the first chamber designed as an annular chamber, is not absolutely necessary, but advantageous.

In a preferred embodiment of the coupling device according to the invention, the second piston is formed separately from the loading element. As a result, the production is simplified. Moreover, by the separate formation of the second piston and the loading element, a rotational drive decoupling between the second piston and the loading element can be achieved, as is furthermore preferred in this embodiment. Thanks to the rotational drive decoupling, which can be done for example via a sliding or roller bearing, and the second piston with respect to the circumferential directions or directions of rotation of the clutch may be formed fixed, which in addition to a fixed, the second chamber limiting housing to a simple and safe Sealing of the second chamber and an elimination of a centrifugal force influence on the hydraulic medium in the second chamber leads.

In a further advantageous embodiment of the coupling device according to the invention, which represents an alternative to the above-described embodiment, the second piston is formed integrally with the biasing member or fixed thereto, so that the second Piston and the biasing element are in rotational driving connection with each other. This embodiment is particularly advantageous in a co-rotating, so not fixed, second chamber.

In a further preferred embodiment of the coupling device according to the invention, the first piston is displaceable from a first position, in which the clutch is closed, counter to the spring force of the spring device into a second position, in which the clutch is open. For this purpose, for example, a corresponding actuating element for applying a force to the first piston or the spring device may be provided.

In a particularly preferred embodiment of the coupling device according to the invention, the first piston is displaceable from the aforementioned second position against the spring force of the spring device into a third position, in which the first chamber is in flow communication with a hydraulic medium reservoir. This has the advantage that any leakage losses in the region of the first chamber, the flow connection between the first and second chambers and the second chamber can be compensated by transferring the first piston to the third position described by the first chamber with the hydraulic medium reservoir in the third position is in flow communication. It is advantageous if the second and third positions of the first piston are selected such that in the second position, the clutch is not only opened, but also any overpressure in the first chamber is substantially or completely degraded, before the first piston achieved in achieving the flow connection with the hydraulic medium reservoir in the third position, in order to achieve any loss of leakage existing particularly easily by the flow of hydraulic medium from the hydraulic medium reservoir into the first chamber. A residual pressure due to the second spring device described in more detail later is, however, acceptable, this can preferably be counteracted by a stop for the biasing element.

In order to be able to open the clutch, which is normally closed by the spring device, in a further preferred embodiment of the coupling device according to the invention, an actuating element is provided for applying a control force by overcoming the spring force of the spring device. The actuator can in this case be driven in any way to apply said force. For example, the actuating element may be an electrically or hydraulically driven actuating element.

In a further particularly advantageous embodiment of the coupling device according to the invention, the actuating element acts to apply the actuating force, bypassing the Beaufschlagungselements with the first piston or the spring means together. In this case, it is preferable for the actuating element also to cooperate with the first piston or the spring device in bypassing the second piston and / or the hydraulic medium in the first or second chamber. In this context, it has proved to be particularly advantageous if the loading element interacts directly with the first piston or the spring device. This embodiment and its variants have the advantage that the actuating element for applying the actuating force does not have to be arranged in the vicinity of the coupling, the Beaufschlagungselements or the second piston and in particular outside of a - depending on the design of the drive train - are placed relatively small coupling receiving space can. Consequently, this embodiment causes a further space optimization of the coupling device and in particular allows a flexible arrangement of an optionally space-consuming actuator. Also, this embodiment allows the arrangement of the first piston and the actuating element in a common actuating housing.

In a further particularly advantageous embodiment of the coupling device according to the invention, an actuating housing is provided, in which the first piston, the first chamber and the actuating element is arranged or formed. The actuating housing can be designed as a housing portion of a larger hydraulic housing, which also serves to supply additional components within a drive train with hydraulic medium. Alternatively, the actuator housing may be formed separately and thus in the manner of a module that may be relatively easily and flexibly attached to a component of the powertrain. Moreover, in this embodiment, it is not necessarily preferred if the spring device is arranged within the actuating housing. As already indicated above, it is also preferred in this embodiment if the actuating housing is stationary and thus not co-rotating, for example, in order to avoid a centrifugal force influence on the hydraulic medium in the first chamber and optionally also on the spring device.

