DE10009576A1 - Hydrodynamic coupling device esp. torque converter has third connection channel arrangement to remove working fluid from working chamber when coupling element is pressed towards housing - Google Patents

Abstract

The torque converter incorporates a first and a second connection channel arrangement for a working fluid. A third channel arrangement (78,80,82) drains the working fluid from a fluid chamber (56), when a coupling element (50) is pressed towards a housing (12) or a component connected to it via a friction plate arrangement (53). The fluid chamber contains a rotating turbine wheel (26). First and third connection channels are connected to the first fluid chamber on axially opposite sides of esp. a turbine wheel shell (28).

Description

The present invention relates to a hydrodynamic coupling direction, especially torque converter, the interior of which by a Coupling element of a lock-up clutch and a friction surface arrangement is separable into a first fluid space and a second fluid space, wherein the coupling element with the interposition of the friction surfaces arrangement to a housing or an associated component is compressible and wherein a fluid channel in the friction surface arrangement Arrangement is provided, in which working fluid from the first fluid space can occur and from which working fluid only to the first fluid space can emerge, wherein the first fluid space through a first Connection channel arrangement working fluid can be supplied and by a second Connection channel arrangement working fluid to or / and from the second Fluid space can be directed.

Such a hydrodynamic coupling device is known from EP 0 428 248 A1 known. The lock-up clutch this as hydrodynamic Coupling device designed torque converter has a Clutch piston on, in the radially outer area with intermediate storage a ring-like friction lining as a friction surface arrangement against one Housing cover can be pressed. In the ring-like friction lining are axially through fluid that extends radially outward at an angle Flow channels provided, in which working fluid from a fluid space of the torque converter enter through a passage opening in the piston can and then radially outward again into an area of the same Fluid space is released. In this way, a by means of a combination of centrifugal effects and shear fluid effects generated flow for cooling the friction lining in the slip  was taken care of, at the same time taking care that none of the Working fluid cooling friction in a between the piston and the Housing cover formed fluid space can enter, so that the coupling efficiency of the lock-up clutch is not impaired.

Although maintaining high coupling efficiency of the Bridging clutch such an embodiment turns out to be has proven to be advantageous, there is basically the problem that the working fluid entering the same fluid space again not on one Total fluid exchange participates and thus through different structural Measures, for example external cooling using cooling fins or the like, care must be taken to ensure that there is no gradual warming of the entire torque converter occurs.

It is the object of the present invention, a generic to further develop hydrodynamic coupling device such that at high coupling efficiency ensures good cooling of the overall system becomes.

According to the invention, this object is achieved by a hydrodynamic Coupling device, in particular torque converter, the interior thereof by a coupling element of a lock-up clutch and a Friction surface arrangement in a first fluid space and a second Fluid space is separable, the coupling element being arranged in between tion of the friction surface arrangement on a housing or a ver tied component is too compressible and being arranged in the friction surface a fluid channel arrangement is provided, in which working fluid can enter the first fluid space and from which working fluid only for can emerge from the first fluid space, furthermore the first fluid space working fluid can be supplied through a first connection channel arrangement and through a second connection channel arrangement working fluid to the and / or can be conducted from the second fluid space.  

The hydrodynamic coupling device according to the invention stands out through a third connection channel arrangement, through which working fluid can be derived from the first fluid space at least if the coupling element with the intermediate arrangement of the friction lining arrangement is pressed onto the housing or the component connected to it.

It is therefore ensured according to the invention that, despite the fact that under Including the first fluid space generated cooling flow over the Friction surface arrangement away even with a long slip operation which otherwise by maintaining the fluid pressure in the interior the coupling device is not provided for a fluid exchange that heated working fluid at least partially flow out of the interior can and can be replaced by colder working fluid.

For example, it can be provided that in the first fluid space Turbine wheel is arranged rotatable about an axis of rotation and that the first Connection channel arrangement and the third connection channel arrangement opposite axial sides of the turbine shaft with respect to the axis of rotation of the same, in particular a turbine wheel shell, with the first Stand in fluid space, preferably the third Ver connection channel arrangement in an area between the turbine wheel, in particular a turbine shell, and the clutch element is in communication with the first fluid space. It will therefore be for it worried that not immediately entered the first fluid space Working fluid again through the third connection channel arrangement at least can partially flow out of the first fluid space without the circulation to have participated in the operation.

For example, it can be provided that the third connection channel arrangement in a turbine wheel hub at least one essentially radial extends extending first fluid passage opening.  

To supply or remove fluid from the second fluid space in a simple manner To be able to discharge this, an output shaft can be provided in which extends essentially in the direction of an axis of rotation second fluid passage opening is formed, which at least a part of the second connection channel arrangement.

To get a very simple structure in which not three completely separately controllable connection channel arrangements can be provided as is the case with a 3-pipe system, it is proposed that the second connection channel arrangement and the third connection channel arrangement in a radially inner region in Connect with each other.

For example, this can be realized in that the third Connection channel arrangement in the second fluid passage opening flows.

At least one passage opening can be in the coupling element be provided for guiding working fluid into the fluid channel arrangement. Furthermore, it is advantageous if at least one in the coupling element Outlet opening for guiding working fluid from the fluid channel arrangement is provided in the first fluid space. It is thus ensured that the working fluid again in the area or on the side of the Coupling element flows into the first fluid space, from which it has previously entered the fluid channel arrangement. This is especially so advantageous if this area of the first fluid space is also in fluid exchange connection is with the third connection channel arrangement.

In particular, when flowing through the fluid channel arrangement to be able to use occurring shear effects or friction effects suggested that an inlet opening and an outlet opening, which are assigned to the same fluid channel section of the fluid channel arrangement, in  Are circumferentially offset from each other. It is also preferred provided that the friction surface arrangement with respect to at least one Assembly of coupling element and housing or so connected component is movable in the circumferential direction and that Fluid channel arrangement comprises a groove-like channel arrangement, which on a friction surface interacting with the at least one assembly the friction surface arrangement is open.

The shear or friction effect can be used with the greatest possible efficiency if the fluid channel arrangement has at least one fluid channel region comprises, which extends essentially only in the circumferential direction.

The present invention further relates to a friction surface arrangement, in particular for a hydrodynamic coupling device, in which A fluid channel arrangement is provided in the friction surface arrangement, in which Working fluid can enter from a fluid space and only to the same Fluid space can leak.

According to the invention, this friction surface arrangement provides that the Fluid channel arrangement at least in regions essentially only in Is designed to extend circumferentially, or / and that the fluid channel arrangement in an outer peripheral surface area and an inner circumference Abge area area of the friction surface arrangement against fluid passage is closed.

Furthermore, the friction surface arrangement can be designed such that the Fluid channel arrangement has at least one inlet area, in which Working fluid through a coupling element of a lock-up clutch hydrodynamic coupling device can occur, and at least has an exit area from which working fluid through the Coupling element can escape through. As before executed, such an arrangement has the advantage that the  Working fluid leaving fluid channel arrangement then very quickly becomes one this working fluid with a relatively high temperature from the interior of the Coupling device executing connection channel arrangement can flow.

According to a further aspect, the present invention relates to a Friction surface arrangement, a fluid channel in the friction surface arrangement Arrangement is provided, in which working fluid from a fluid space can occur and can only exit to the same fluid space.

According to the invention it is further provided that the fluid channel arrangement has at least one fluid channel which has a first end region and with a second end region each to a radial end region, preferably radially outer area, the friction surface arrangement is open.

In this embodiment, both end regions are a fluid channel open to the same radial end region, so that the Fluid exchange can take place to the same fluid space.