In a further advantageous embodiment of the coupling device, the actuating element is a hydraulically driven actuating piston. The actuator formed as an actuating piston is preferably a third chamber assigned, which can be acted upon by generating a hydraulic pressure in generating the actuating force. For the purpose of a simple to manufacture and compact hydraulic device of the coupling device according to the invention, it is preferred if the actuating piston associated with the third chamber is formed in the aforementioned actuator housing.

In a further preferred embodiment of the coupling device according to the invention, the first chamber is limited in the direction of displacement of the first piston by the first piston on the one hand and by a wall of the actuating housing on the other. It is preferred if the first piston has a protruding support portion which extends through an opening in the wall. In this case, it is also advantageous if the protruding support portion of the first piston extends under sealing of the first chamber and / or under the guidance of the first piston on the wall or at the opening edge through the opening.

According to a further preferred embodiment of the coupling device according to the invention the actuating piston is supported or supported in the direction of displacement of the first piston to cooperate with the first piston and thus indirectly via the first piston with the spring device. Alternatively or additionally, the actuating piston is guided in the displacement direction of the first piston to cooperate with the first piston and / or the spring means. In both cases, it is advantageous if the actuating piston can be supported or supported and / or guided in the displacement direction thereof on the abovementioned support section of the first piston. In the case of the guide of the actuating piston on the first piston, the actuating piston preferably has a projecting guide section which is guided on the first piston, possibly the protruding support section of the first piston. In order to counteract an undesirable back pressure during displacement of the actuating piston, a ventilated or pressureless chamber is preferably provided between the wall and the actuating piston within the actuating housing. The ventilation can be effected in this case, for example, by recesses on the protruding support portion of the first piston and / or by recesses on the protruding guide portion of the actuating piston. Although this is ventilation, this also includes a vented or pressureless chamber filled with oil or grease between the wall and the actuating piston.

In principle, when the first piston is displaced from the first to the second position and optionally beyond that into the third position, the second piston can be retracted hydraulically, so that the clutch is open in the second position of the first piston. In order to support this movement of the second piston, however, in a further preferred embodiment of the coupling device according to the invention a second spring means for generating an opening force opposite the closing force is provided which can be applied or applied to the loading element. In particular, in a separate from the second piston formed Beaufschlagungselement this is advantageous to quickly move the biasing member in a reset position, especially since the first piston is already moved to its second position. It may be advantageous here if the second spring device cooperates directly with the loading element or, in particular, with an admission element formed integrally with the second piston, the second piston. For example, the second spring device can be supported, on the one hand, on a component of the coupling device and, on the other hand, on the loading element or the second piston.

As already indicated above, the clutch in an advantageous embodiment of the coupling device according to the invention is a multi-plate clutch.

In order to be able to provide a particularly space-saving second spring device in the region of the clutch formed as a multi-plate clutch, the second spring device in a further advantageous embodiment of the coupling device according to the invention at least one spring element between the disks of the multi-plate clutch, optionally at least one corrugated spring on. Alternatively or additionally, the second spring device has at least one elastic, optionally corrugated, formed lamella of the multi-plate clutch in order to create a space-saving second spring device.

The drive train according to the invention for a motor vehicle has a coupling device of the type described above according to the invention. The drive train preferably has a drive unit, particularly preferably an internal combustion engine, and a transmission, wherein the clutch of the clutch device for selectively transmitting torque between the drive unit and transmission between the drive unit and the transmission is arranged.

In a preferred embodiment of the drive train according to the invention, the clutch, optionally also the biasing element and / or the second piston and / or the second chamber and / or the housing of the second chamber, arranged in a coupling receiving space. The coupling receiving space is preferably formed between the aforementioned drive unit and the aforementioned transmission. The spring device, where appropriate, the first chamber and / or the first piston and / or the actuating element and / or the actuating housing, however, is arranged outside of the coupling receiving space. Thus, the last-mentioned components of the coupling device can be arranged, for example, in the region of the transmission or in the region of the drive unit, here in each case, for example, in or on the housing of the drive unit or of the transmission.

In a particularly preferred embodiment of the drive train according to the invention, the coupling receiving space is limited by a fixed coupling housing. The clutch housing may in this case be formed, for example, by a transmission housing bell or a drive housing bell. Alternatively, however, the clutch housing may also be formed as a separate housing part, which is arranged between the gear housing and the drive housing, and optionally attached to one of the two said housings.