It can be provided that the at least one fluid channel with respect a radial line is essentially symmetrical. Example it is possible that the at least one fluid channel is essentially Chen extends straight. In order to maximize the area or Volume area of the friction surface arrangement cool by cooling medium , it is proposed that the at least one fluid channel between has a region of curvature at its end regions. It is further possible that the at least one fluid channel in its end regions in the Runs essentially straight.

In order for a relatively high stability of the friction surface arrangement per se uniform cooling across the entire surface ensures can, it is further proposed that the fluid channel arrangement little  has at least two radially staggered fluid channels, the End regions from one of the at least two fluid channels to the radial one End region of the friction surface arrangement in the circumferential direction between the End regions of the other of the at least two fluid channels are open. It has proven to be advantageous if the end regions of one the at least two fluid channels have an opening angle in the range of 60 ° -70 °, preferably enclose about 65 °. It is also advantageous if the end regions of the other of the at least two fluid channels one Opening angle in the range of 65 ° -75 °, preferably approx. 70 °, lock in.

To avoid fluid jamming in the curvature area, i. i.e., the Flow resistance as low as possible is preferred suggest that one of the at least two fluid channels in its Area of curvature a radius of curvature in the range of 6-8 cm, preferably about 6.8 cm, and that the other of the least two fluid channels in its area of curvature a radius of curvature in Range of 12-14 cm, preferably about 12.8 cm.

According to an alternative very advantageous embodiment, be provided that the at least one fluid channel one in the Central region and extending essentially in the circumferential direction then has respective curvature areas on the central area. The provision of a substantially circumferential direction extending central region of the at least one fluid channel results in that due to the shear effect, a very effective advance transport of the Fluid located in the channel is generated.

With such a configuration, it can then be provided that at least one of the regions of curvature is essentially one rectilinearly extending, an end region of the first and second End section forming channel section connects. Alternatively or additionally  it is possible for at least one of the regions of curvature to be one End area of the first and second end area forms.

In order to have a stable configuration even with such an embodiment to get d. i.e., the risk of various materials breaking away To exclude rich people as much as possible, it is proposed that the first and / or the second end region of the at least one fluid channel with respect to a tangential line an angle in the range of 40 ° -60 °, preferably about 50 °, includes and / or in at least one crumb a radius of curvature in the range of 12-23 cm, preferably about 17.5 cm.

According to a preferred embodiment, it can be provided that the at least one fluid channel radially near one of its end regions is curved outside. This has the consequence that through the turning mode centrifugal forces occurring in the radially outward Endbe the fluid arranged therein is pulled outwards and thus in flow in a defined manner.

Furthermore, it is advantageous for heat dissipation to be as uniform as possible if at least two fluid channels through a connecting channel arrangement are interconnected.

To maintain an even cooling effect over the entire upper It is further proposed that the fluid channel arrangement a plurality of successive ones in the circumferential direction Has fluid channels.

Furthermore, the configuration is in the friction surface arrangement according to the invention device preferably such that the plurality of fluid channels a plurality of fluid channel groups, with a distance between the fluid channels len in a fluid channel group is smaller than a distance between individual  Fluid channel groups. The breakdown into individual fluid channel groups has the Advantage that there are larger open spaces between the individual groups created that are not penetrated by channels, and in which are then so-called pad locks of individual pad segments can to a complete annular friction lining from a A plurality, for example, of similarly shaped covering segments together to be able to ask.

For manufacturing reasons, it is also advantageous if at least one fluid channel in its first and second end regions a radially inner end region of the friction surface arrangement is open. At Such an arrangement can at least one radially inward open fluid channel can be produced in the stamping process and through the extend the entire material thickness of a friction lining. Radially inside subsequent to the inner end region of the channel, a can then Glue such a friction lining to a friction lining carrier first still holding different sections of the friction lining together Fixing ring section can be provided, which after gluing is punched, so that ultimately completely separated from each other Material areas can be created.

According to a further aspect, the present invention relates to a Friction surface arrangement, a fluid channel in the friction surface arrangement Arrangement is provided, in which working fluid from a fluid space can occur and can only exit to the same fluid space.

According to the invention, it is further provided that the friction surfaces are arranged a friction surface carrier and a friction on both sides of the same Has surface element, wherein in a first of the friction surface elements first fluid channel arrangement area is arranged and in a second the A second fluid channel arrangement area is provided for the friction surface elements is, in the friction surface carrier a connection opening arrangement  is provided, via which the first fluid channel arrangement area and the second fluid channel arrangement area with each other in fluid exchange bond.

An arrangement is thus created in which at least two Rub the pairs of friction surfaces against each other, so that the Contact pressure increases the total friction area and thus the torque transmission capacity can also be increased.

In this embodiment too, it is advantageous if the first Fluid channel arrangement area and the second fluid channel arrangement area to a radial end region, preferably radially outer region, of the first friction surface element or the second friction surface element open are. It can be provided that the first fluid channel arrangement area and the second fluid channel arrangement area each at least have a fluid channel that in an end region to the radial end range of each friction surface element is open and another End area in connection with the other fluid channel arrangement area stands.

In the embodiment in which the friction surface arrangement two Has friction surface elements, the assembly as easy as possible design, d. H. those used to align certain fluid passages To minimize openings required work can be provided that at least one of the fluid channel arrangement regions at least one has annular connection opening arrangement into which the Ver binding opening arrangement opens. In this case it is advantageous if the at least one fluid channel with its other end region in the ver binding channel arrangement opens.

To create an arrangement in which in different radial To be able to use areas prevailing pressure conditions,  it can be provided that one of the fluid channel arrangement areas a radial end region, preferably a radially outer region, of the associated friction surface element is open and that the other fluid channel arrangement area via a further connection opening arrangement in a clutch element that can be brought into this frictional engagement Bridging clutch assembly in fluid communication with the Fluid space stands or can be brought.

In this embodiment too, it is again advantageous if one Fluid channel arrangement region has at least one fluid channel, which in an end region to the radially outer end region of the associated one Friction surface element is open and in over its other end region Connected to the other fluid channel arrangement area. The other fluid channel arrangement region then preferably has one ring-like connection channel arrangement in which the connection opening arrangement and / or the further connection opening arrangement flows into.

To ensure that the cooling fluid flows through the fluid channel placement areas flows through before it through the further connection opening arrangement emerges, it is further proposed according to the invention that the connection opening arrangement and the further connection opening arrangement each have at least one fluid passage connection opening and that the Number of fluid passage connection openings of the connection opening arrangement depends on the number of fluid passage connection differentiates openings of the further connection arrangement. Then it can to avoid that the fluid passes through in any relative rotational position tread connection openings of the connection opening arrangement with the Fluid passage openings of the further connection opening arrangement are aligned and thus the fluid directly into other channel areas enter, is fed back into the fluid space.  

In the friction surface arrangement according to the invention is preferably further provided that the fluid channel arrangement in at least one length hand it a tapered towards a canal bottom Has cross-sectional profile. Such an arrangement has the consequence that if the lock-up clutch is disengaged, for example moment with which a component which is in contact with a rotating component Friction lining is taken, is reduced because of the ver recent channel geometry in the manner of a nozzle or a wedge of fluid between the surface and the rotating component is pushed and thus contributes to lifting the topping.

For example, it can be provided that the tapered Cross-sectional profile essentially straight to the channel base extending channel walls is formed. It is also possible that at least one channel wall delimiting the fluid channel wall in a region of curvature into a friction surface region of the friction surface arrangement merges.

The present invention further relates to a hydrodynamic coupling device, in particular hydrodynamic torque converter or Fluid coupling, with a friction surface arrangement according to the invention or a friction element, which a friction lining carrier with approximately ring-like shape and on at least one side of the same fiction has appropriate friction surface arrangement.

The invention will now be described with reference to the accompanying drawings described in detail using preferred embodiments. It shows:

Figure 1 is a partial longitudinal sectional view of a torque converter according to the invention.

. Figure 2 is an axial view of a friction lining or friction surfaces arrangement with a first fluid channel configuration;

Fig. 3 is a view corresponding to Figure 2 with an alternative fluid passage configuration.

FIG. 4 is a partial view of FIG. 1, which shows an embodiment with the friction lining attached to the clutch piston;

FIG. 5 is a view corresponding to FIG. 4 of an embodiment with a friction lining attached to the housing cover;

Fig. 6 is a friction surface with the fluid channels for the embodiment form shown in Figures 4 and 5, respectively.

FIG. 7 is a view corresponding to FIG. 6 with an alternative fluid channel arrangement, which is particularly suitable for an embodiment according to FIG. 5;

Fig. 8 is a fluid channel arrangement which extends substantially only in the circumferential direction of the friction surface;

Fig. 9 is another partial longitudinal sectional view showing a friction surface arrangement with two friction linings carried on a plate;

FIG. 10 is a partial longitudinal sectional view corresponding to FIG. 1 of a modified embodiment of a torque wall;

FIG. 11 shows a further view corresponding to FIG. 1 of a modified embodiment of a torque converter;

Fig. 12 shows a modification of the torque converter shown in Fig. 11;

FIG. 13 is a partial longitudinal sectional view of a further torque converter according to the invention, in which a friction surface arrangement is used, as shown in FIG. 9 on an enlarged scale;

Fig. 14 shows a modification of the torque converter shown in Fig. 13;

FIG. 15 is a partial axial view of a friction pad with Belagsnutung;

Fig. 16 is a view corresponding to Figure 15 with a different pattern of Belagsnutung.

Fig. 17 is another partial axial view of a friction lining with lining groove;

FIG. 18 is an axial view of a friction surface formed in the shape of a fin with two partially overlapping Belagsnutungsmustern;

FIG. 19 is a partial axial view of a friction lining as can be used in the lamella of FIG. 18;

FIG. 20 is a corresponding view of Figure 18 of a modified embodiment form.

FIG. 21 shows another view corresponding to FIG. 18 of a modified embodiment;

FIG. 22 is a partial axial view of one of the friction linings used in the embodiment according to FIG. 21;

Fig. 23 is a partial axial view of the other friction lining, which is used in the embodiment according to Fig. 21;

Fig. 24 is another one of the 18 corresponding view of a friction surface to the invention OF INVENTION.

Fig. 25 is a partial axial view of a in the embodiment according to the friction lining 24 inserted Fig.

Fig. 26 is a partial axial view of the other in the embodiment according to the friction lining 24 inserted Fig.

Fig. 27 is another axial view of a friction surface arrangement according to the invention;

Fig. 28 arrangement, a cross-sectional view of a friction surfaces according to the invention, showing the channel cross-sectional geometry;

FIG. 29 is a view corresponding to Fig 28 of an alternative embodiment variant.

FIG. 30 is a partial axial view of a modified form of the friction surface Ausgestaltungs shown in Fig. 27;

Fig. 31 is another partial axial view of an alternative embodiment of a friction surface arrangement according to the invention.

In Fig. 1, the present invention is shown in the form of a hydrodynamic torque converter. The torque converter 10 comprises a housing, generally designated 12 , which comprises a housing cover 14 and an impeller shell 16 of an impeller 18 , which is firmly connected to the latter radially on the outside, for example by welding. The impeller shell 16 carries on its inside a plurality of impeller blades 20 which follow one another in the circumferential direction. Radially on the inside, the impeller shell 16 is firmly connected to an impeller hub 22 , which can drive, for example, a fluid pump arranged in a transmission.

In the interior 24 of the torque converter 10 is generally arranged with a 26 designated turbine wheel having a turbine wheel 28, one with the rigidly connected turbine hub 30 and the turbine 28 in the circumferential direction radschale successively several turbine wheel shovel comprises 32nd The turbine wheel hub 30 is connected radially on the inside to an output shaft, for example a transmission input shaft 32 , in a rotationally fixed manner by means of axial toothing or the like, in order to thus transmit the driving force of the housing 12 which is driven for rotation by an internal combustion engine or the like to this shaft 32 .

Arranged axially between the turbine wheel 26 and the pump wheel 18 is a stator wheel 34 , which comprises a plurality of stator wheel blades 36 which follow one another in the circumferential direction and are carried on a stator wheel ring 38 . The stator ring 38 is supported via a freewheel 40 on a support element (not shown), for example a support shaft or the like, which coaxially passes through the impeller hub 22 and coaxially surrounds the output shaft 32 , in such a way that the stator 34 in a circumferential direction around the axis of rotation A. is rotatable, but is blocked against rotation in the other direction. The freewheel 40 or the stator 34 is axially supported via two axial bearings 42 , 44 on the pump wheel 18 on the one hand and on the turbine wheel hub 30 on the other hand, these two bearings 42 , 44 being rolling element bearings, plain bearings or the like. The turbine wheel hub 30 , on the other hand, is in turn supported axially on the housing cover 14 in its radially inner region via a bearing 46 , the bearing 46 again being able to be a roller bearing or, as in the embodiment shown, a sliding body bearing made from a sliding ring.

The torque converter 10 further includes a generally designated 48 lock-up clutch with a clutch piston 50 , which can be pressed with its radially outer region with the interposition of a friction surface or friction lining arrangement 53 , in the illustrated embodiment of a ring-shaped friction element 52 , against a surface region of the housing cover 14 . Radially inside the piston 50 is axially movable, but sealed on the turbine hub 30 , radially outside the piston 50 , for example by a gear configuration with a driving element 54 , which is attached to the turbine shell 28 , rotatably connected. It should be noted that the latter non-rotatable connection can also be made, for example, with the interim storage of a torsional vibration damper or the like.

By the piston 50, the friction surface 53 and, that is, the friction ring 52, the interior 24 of the torque converter 10 basically divided into two areas. A first in the illustration between the piston 50 and the impeller shell 16 fluid chamber 56 contains in wesentli Chen that working fluid that is put into circulation for torque transmission between the impeller 18 and the turbine wheel 26 . A second fluid chamber 58 , which is formed between the piston 50 and the radially inside the friction surface arrangement 53 area of the housing cover 14 , serves to build up a counterpressure in order to be able to move the coupling piston 50 away from the housing cover 14 in a defined manner.

In the two fluid spaces 56 , 58 there is 10 working fluid during operation of the torque converter. For this purpose, various connection channel arrangements are provided, through which the working fluid can be introduced into or released from the respective fluid spaces 56 , 58 . A first connection channel arrangement comprises a space between the impeller hub 22 and the output shaft 32 or the support element for the stator 34 , not shown, this space being generally designated by 60 . This intermediate space leads to a gap 62 between the freewheel 40 and the turbine wheel hub 30 , via an opening area 64 past the bearing 44 radially outward and further between the stator ring 38 and the turbine wheel shell 28 into the first fluid space 56 . Radially outside, the working fluid also reaches a space region 66 of the first fluid space 56 formed between the piston 50 and the turbine wheel 26 and a space region 70 of the first fluid space formed radially outside between the housing cover 14 and a substantially axially extending section 68 of the piston 50 56 . It should also be pointed out that, of course, the fluid supply via the first connecting channel arrangement 60 , 62 , 64 can alternatively or additionally also take place in the region between the freewheel 40 and the bearing 42 and over the freewheel 40 .