• 1 eine Hydraulikeinrichtung einer Ausführungsform der erfindungsgemäßen Kupplungsvorrichtung in geschnittener Darstellung mit dem ersten Kolben in einer ersten Stellung,
• 2 eine Seitenansicht einer Kupplung der ersten Ausführungsform der Kupplungsvorrichtung in geschnittener Darstellung mit einem Beaufschlagungselement und weiteren Teilen der Hydraulikeinrichtung aus 1,
• 3 die Hydraulikeinrichtung aus 1 mit dem ersten Kolben in einer zweiten Stellung und
• 4 die Hydraulikeinrichtung aus den 1 und 3 mit dem ersten Kolben in einer dritten Stellung.

The invention will be explained in more detail below with reference to an exemplary embodiment with reference to the accompanying drawings. Show it:

• 1 a hydraulic device of an embodiment of the coupling device according to the invention in a sectional view with the first piston in a first position,
• 2 a side view of a coupling of the first embodiment of the coupling device in a sectional view with an urging member and other parts of the hydraulic device 1 .
• 3 the hydraulic device off 1 with the first piston in a second position and
• 4 the hydraulic device from the 1 and 3 with the first piston in a third position.

1 shows essential components of a hydraulic device 2 and 2 a clutch 4 an embodiment of the coupling device according to the invention, wherein first below the structure of the clutch 4 with reference to FIG. 2 will be explained in more detail.

In 2 are the opposite axial directions 6 . 8th , the opposite radial directions 10 . 12 and the opposite circumferential directions 14 . 16 the clutch 4 indicated by corresponding arrows, the clutch 4 or their components around one in the axial directions 6 . 8th extending axis of rotation 18 are rotatable.

The coupling 4 is designed as a multi-plate clutch. So has the clutch 4 an input-side plate carrier 20 that has a clutch input hub 22 is indirectly or directly with an output side of a drive unit (not shown) in rotary driving connection, and an output-side plate carrier 24, which via a clutch output hub 26 is indirectly or directly with a transmission input shaft of a transmission (not shown) in rotary driving connection. Between the Lamellentragabschnitten the two plate carrier 20 . 24 is a disc pack 28 arranged, the non-rotatably connected to the input-side plate carrier 20, but in the axial direction 6 . 8th movable slats 30 and rotatably with the Lamellentragabschnitt the output side plate carrier 24 connected, but in the axial direction 6 . 8th movable slats 32 having, wherein the slats 30 . 32 in the axial direction 6 . 8th alternately succeed each other. In the illustrated embodiment, the input-side plate carrier 20 from outer plate carrier and the output side plate carrier 24 designed as an inner disk carrier, so that the slats 30 also as outer fins and the fins 32 can also be referred to as inner disks. Moreover, the slats are 30 formed in the illustrated embodiment as reibbelaglose slats or steel plates, while the slats 32 are formed as Reibbelaglamellen, which are provided on both sides in the illustrated embodiment with a friction lining.

The clutch 4 or the disk pack 28 the clutch 4 is one in the axial direction 6 . 8th sliding loading element 34 assigned. The imposition element 34 , which can also be referred to as a power transmission element here, serves to act on the clutch 4 or of the disk pack 28 in the axial direction 6 with a closing force 36 to close the clutch 4 , While on the feather device 38 in 1 will be discussed in more detail, is already at this point the second spring device 40 the coupling device described. The second spring device 40 serves to generate one of the closing force 36 in the axial direction 8th opposite opening force 42 pointing to the applying element 34 can be applied or applied. In the illustrated embodiment, the second spring means 40 several spring elements 44 on, in the axial direction 6 . 8th between the slats 30 the clutch 4 are arranged, wherein the spring elements 44 preferably designed as so-called corrugated springs are. Alternatively or additionally, corresponding spring elements 44 or corrugated springs in the axial direction 6 . 8th be arranged between the slats 32.

Although the in 2 shown spring elements 44 the second spring device 40 and their arrangement is preferred, so the second spring means 40 alternatively or supplementarily directly with the Beaufschlagungselement 34 or / and directly with the second piston of the hydraulic device described in detail later 2 interact, as this is based on the only schematically indicated spring elements 46 and 48 in 2 is illustrated. Alternatively or additionally, it comes for a second spring device 40 Also consider that these at least one in the axial direction 6 . 8th elastically formed lamella 30 or 32 having. For this purpose, the corresponding slat 30 or 32 in the circumferential direction 14 . 16 be corrugated or wavy, to an elastic deformation thereof in the axial direction 6 . 8th to enable. In particular, the slats 32 in addition to the spring elements 44 in the circumferential direction 14 . 16 be formed wavy to an elastic deformability in the axial direction 6 . 8th to effect and together with the spring elements 44 the second spring device 40 train.

The above with reference to 2 mentioned spring device 38 serves to generate a spring force 50, generating the closing force 36 of the urging element 34 on the loading element 34 can be applied or applied, as in 1 is indicated. The spring force 50 However, it does not affect the loading element directly 34 applied, but rather the spring force 50 the spring device 38 hydraulically on the loading element 34 transferable, as will be explained in more detail below, wherein for this purpose first the hydraulic device 2 to 1 should be described.

The coupling device has an in 1 shown actuator housing 52 on, whose opposite longitudinal directions 54 . 56 in 1 are indicated by corresponding arrows, wherein a receiving space 58 in the longitudinal directions 54 . 56 within the actuator housing 52 extends, which is substantially, here with gradations, cylindrical. Inside the recording room 58 the spring means 38 is arranged, which is here formed by a plurality of disc springs, so that in the spring device 38 can also be spoken by a disc spring package. So is the spring device 38 longitudinal 56 supported by means of a securing ring on the actuating housing 52. In the opposite longitudinal direction 54 is the spring device 38 however, on a first piston 60 supported.

The here designed as an annular piston first piston 60 is a first chamber 62 assigned, which is filled with a hydraulic medium, so preferably oil. The first chamber 62 , which is formed as an annular chamber is in the displacement directions of the first piston 60 here the longitudinal directions 54 . 56 match, through the first piston 60 and one inside the reception room 58 protruding wall 64 of the actuator housing 52 limited. More precisely, the first chamber 62 longitudinal 56 through the first piston 60 and in the longitudinal direction 54 through the wall 64 limited to the actuator housing 52. In addition, the first piston points 60 one in the longitudinal direction 54 protruding, here substantially tubular, support portion 66 on. The support section 66 extends in the longitudinal direction 54 through a central opening 68 in the wall 64 , this being under sealing of the first chamber 62 , here by means of a seal 70 on the wall 64 , and under the leadership of the first piston 60 in the longitudinal directions 54 . 56 on the wall 64 he follows. Also is off 1 it can be seen that on the support section 66 , here in the longitudinal direction 54 pointing end of the support section 66 , Recesses 71 are provided, whose purpose will be discussed again later. Thus, the first chamber formed as an annular chamber 62 inside through the support section 66 and out through the actuator housing 52 limited. The spring force 50 , also called the restoring force of the spring device 38 may be designated by increasing a hydraulic pressure in the first chamber 62 in the longitudinal direction 54 on the first piston 60 be applied.

The first chamber 62 stands over an opening 72 and one to the opening 72 subsequent elongated line 74 or hydraulic line with an in 2 shown second chamber 76 in fluid communication. The second chamber 76 is again designed as an annular chamber and through a housing 78 limited, with both the actuator housing 52 as well as the case 78 is formed fixed, so that neither the actuator housing 52 still the case 78 around the in 2 shown axis of rotation 18 the clutch 4 rotate. In this way, a centrifugal force influence on the hydraulic medium within the first and second chambers 62 . 76 be excluded. General may also be of a fixed first and second chambers 62 . 76 to be spoken. The second chamber 76 is one in the axial directions 6 . 8th the clutch 4 sliding second piston 80 associated with the aforementioned loading element 34 in the axial direction 8th on the second piston 80 is supported or supported and thus with the second piston 80 interacts. Basically, the second piston could 80 integral with the biasing element 34 be formed or attached to this. In the illustrated embodiment, the second piston 80 however, separate or separate from the apply element 34 formed, wherein the second piston 80 about a camp 82 , here a rolling bearing, of the impingement element 34 is decoupled.