The second fluid space 58 can be brought into connection with a working fluid source or a working fluid sump or reservoir via a second connecting channel arrangement. This second connection channel arrangement comprises a central passage opening 72 in the output shaft 32 , a region 74 formed between the housing cover 14 in its radially inner region and the turbine wheel hub 30 and a plurality of substantially radially extending passage openings 76 in the bearing element 46 , which openings then lead directly to the second fluid chamber 58 .

In the hydrodynamic torque converter 10 according to the invention, a third connection channel arrangement is also provided, which comprises a plurality of substantially radially extending passage openings 78 in the turbine wheel hub 30 . These passage openings 78 open radially outwardly in the space region 66 at its radially inner end, that is open substantially between the radially inner portion of the piston 50 and the radially inner portion of the turbine wheel 28 in the space area 66th Radially on the inside, these passage openings 78 open into a space 80 surrounding the output shaft 32 , which is fluid-tightly sealed axially on both sides of the passage openings 78 , this space 80 being formed by passage openings 82 which extend essentially radially in the output shaft 32 in connection with the along the Axis A extending through opening 72 is in the output shaft 32 . As a result of this third connection channel arrangement 78 , 80 , 82 , as will be described in the following, in particular when the lockup clutch 48 is slipping, the working fluid can leave the first fluid space 56 in the direction of the fluid sump or reservoir.

The friction surface arrangement 53 , ie in the illustrated embodiment the friction ring 52 , comprises a fluid channel arrangement 84 with a plurality of fluid channels 86 extending in the circumferential direction and in the radial direction. As can be seen in FIG. 2, the length of these fluid channels 86 can be slightly curved, but can also extend essentially in a straight line. It is now further assumed that the friction ring 52 is fixed on the piston 50 , for example by gluing or the like. In the radially inner end region 88 , an opening 90 in the piston 50 is then assigned to each fluid channel 86 , and in the radially outer region 92 of each fluid channel 86 , a further opening 94 is provided in the piston with respect to the opening 90 in the circumferential direction and in the radial direction. It should be noted that these two openings 90 , 94 are shown in a sectional plane in FIG. 1 due to the clearer representation. A fluid exchange can take place between the first fluid space 56 and the fluid channel arrangement 84 via the openings 90 , 94 , so that the working fluid present in the fluid space 56 can flow through the fluid channel arrangement 84 and thus in particular in slip operation, in which the housing cover 14 generally rotates faster than the piston 50 is provided for cooling the friction surface arrangement 53 , ie the friction ring 52 . It can be seen that in this state, in which the piston 50 is pressed against the housing cover 14 while the friction ring 52 is temporarily stored, then no fluid passage from the first fluid space 56 to the second fluid space 58 can take place, since the friction ring 52 has none at its inner peripheral surface area 96 Fluid chamber 58 has open through opening or the like.

Since no pressure difference between the two fluid spaces 56 , 58 can now ensure that the fluid is transported through the fluid channel arrangement 84 , other physical effects are used for this purpose. It is assumed, for example, that with respect to the friction ring 52 in the slip, the housing cover 14 rotates in the direction of an arrow P. Since the fluid channels 86 are open in their entire extension area on a surface or friction surface 98 of the friction ring 52 facing the housing cover 14 , the relative movement of the surface of the housing cover 14 with respect to the friction ring 52 and thus also with respect to the working fluid arranged in the fluid channels 86 creates a shear or frictional entraining effect, by means of which the working fluid arranged in the fluid channels 86 is carried in the direction of arrows F from the opening 90 to the opening 94 . That is to say, the fluid flows through the fluid channel arrangement 94 in the illustrated case from the inside radially, after it has entered through the openings 90 in the piston 50 , in the circumferential direction and radially outwards, and leaves the fluid channel arrangement 84 again through the openings 94 in the piston 50 . In order to obtain this entrainment effect caused by friction or shear forces, the fluid channels 86 must have an extension component in the circumferential direction.

When flowing through the fluid channel arrangement 84 , the working fluid then absorbs heat. Since the working fluid cannot reach the fluid sump or reservoir via the second fluid space 58 and the second connection channel arrangement 72 , 74 , 76 , which is in this state in communication with the second fluid space 58 , the third connection channel arrangement 78 , 80 , 82 according to the invention ensures that the heated working fluid can be removed from the first fluid space 56 and can reach the fluid sump or reservoir. It is particularly advantageous that the third connection channel arrangement 78 , 80 , 82 is connected to that space region 66 of the first fluid space 58 in which the working fluid heated after flowing through the fluid channel arrangement 84 will also accumulate. This means that there is no additional flow around the turbine wheel 26 or another assembly.

The removal of the heated working fluid can take place in that cooler via the first connecting channel assembly 60, 62, 64 the working fluid is fed into the first fluid chamber 56, which is then at the impeller 18 side facing the turbine wheel passes due to the inflow 26 directly to the converter circuit , there takes part in the torque transmission and can then reach the outside radially into the space region 66 , where it can initially contribute to cooling the friction surface arrangement 53 and can then be withdrawn again via the third connecting channel arrangement 78 , 80 , 82 .

In this way according to the invention, even in the case of a converter which basically complies with the two-line principle, the slip components of the lock-up clutch 48 can be cooled without reducing the coupling efficiency thereof by working fluid entering the second fluid chamber 58 .

It can be seen that the third connection channel arrangement 78 , 80 , 82 and the second connection channel arrangement 72 , 74 , 76 open into one another, but at a region located away from the second fluid space 58 radially inside the bearing 46 . In addition, the opening cross section of the passage openings 78 , that is to say the fluid flow resistance of the third connecting channel arrangement 78 , 80 , 82 , is designed in such a way that a relatively high flow resistance is provided here, in any case a higher flow resistance than is offered to the fluid when flowing through the fluid channel arrangement 84 . In this way it is achieved that a pressure compensation between the first fluid space 56 and the second fluid space 58 cannot take place via the connection of the third connection channel arrangement 78 , 80 , 82 to the second connection channel arrangement 72 , 74 , 76 . In addition to the fact that the coupling efficiency of the lock-up clutch 48 is increased by avoiding the passage of fluid from the first fluid space 56 to the second fluid space 58, the configuration according to the invention also provides the essential advantage that the extracted, heated working fluid without the formation of substantial eddies, the interior 24 of the converter 10 , which would generally be the case if the working fluid leaves the interior 24 via the second fluid space 58 .

Fig. 3 shows an alternative embodiment of the fluid passage means 84 and the fluid channels 86 thereof. It can be seen that the fluid channels 86 here in their circumferential center region have a channel section 100 which extends essentially from the radially outward to the radially inward and in the circumferential direction and radially outside and radially inward adjacent to this channel section 100 and have respective channel sections 102 , 104 which only extend in the circumferential direction . Such a configuration of the fluid channels 86 is particularly advantageous if the friction ring 52 is not attached to the piston 50 but to the housing cover 14 . In this case, respective pairs of openings 90 , 94 would be formed in the piston 50 , which also have a circumferential distance from one another to the existing radial distance, which is dimensioned such that when the opening 90 lies in the end region 88 of the fluid channel 86 , the radially outer opening 94 lies in the transition region between the inclined section 100 and the other circumferentially extending section 104 , and vice versa. In this way, it can be ensured that, with relative rotation between the friction ring 52 rotating with the housing cover 14 and the piston 50, a longest possible overlap between the openings 90 , 94 and the associated fluid channels 86 is achieved. If, in this case, the housing cover 14 rotates again in the direction P with respect to the piston 50 , the fact that the shear effect is generated between the fluid entrained by the friction ring 52 and arranged in the fluid channels 86 and the slower rotating piston 50 is now generated , the fluid in a direction opposite to the illustration of FIG. 2 flow in a direction F '.