In summary, it must therefore first be noted that the spring force 50 the spring device 38 over the first piston 60 in the actuator housing 52 and then over the first chamber 62 , The administration 74 and the second chamber 76 hydraulically to the second piston 80 and thus also to the biasing element 34 is transferable, as a result, the aforementioned closing force 36 in the axial direction 6 on the disk pack 28 the clutch 4 so that it is closed. It is thus thanks to the spring device 38 is a normally closed clutch 4 ,

To the normally closed clutch 4 is also an in. open 1 shown actuator 84 for applying a force 86 overcoming the spring force 50 the spring device 38 intended. The actuator 84 is there as a hydraulically driven actuating piston 88 formed, wherein the actuating element 84 within the actuator housing 52 and in the longitudinal directions 54 . 56 the same is arranged displaceably. The actuating piston 88 is formed substantially as a cylindrical piston, which in the longitudinal direction 54 behind the aforementioned wall 64 is arranged. In this case, the actuating piston 88 is a third chamber 90 on his wall 64 Assigned to the opposite side, wherein the substantially cylindrical third chamber 90 longitudinal 56 through the actuating piston 88 , Outwardly through the actuator housing 52 and in the longitudinal direction 54 by one, optionally releasably on the actuator housing 52 fortified wall 92 is limited, being in the wall 92 or in the actuator housing 52 an opening 94 is provided, over which the third chamber 90 while generating the force 86 can be acted upon by hydraulic pressure. More specifically, that is in the actuator housing 52 trained third chamber 90 about one to the opening 94 leading line 96 or hydraulic line can be acted upon by hydraulic pressure, wherein the hydraulic medium is taken from a hydraulic medium reservoir 98 and by means of a pump shown only schematically 100 increasing the hydraulic pressure in the third chamber 90 can be pumped.

The actuating piston 88 is in the direction of displacement, here in the longitudinal direction 56 , on the first piston 60 , more precisely, through the opening 68 extending support section 66 , supportable or supported. Thus, the actuator acts 84 in the form of the actuating piston 88 bypassing the apply element 34 , the second piston 80 and the hydraulic medium in the first or second chamber 62 . 76 with the first piston 60 together. In the illustrated embodiment may also be a direct interaction of the actuating element 84 with the first piston 60 to be spoken. In addition, the actuating piston 88 in his displacement directions or in the longitudinal directions 54 . 56 not only on the actuator housing 52 but also on the first piston 60 more precisely, its supporting section 66 , guided. For this purpose, the actuating piston 88 a central, longitudinal direction 56 projecting guide section 102 on, in the longitudinal direction 56 in the substantially tubular support portion 66 of the first piston 60 dives in and out on this supported and thus guided in the displacement. Also the leadership section 102 is substantially tubular, so that this a central recess 106 having. Moreover, in the guide section 102 again recesses 104 provided to the central recess 106 in the tubular guide portion 102 to lead.

Longitudinal 54 . 56 between the wall 64 and the actuating piston 88 is a ventilated or pressureless chamber 108 formed, in addition to the outside through the actuator housing 52 and inwardly through the support section 66 of the first piston 60 and the guide section 102 of the actuating piston 88 is limited, thus forming an annular chamber. This effect the recesses 71 in the support section 66 , the recesses 104 in the guide section 102 and the central recess 106 that the chamber 108 ventilated or formed substantially depressurized. Although this is a case of ventilation, so the chamber 108 basically be filled with grease, a hydraulic medium or the like.

Before discussing the operation of the coupling device is closer, is still on a further opening 110 in the actuator housing 52 referenced over a line 112 or hydraulic line with the already mentioned hydraulic medium reservoir 98 is in flow communication. Also, the first piston points 60 longitudinal 54 . 56 spaced apart seals 114 and 116 whose function will be further discussed in the following description.

Hereinafter, the operation and other features of the coupling device with reference to Figs. 1 to 4 will be described in more detail.

In the 1 and 2 is the first piston 60 in a first position. In the first position, the spring device exercises 38 their spring force 50 on the first piston 60 out, with the spring force 50 via the hydraulic medium in the first chamber 62 , the line 74 and the second chamber 76 on the second piston 80 is transmitted, which is the biasing element 34 against the opening force 42 the second spring device 40 against the disk pack 28 pushes, which is thus compressed. Consequently, the clutch 4 closed. In this first position of the first piston 60 opens the mouth 110 between the two seals 114 . 116 in the recording room 58 , so that no hydraulic medium from the hydraulic medium reservoir 98 over the line 112 and the opening 110 longitudinal 54 in the first chamber 62 or in the longitudinal direction 56 in the recording room 58 can get.

Should the clutch 4 be opened, so will the actuating piston 88 associated third chamber 90 over the pump 100 and the line 96 subjected to a hydraulic pressure, so that the actuating piston 88 his power 86 longitudinal 56 on the first piston 60 exercises. This overcomes the restoring force 86 the spring force 50 the spring device 38 so that the first piston 60 longitudinal 56 in the in 3 shown second position is moved. In the second position of the first piston 60 is the clutch 4 opened, wherein the second spring means 40 or their opening force 42 not just pushing apart the slats 30 . 32 , but also a displacement of the actuating element 34 and the second piston 80 in the axial direction 8th effects and / or supports. In the second position of the first piston 60 according to 3 prevents the seal 114 still an inflow of hydraulic medium from the hydraulic medium reservoir 98 via the opening 110 into the first chamber 62 ,

Is the force 86 so large that the first piston 60 under further compression of the spring device 38 from the second position 3 longitudinal 56 in the in 4 shown third position is moved, so is the first chamber 62 over the opening 110 and the line 112 with the hydraulic medium reservoir 98 in flow communication, whereby hydraulic medium from the hydraulic medium reservoir 98 in the now largely unpressurized first chamber 62 can flow to compensate - if any - any leakage losses, especially the opening 110 in the third position 4 now in the longitudinal direction 54 behind the seal 114 in the interior of the actuator housing 52 and thus into the first chamber 62 empties.

Will the pressurization of the third chamber 90 finished, so the first piston returns 60 after the second position 3 due to the spring force 50 the spring device 38 back to the first position 1 back, in which the clutch 4 closed is.

How out 2 Obviously, the clutch is 4 in a - only schematically indicated - coupling receiving space 118 in the axial direction 6 . 8th between a drive unit and a transmission (not shown), wherein in the illustrated embodiment, the biasing element 34 , the second piston 80 , the second chamber 76 and the case 78 the second chamber 76 in the clutch receiving space 118 is arranged. In contrast, the spring device 38 outside the clutch receiving space 118 arranged. The same applies in the present embodiment for the first chamber 62 , the first piston 60 , the actuator 84 and the actuator housing 52 in which the aforementioned components are arranged, so that the spring device 38 and the others in the actuator housing 52 arranged components of the hydraulic device 2 flexible and space-optimized outside of the coupling receiving space 118 be arranged or can be. It is preferred if the coupling receiving space 118 is limited by a fixed clutch housing (not shown), wherein the clutch receiving space 118 is preferably designed as a wet room.

The coupling device is suitable in its entirety, even in drive trains with a relatively small clutch receiving space 118 to be used, especially the hydraulic device 2 flexible outside the clutch receiving space 118 can be positioned without in particular the space-consuming spring means 38 within the coupling receiving space 118 would have to be placed.

LIST OF REFERENCE NUMBERS

2

hydraulic device

4

clutch

6

axial direction

8th

axial direction

10

radial direction

12

radial direction

14

circumferentially

16

circumferentially

18

axis of rotation

20

input-side plate carrier

22

Kupplungseingangsnabe

24

output-side plate carrier

26

Kupplungsausgangsnabe

28

disk pack

30

slats

32

slats

34

impinging

36

closing force

38

spring means

40

second spring device

42

opening force

44

spring elements

46

spring element

48

spring element

50

spring force

52

actuator housing

54

longitudinal direction

56

longitudinal direction

58

accommodation space

60

first piston

62

first chamber

64

wall

66

support section

68

opening

70

poetry

71

recess

72

opening

74

management

76

second chamber

78

casing

80

second piston

82

camp

84

jig

86

force

88

actuating piston

90

third chamber

92

wall

94

opening

96

management

98

Hydraulic fluid reservoir

100

pump

102

guide section

104

recesses

106

central recess

108

chamber

110

opening

112

management

114

poetry

116

poetry

118

Clutch housing space

Claims (11)