It should be pointed out that the grooves in the friction ring 52 or the friction surface arrangement 53 can be embossed or stamped or can be introduced in a different way during the production of this friction ring 52 . Furthermore, the components having friction surfaces of the friction surface arrangement 53 can be formed from any material that can be used for this purpose.

FIGS. 4 and 5 show an alternative embodiment of the friction ring 52, in particular regarding the design of the fluid channels 86 of the fluid channel assembly 84. On the one hand, it can be seen that the fluid channels 86 are open on an outer peripheral surface area 106 of the friction ring 52 . This means that the working fluid will pass through the opening 90 in the piston 50 into the end region 88 of the fluid channels and leave the fluid channel arrangement 84 in the region in which the fluid channels 86 are open to the outer peripheral surface 106 . This can also be seen in the illustration in FIG. 6. Further, it can be seen in Fig. 4 in that the fluid channels are in which attached to the piston 50 the friction ring 52 86 is provided not over the entire thickness of the friction ring 52 away, but only formed of the friction ring 52 in the surface region 98 and are open, with which this friction ring 52 will move along the surface of the housing cover 14 . This is also possible in the embodiment according to FIGS. 1-3. For this purpose, each of the fluid channels 86 is assigned a further opening 108 in the friction ring 52 , which is aligned with an opening 90 when the friction ring 52 is attached.

In this embodiment, in which, due to the circumferential extension component of the fluid channels 86 , the above-mentioned shear or friction effect in turn contributes to the fluid transport in the direction F, a further physical effect leads to the build-up of a pressure difference between the inlet area at the opening 90 and the outlet area at the Outer peripheral surface 106 . In slip operation, as already stated, the housing cover 14 will rotate faster than the piston 50 . This has the consequence that in the outlet area near the outer circumferential surface 106, the working fluid arranged in the space area 70 is taken along by the frictional action with the surface of the housing cover 14 to a faster rotation than will be the case in the vicinity of the openings 90 in the piston 50 . The result of this is that a centrifugal force of different magnitude will result in a pressure difference which will result in a lower pressure in the area of the outer peripheral surface 106 than in the area of the opening 90 and will thus support the flow in the direction F. This effect cannot occur in the embodiment according to FIGS. 1-3, since there both openings 90 , 94 lead to the same spatial region 66 , in which the fluid is carried along by the rotation of the piston 50 in the circumferential direction, so that there are no different rotational speeds here of the fluid can be generated or different web speeds and resulting pressure differences inside and outside the fluid channel arrangement are compensated.

FIG. 5 shows an embodiment variant in which the friction ring 52 is again fixed on the housing cover 14 and the fluid channels 86 not extending over the entire thickness of the friction ring 52 are now open on the surface of the friction ring 52 facing the piston 50 . A preferred embodiment of such fluid channels is shown in FIG. 7. It can be seen that here again a channel section 110 extending essentially in the circumferential direction and a channel section 112 extending radially outward from this channel section 110 are provided. The essentially circumferentially extending channel section 110 lies in the radial area in which the opening 90 is also positioned in the piston 50 , so that by moving the opening 90 along the channel section 110, as long as possible coverage of each fluid channel 86 with the associated one or opening 90 located in the area is achieved. Due to the attachment of the friction ring 52 to the housing cover 14 , a flow in the direction F 'will again occur, which is now essentially generated by the shear or friction effect mentioned above. It should be noted that in the embodiment in which the fluid channels 86 are open radially outward, ie on the outer circumferential surface 106 of the friction ring 52 , a purely radial extension of the fluid channels 86 is also conceivable, in which case solely through the pressure difference generated the fluid transport will take place.

FIG. 8 shows an embodiment of a friction ring 52 or a friction surface arrangement in which the fluid channels 86 of the fluid channel arrangement 84 extend exclusively in the circumferential direction, ie are formed by circular segments, so that the fluid can flow here essentially only in the circumferential direction. This embodiment, in which there is therefore no fluid line contact with either the inner circumferential surface 98 or the outer circumferential surface 106 , is particularly suitable again for a friction ring 52 which is fixed on the piston 50 and in which the end regions 88 , 92 of the fluid channels 86 are then each in alignment with the openings 90 , 94 are in the piston. In this embodiment, it is also conceivable to provide a plurality of such fluid channels 86 in a radially staggered manner, which can then partially overlap in the circumferential direction, so that here, too, all circumferential regions of the friction ring 52 can ultimately be cooled. In the embodiments described above, it is advantageous to also design the fluid channels 86 in such a way that there is essentially no uncooled area in the circumferential direction. This means that it can advantageously be seen here that the individual channels 86 also overlap in the circumferential direction, as is the case in the embodiment forms of FIGS. 3 and 7.

Fig. 10 shows a modification of hydrodynami's torque converter 10 according to the invention, wherein the friction surface 53 again comprises a friction ring 52, which for example is mounted here on the piston 50. Similar to the embodiment shown in FIG. 6, the channels 86 of the fluid channel arrangement 84 are open radially towards the outside and, as shown with arrows in FIG. 10, allow the fluid to enter from the radial outside. In this embodiment too, the fluid channels 86 do not necessarily have to extend over the entire material thickness of the friction ring 52 . Rather, they could only be axially open to the side facing the housing cover 14 or the side facing the piston 50 .

A further modification of the hydrodynamic torque converter according to the invention is shown in FIG. 11. It can be seen that in this embodiment, cooling is still provided by the self-induced flow in the area of the friction ring 52 , similar to that described in the embodiment according to FIG. 1. Nevertheless, an opening or a plurality of openings 150 is now provided in the clutch piston 50 , which spaces 56 , 58 bring the two fluid spaces together. The fluid can then flow out radially inward via the channel regions 76 , as is known per se in converters of the 2-line type. That is, although in order to maintain a fluid exchange, a fluid passage to the fluid space 58 must take place and the contact pressure of the piston 50 is thus reduced, the advantageous effect of the self-induced flow in the area of the friction surface arrangement can be used.

In the embodiment according to FIG. 12, which essentially corresponds again to the embodiment according to FIG. 11, the fluid channels 86 are in turn open radially outwards and thus allow the fluid to enter the fluid channel arrangement 84 from the radially outside.

A further modification of the hydrodynamic coupling device according to the invention is shown in FIG. 9 and FIG. 13. It can be seen that here the piston 50 is not coupled to the turbine wheel 26 for common rotation, but rather that a friction surface element 120 , for example a lamella 120 , is provided which is in circumferential driving engagement with the driving element 54 with a gear configuration or argument. In this case, the piston 50 is connected in a rotationally fixed manner to the housing cover 14 , for example a hub centrally attached to it. Friction rings 52 , 52 ′ are again provided on both axial sides of the lamella 120 , and passage openings 122 , 124 are formed in the lamella 120 . Fluid which, for example, reaches the fluid channel arrangement 84 ′ of the friction ring 52 ′ via the openings 90 can continue to pass through the opening 124 into the fluid channel arrangement 84 of the friction ring 52 and can from there via the opening 122 again into the area of the fluid channel arrangement 84 ′. arrive and then exit the opening 94 into the room area 66 . It should be noted that any of the configurations of the fluid channels 86 described above can be used with the friction rings 52 , 52 ′ carried on the lamella 120 . Furthermore, it should be pointed out that, of course, the friction surface arrangement 53 here can have not only one but a plurality of such disks 120 with friction rings 52 , 52 ′ carried thereon, between which a respective disk element is then positioned, which is non-rotatably connected to the piston 50 .