Coupling device comprising a coupling (4), a loading element (34) for acting on the coupling (4) with a closing force (36) for closing the coupling (4) and a spring device (38) for generating a spring force (50) generating the closing force (36) can be applied or applied to the loading element (34), characterized in that the spring force (50) of the spring device (38) can be transferred hydraulically to the loading element (34). Coupling device according to Claim 1 characterized in that the spring force (50) is applied or applied to a displaceable first piston (60) by increasing a hydraulic pressure in a first chamber (62) associated with the first piston (60), the first chamber (62) being provided with a first chamber (62) second chamber (76), optionally via at least one elongated conduit (74) is in flow communication associated with a displaceable second piston (80) which cooperates with the biasing element (34). Coupling device according to Claim 2 , characterized in that the first and / or second chamber (62; 76) is fixed, preferably each within a fixed housing (52; 78), or / and designed as an annular chamber. Coupling device according to one of Claims 2 or 3 characterized in that the second piston (80) is formed separately from the biasing member (34), preferably decoupled from the biasing member (34), or integrally formed with or secured to the biasing member (34). Coupling device according to one of Claims 2 to 4 , characterized in that the first piston (60) from a first position in which the clutch (4) is closed, against the spring force (50) of the spring means (38) in a second Slidable position in which the clutch (4) is opened, wherein the first piston (60) preferably from the second position against the spring force (50) of the spring means (38) is displaceable in a third position in which the first chamber ( 62) is in flow communication with a hydraulic medium reservoir (98). Coupling device according to one of the preceding claims, characterized in that an actuating element (84) for applying a control force (86) overcoming the spring force (50) of the spring device (38) is provided, wherein the actuating element (84) preferably bypassing the Beaufschlagungselements (84). 34) and / or the second piston (80) and / or the hydraulic medium in the first or second chamber (62, 76), particularly preferably directly, with the first piston (60) or the spring means (38) cooperates. Coupling device according to Claim 6 , characterized in that an actuating housing (52) is provided, in which the first piston (60), the first chamber (62) and the actuating element (84), preferably also the spring device (38), are arranged or formed, wherein the Actuating housing (52) is particularly preferably designed to be stationary, and / or the actuating element (84) is designed as a hydraulically driven actuating piston (88), which is preferably associated with a third chamber (90), which generates the actuating force (86) with hydraulic pressure can be acted upon, wherein the third chamber (90) is particularly preferably formed in the actuator housing (52). Coupling device according to one of Claims 2 to 7 , characterized in that the first chamber (62) in the direction of displacement of the first piston (60) by the first piston (60) on the one hand and by a wall (64) of the actuating housing (52) on the other hand is limited and the first piston (60) preferably a projecting support portion (66) extending through an opening (68) in the wall (64), more preferably sealing the first chamber (62) and / or under the guidance of the first piston (60) on the wall (64) , extends, and / or the actuating piston (88) in the direction of displacement on the first piston (60), optionally its support portion (66), supportable or supported and / or guided, wherein the actuating piston (88) preferably a projecting guide portion (102 ), which is guided on the first piston (60), optionally its support portion (66), and more preferably a vented or pressureless chamber (108) between the wall (64) and the Betätigungskolb en (88). Coupling device according to one of the preceding claims, characterized in that a second spring device (40) for generating a closing force (36) opposite opening force (42) is provided, which is applied or applied to the biasing member (34), wherein the second spring means ( 40) preferably interacts directly with the loading element (34) or the second piston (80). Coupling device according to one of the preceding claims, characterized in that the clutch (4) is a multi-plate clutch, wherein the second spring means (40) preferably at least one spring element (44) between the fins (30) of the multi-plate clutch, optionally at least one corrugated spring, or / and at least one elastic, optionally corrugated, formed lamella (30, 32) of the multi-plate clutch. Drive train for a motor vehicle with a coupling device according to one of the preceding claims, wherein preferably the coupling (4), optionally also the biasing element (34) and / or the second piston (80) and / or the second chamber (76) and / or Housing (78) of the second chamber (76), in a coupling receiving space (118) and the spring means (38), optionally also the first chamber (62) and / or the first piston (60) and / or the actuating element (84) or / and the actuator housing (52), outside the clutch receiving space (118) is arranged, wherein the coupling receiving space (118) is particularly preferably limited by a fixed coupling housing.

Images