It can be seen in particular in FIG. 13 that, even in this embodiment, fluid passage from room area 56 to room area 58 is not required. Rather, here too, a channel region 78 is created in the turbine wheel hub 30 , through which fluid flowing in from the space region 66 can reach radially inward in order to reach the interior of the output shaft 32 through the openings or channels 82 . The channels or the channel arrangement 76 are then provided in a lid hub 152 which is fixedly connected to the housing lid 14 and which enables fluid or volume compensation in the fluid space 58 . Here, too, the fluid space 58 is connected to the opening 72 in the output shaft 32 via these channels 76 . It should also be pointed out that the piston 50 is connected to the housing 12 , ie the cover hub 152 , in a rotationally fixed manner with respect to the latter, but is axially movable with respect to a drive arrangement, generally designated 154 . For example, the piston 50 is o provided with an internally toothed coupling member 156 by riveting. Like. Fixedly connected, said coupling element 156 non-rotatably but axially movably seated on an outer toothing on the cover hub 152nd A biasing spring 158 , for example in the form of a plate spring, is supported on the housing cover 14 on the one hand and on the coupling element 156 on the other hand and thus biases the piston in the direction of the disengagement position.

A modification of the torque converter shown in FIG. 13 is shown in FIG. 14. Here, too, at least one passage opening 150 is again provided in the piston 50 , which now provides for a fluid outflow into the fluid chamber 58, which radially inwards via the fluid channels 76 . In order to enable this fluid outflow, as in the embodiment according to FIG. 14, a central passage opening 162 is provided in the cover hub 152 in a cap-like guide part 160 inserted therein. In the embodiment according to FIG. 14, although a fluid exchange between the two fluid spaces 56 and 58 will take place here, the self-induced flow through the friction linings 52 , 52 described above with reference to FIG. 9 can also take place when the bridging clutch arrangement 48 is engaged '' be provided for cooling in hatching.

The selection of which of the torque converters shown above is used in a drive system depends on the system conditions. For example, if only a relatively weak feed pump can be used to generate the fluid pressure in the fluid space 56 , the embodiment in which the two fluid spaces 56 , 58 are not connected to one another is advantageous, since a low fluid pressure due to the lack of fluid leakage between the two is then also advantageous Fluid spaces 56 , 58 contributes to the generation of a correspondingly high torque transmission capacity. A further increase in the torque transmission capacity can be achieved if the variant shown in FIGS . 13, 14 and 9 is provided with two surface pairs rubbing against each other. In all of these design variants, even if no fluid passage between the two fluid spaces 56 , 58 is possible via the friction linings, sufficient heat dissipation can be achieved by the self-induced flow in the area of the friction linings, so that overheating, particularly in slip operation, cannot occur.

With reference to FIGS. 15-26, various design variants of friction linings or friction surface arrangements, which contribute to the generation of such a self-induced flow through the friction linings with the advantageous feature that no fluid exchange between the individual fluid spaces must be present, are described below.

FIG. 15 is a friction surface 53 in the form of a friction ring 52 which has a plurality of to a radial line R extending perpendicular fluid channels 86th These fluid channels 86 run in a straight line and open in their two end regions 88 , 92 to the same radial side of the friction ring 52 , namely the radial outer side thereof. The fluid channels 86 are thus connected in both end regions to the fluid space 56 of the torque converters described above. If such a friction ring 52, for example, glued to a piston, so it that with which the Belagsnutung or channels 86 surface having the housing cover 14 is located opposite, so is through the substantially open in the circumferential direction of fluid channels 86 forcibly sets the radially outside of the friction lining 52 subsequent fluid pushed through, so that in addition to the delivery effect generated by shear forces, an enhanced delivery effect can be obtained. It can be seen that the friction ring 52 also has fluid channels 170 which are open towards the radial inside and are also approximately symmetrical with respect to a radial line R. The essential task of these fluid channels 170 is to produce tear-off edges in their end regions which, when the friction lining 52 rotates, cause turbulence and thus a reduced drag torque in the fluid arranged radially within it. Nevertheless, these fluid channels 170 , which are now open to the other fluid chamber 58 , also contribute to cooling in the same way. However, step-like profiles or blind hole-like bores on the inside of the friction ring 52 could also serve for the effect of reducing the drag torque.

Since this pattern of fluid channels is essentially symmetrical, such a friction lining is suitable for use, for example, on both axial sides of a plate 120 , as is provided in FIG. 9.

FIG. 16 shows a friction ring 52 , in which, as can be seen in FIG. 15, the fluid channels 86 running in pairs next to one another in or near one of their end regions, namely the end region 92 , are curved radially outward so that they approximate are open in the radial direction to the outer peripheral region of the friction ring 52 . The fluid entering via the openings 88 is thus conveyed more radially outwards when the end regions 92 are approached by the centrifugal force, so that increased fluid removal with a corresponding suction effect in the region of the inlet openings 88 is ensured. In order to provide approximately uniform volume or surface cooling in this embodiment too, the inner channels 86 of the fluid channels arranged in pairs are in fluid exchange connection with a connecting channel 174 . In this way, the surface areas formed between the individual internal fluid channels 86 can also be cooled. If such a friction ring 52 is to be used in an arrangement as shown in FIG. 9, it is advantageous to have two mirror-symmetrical friction linings 52 ready, so that the same centrifugal force-related delivery effect will occur on both axial sides of the lamella 120 .

FIG. 17 shows an embodiment variant in which fluid channels 86 are again provided in pairs in the friction ring 52 , which are essentially V-shaped open radially towards the outside. That is, between their end regions 88 , 92 they preferably have a curvature region 176 in a central region.

The friction rings 52 described above with reference to FIGS. 15-17 are particularly advantageous because, even when used in conjunction with the plate shown in FIG. 9, they do not take into account the friction ring or friction lining provided on the other axial side of the plate can be attached. A fluid exchange always takes place on the same radial side of the friction surface arrangement 53 , in the case shown the radially outer side, without a fluid passage in the axial direction through the plate being necessary.

FIGS. 18 and 19 show a friction surface 53, as it can be applied to a hydrodynamic torque converter according to the Fig. 9 13 or 14. A lamella 120 is shown which carries a friction lining 52 or 52 'on both axial sides of the lamella carrier 180 , which is generally formed from sheet metal material. It should be pointed out that in the illustration in FIG. 18, the friction lining 52 ′ is attached to the non-recognizable axial side of the disk carrier 180 . A fluid channel arrangement 84 with a plurality of fluid channels 86 is provided in each of the friction linings or friction rings 52 , 52 ′. These fluid channels 86 of the friction ring 52 or 86 'of the friction ring 52 ' extend approximately rectilinearly from the radially outer region of the respective friction rings 52 , 52 'obliquely inwards and end in their region 92 or 92 ' in such a way that these end regions 92 or 92 ' 92 'of the two friction rings 52 , 52 ' axially overlap one another. In this overlap area, a passage opening 182 is then provided in the disk carrier 180 , through which fluid which has flowed through a fluid channel 86 can pass into the adjoining fluid channel 86 ′ located on the other axial side of the disk carrier 180 . From this fluid channel 86 ′ or its end region 88 ′, the fluid can then enter the fluid space 56 radially outward again.

In the embodiment, as shown in FIGS. 18 and 19, there is the essential advantage that the two friction rings 52 , 52 'can be identical to each other. When assembling, care must be taken to ensure that the end regions 92 , 92 ′ can be arranged to overlap one another, in particular in a region in which an opening 182 is provided. The opening 182 could ultimately also be drilled after the friction rings 52 , 52 'have been attached to the disk carrier 180 . The fluid channels 86 , 86 'can extend through the entire material of the friction rings 52 , 52 ', but can also only be in a thickness range. Depending on whether the fluid channels 86 , 86 'are then on the side facing away from or facing the disk carrier 180 , a corresponding passage opening must also be provided in the friction rings 52 , 52 ' associated with the opening 182 or each opening 182 .

A modification of this embodiment is shown in FIG. 20. It can be seen that here the lying on both axial sides of the disk support 180 portions 84, 84 'of the fluid passage means in pairs to each other substantially parallel fluid channels 86 and 86' include. In this way, a relatively good distribution of the cooling effect over the entire surface can be ensured with a relatively small channel width.

A further modified embodiment of a friction surface arrangement 53 is shown in FIGS. 21-23. Here, too, two friction rings 52 , 52 'are arranged on both axial sides of a disk carrier 180 . The friction ring 52 lying at the front in the illustration is shown in FIG. 22 and in turn has a plurality of fluid channels 86 which extend essentially in a straight line and obliquely from radially outside to radially inside. The fluid channels 86 again end in an end region 92 , in which a passage opening for the fluid can optionally be provided in the friction ring 52 . The friction ring 52 'to be provided on the other axial side in turn has fluid channels 86 ', which likewise extend from the radially outside, ie from their radially outwardly open end region 88 ', essentially in a straight line and obliquely radially inwards and in their radially inner end region 92 'open into a connecting channel 184 '. This connecting channel 184 'is a ring-like channel which is preferably completely continuous in the circumferential direction. Through this connecting channel 184 ', an even better distribution of the cooling effect is achieved. If the friction ring 52 'is designed such that the fluid channels 86 ' and the connecting channel 184 'extend only over a partial depth of the material, then this friction ring 52 ' is preferably on the side on which the channels 86 ', 184 ' towards the surface are open, set on the disk carrier 180 . The openings 182 then to be provided in the disk carrier 180 can be positioned such that they open directly into the connecting channel 184 ′, so that, at least in the case of the friction ring 52 ′, there is no need to pay attention to a defined circumferential positioning. When such a friction ring 52 'is positioned in the other orientation, ie the channel grooves open towards the surface point away from the disk carrier 180 , passage openings must also be provided in the friction ring 52 ', through which openings the fluid can then flow into the channels 86 '.

It should be pointed out that, in the embodiment according to FIGS. 21-23, two identical friction rings can of course also be used, as shown for example in FIG. 23. If both friction rings are then positioned with the surface to which the groove-like channels 86 ', 184 ' are open facing the disk carrier 180 , special care must not be taken when attaching them that there are any openings in the friction rings with corresponding openings in the disk carrier 180 are aligned. Furthermore, it should also be pointed out that, of course, also with this embodiment on the inside, ie the radially inner side, the friction rings have structures, for example through teeth or introduced openings or bores for generating turbulence and thus for reducing the drag torque when driving the radially inside arranged fluids can contribute. An advantage of an embodiment in which two friction rings are provided on a lamella 120 can result from the fact that different pressure ratios occur on both axial sides of the lamella carrier 180 during rotation, since one axial side of the fluid space 56 , in which flow conditions may arise sets a suction effect, faces more. A pressure difference then arises between the opening or end regions 88 , 88 'of two fluid channels 86 , 86 ' which are connected to one another, so this is also additionally supported by the shear effect on the piston or on the housing cover of the fluid flow.

Another modification of a friction surface arrangement is shown in FIGS. 24-26. Here, too, a lamella 120 is shown, in which friction rings 52 and 52 'are attached to a lamella carrier 180 on both axial sides. These friction rings 52 and 52 'can be seen in FIGS. 25 and 26. The friction ring 52 substantially corresponds again to the above-described previously and in FIG. Friction ring 22 shown with the slanted and the end portion 88 in the radially outer region of the friction rings 52 is substantially ending straight radially inwardly extending fluid channels 86 in an end portion of the 92nd Depending on whether the channels 86 extend through the entire material thickness thereof, may be again fluid passage openings for axial passage of fluid through the friction ring 52 is provided in the end region 92 in incomplete extension of the channels through 86th The friction ring 52 'has two ring-like connecting channels 184 ', 186 'which run essentially concentrically to one another and which are connected by an undulating channel arrangement 188 '. The aim, as in the previously described embodiments, is to obtain a surface distribution of the channel regions that is as uniform as possible, which should take up approximately 30% of the surface of the friction rings. This can be set on the one hand by the number of channels and on the other hand by the channel width.

It can be seen that the connecting ducts 184 ', 186 ', which ultimately connect individual sections of the undulating duct structure 188 'to one another, do not extend either radially inwards or radially outwards, so that the fluid duct arrangement region 84 ', at least in the engaged or partially engaged state, is one The lock-up clutch is neither in fluid exchange with the fluid space 56 nor with the fluid space 58 - leakage losses are disregarded. In the connecting channel 184 ', a plurality of fluid passage openings 190 ' are provided, which we are again positioned with corresponding fluid passage openings in the disk carrier 180 , in order to allow fluid in the end region 92 of the fluid channels 86 of the friction ring 52 to reach the other axial side of the connecting channel 184 '. From this connection channel 184 ', the fluid can then be distributed over the entire fluid channel arrangement region 84 '. In order to allow the fluid to flow away, a plurality of fluid passage openings which follow one another in the circumferential direction are provided in the piston, for example in the radial region of the connecting channel 184 ′, as has already been shown at 90 and 94 in FIG. 9. The fluid thus passes directly into the space 66 between the clutch piston 50 and the turbine wheel shell without being directed radially outward. Since the entry area into the fluid channel arrangement or the fluid channel arrangement is now at a different axial and radial level than the exit area, which lies, for example, in the area of the openings 90 in FIG. 9, pressure differences generated in the axial direction as well as in the radial direction can occur here contribute to the generation of an efficient fluid flow. If the fluid channel arrangement regions 84 , 84 'are then also open to the respectively opposite friction surfaces of the piston 50 or the housing cover 14 , the shear forces which arise in the rotary operation or in the slip operation also contribute to a further conveyance of the fluid. In order to prevent all openings in the disk carrier 180 and all openings in the piston 50 from being axially aligned with one another in this arrangement, the respective number of openings should differ by at least 1. Furthermore, it could be considered not to provide the fluid outlet in the region of the radially inner opening or openings 90 in FIG. 9, that is to say not in the connection channel 184 ', but radially further out, in the connection channel 186 '. It is thus forcibly ensured that the fluid has flowed through the entire fluid channel arrangement region 84 ′ before it can flow back into the fluid space 56 .

A further alternative embodiment of a friction surface arrangement 53 according to the invention or an annular friction lining according to the invention is shown in FIG. 27. It can be seen that the fluid channel arrangement 84 provided in this friction lining 52 comprises a plurality of fluid channels 86 which are arranged one after the other in the circumferential direction, but which are now combined into groups G. That is, each group G has two fluid channels 86 of this type. The distance between individual fluid channels 86 of a group G, which is represented, for example, by the size I in FIG. 27 and should be in the region of 5 mm in order to obtain a stable covering arrangement, is smaller than the distance between two groups G, that is to say those lying adjacent to one another Fluid channels 86 of two adjacent groups G, which is represented, for example, by the angle variable W ₃ , which is in a range of 10 ° -20 °, preferably c 19344 00070 552 001000280000000200012000285911923300040 0002010009576 00004 19225a. 15 °. In this way it becomes possible to arrange so-called pad locks in the free areas 214 of the friction lining 52 formed between two groups G. These covering locks then connect individual covering segments to one another to form a ring configuration, each of these five covering segments then carrying a group G of the fluid channels 86 .

It can also be seen that the fluid channels 86 in FIG. 27 have a central section 200 which extends approximately tangentially in the circumferential direction or approximately to a radial line and which extends via curvature areas 202 , 204 into the end areas 88 and 92 , which then in turn radially inwards are open, that is, are open to the radially inner end region of the friction lining 52 . The radius of curvature of these curvature areas 202 , 204 should be in the range of 12-23 cm, preferably approximately 17.5 cm, in order to provide the lowest possible flow resistance. The angle α, at which the end regions 88 , 92 are inclined with respect to a tangential line T, is in the fluid channels 86 shown in FIG. 27 in the range between 40 ° -60 °, preferably approximately 50 °. In this way it is ensured that the material sections 216 separated by the fluid channels 86 from the remaining area of the friction lining 52 , if the fluid channels 86 are formed by punching, do not have too acute angles and are therefore relatively stable. Furthermore, the distance d which the fluid channels 86 have in their central region 200 from the outer circumference of the friction lining 52 should not be less than 3 mm in order to obtain a stable arrangement here as well. The length L of the central region 200 of the fluid channels 86 , which extends approximately in the circumferential direction or tangential direction, should be in the range between 2-5 cm. In this way, an effective advance of the fluid is generated by shear with respect to the surface moving along the friction lining 52 , for example the converter housing or the clutch piston.

A geometry of the fluid channels, as shown in FIG. 27, has a number of advantages. On the one hand, the configuration, which is open radially inwards, is preferred for production-technical reasons, since such a friction lining can be produced, for example, by stamping technology while simultaneously producing the fluid channels 86 , with a radial lining inner area before being attached to a friction lining carrier 180 ( not shown in FIG. 27) Fixing or retaining ring section is retained, which protrudes radially on the inside over the friction lining carrier 180 and is only separated after the entire friction lining 52 has firmly adhered, so that the regions 216 , which have no connection to the remaining region of the friction lining 52 in the case of stamping technology, also in defined positioning with respect to the friction lining carrier 180 are held. The relatively large angle of inclination α has the advantage that the drag torque with which such a friction lining is carried along a moving surface when the bridging clutch is not engaged can be reduced. Too pointed material areas and the resulting risk of them breaking off are minimized. The relatively long central region 200 which extends in the circumferential direction leads to an effective advance of the fluid by shear action and at the same time contributes to a very good and uniform cooling of the entire surface of the covering. The division into individual groups G ensures that the pad locks can lie between these groups, and by maintaining a certain minimum distance I between the individual fluid channels 86 within a group G, a high stability of the friction linings 52 can also be ensured in this intermediate area. The same also applies to compliance with a minimum thickness d in the radially outer region of the friction lining 53 . Furthermore, it can be seen in FIG. 27 that a relatively uniform penetration of a friction lining 52 with fluid channels is achieved by the channel geometry provided there, which likewise contributes to a good uniform cooling capacity. The curvature-like transition, ie avoiding any edges or corners, between the end regions 88 , 92 and the central region 200 minimizes the flow resistance within the fluid channels.

It should be pointed out that, of course, in the arrangement shown in FIG. 27, for example, between two fluid channels 86 of a group G, there could still be another fluid channel, which, however, is then open to the outside with its two end regions, ie to the radially outer end region of the friction lining 52 is open. Such a fluid channel would then preferably be produced by embossing, since it would be difficult to provide a fixing section in the radially outer region that held it before gluing to the friction lining carrier 180 due to the toothing provided on the friction lining carrier. Furthermore, it is of course possible, in the case of a group G, to design, for example, a fluid channel 86 with its end regions 88 , 92 open radially inwards, and to design a subsequent one with its end regions 88 , 92 open radially outwards.

53 may be provided to FIGS. 28 and 29 show various cross-sectional geometries, such as arrangement of all previously described embodiments of a friction surfaces. Fig. 28 shows a conical shape to the channel base, that is, to the friction lining carrier 180 tapering cross-sectional geometry. That is, this is a geometry in which the channel walls 206 , 208 extend approximately rectilinearly towards the channel base and approach one another. Such a tapering cross-sectional profile, which can be provided in particular in the end regions 88 , 92 , further reduces the drag torque already mentioned, since ultimately the fluid in the manner of a nozzle or wedge effect in the region between the friction lining 52 and an opposite one Surface is pushed and thus a forced lifting of such a friction lining 52 is generated from an opposite surface in the disengaged state.

In the embodiment according to FIG. 29, the transition between the friction surface 212 and the channel walls 206 , 208 is designed with a curvature region 210 , which can ultimately extend as far as the friction lining carrier 180 .

A modification of the embodiment shown in FIG. 27 is shown in FIG. 30. It can be seen here that there is a difference in that the curvature regions 202 , 204 extend almost completely to the radially inner end region of the friction lining 52 . That is, the end regions 88 , 92 are either formed directly by the curvature regions 202 , 204 or by relatively short rectilinearly extending channel sections. Here, too, the angle α, which is formed between a straight extension of the end regions 88 , 92 in their outlet section and the tangential line T, is preferably in the region specified above. The radius of curvature R _K1 , which was already mentioned above with reference to the curvature regions 202 , 204 in FIG. 27, is also preferably in the specified size range here in order to provide the lowest possible fluid flow resistance when flowing through the fluid channels 86 .

A further alternative embodiment of a friction surface arrangement 84 according to the invention is shown in FIG. 31. A friction lining 52 can be seen here, which is applied to a friction lining carrier 180 and has a plurality of fluid channels 86 , 86 ′ which follow one another in the circumferential direction and are arranged in pairs. In each pair of fluid channels 86 , 86 ', these are arranged in a radially staggered manner and have a curvature region 176 and, on both sides thereof, end regions 88 , 92 which extend approximately rectilinearly and which are open radially inwards, ie to the radially inner end region of the friction lining 52 are open.

The fluid channels 86 , 86 'extend approximately parallel to one another. The fluid channel 86 preferably has a radius of curvature R _K3 in the range of 6-8 cm, preferably approximately 6.8 cm, in its area of curvature 176 , and the fluid channel 86 'preferably has a radius of curvature R _K2 in the range of 12-8 cm in its area of curvature. 14 cm, preferably about 12.8 cm. The opening angle W ₄ formed between the two end regions 88 , 92 of the fluid channel 86 is preferably in the range from 60 ° -70 °, most preferably approximately 65 °, and the opening angle W ₅ between the end regions 88 , 92 of the fluid channel 86 ' is preferably in the range between 65 ° -75 °, most preferably approximately 70 °. Even with such an arrangement, a very uniform flow through the friction lining can be obtained, it being possible, for example, to think of providing at least one further fluid channel in the friction lining regions between two pairs of fluid channels 86 , 86 ', which is then open to the outside radially and could for example be designed as shown in FIG. 17. Even with such an arrangement, the fluid channels 86 , 86 ', which are open radially inwards, could again be formed by punching technology, that is to say extending through the entire material thickness of the friction lining 52 , while the fluid channels opening radially outwards could then be embossed, that is to say only in a specific one Thickness range of a friction lining could be formed.

It should be pointed out once again that the friction linings or friction surface arrangements described above, in particular also the arrangements described with reference to FIGS . 27-31, can be used with any type of lock-up clutch or coupling device. This means that such a friction lining could either be attached to a clutch piston of a lock-up clutch, as can also be seen in FIG. 4 or 5, but could also be attached to the housing. Furthermore, it is of course also possible to use a lock-up clutch in which a so-called clutch plate with a friction lining carrier and friction linings provided on both sides thereof is used. Of course, several such slats can then be provided in succession in such an arrangement. Furthermore, the use is of course independent of how a torque converter or a fluid clutch is designed, that is, for example, possible regardless of whether a fluid passage opening in the clutch piston 50 is provided or whether, for example, the fluid transport is provided via a fluid channel arrangement in the turbine wheel hub.

With regard to the previously described embodiments, in which the individual fluid channels are open radially inward, it should be stated that such an arrangement during operation has the following essential advantage over an embodiment in which the fluid channels are open radially outwards. For this purpose, consider, for example, FIG. 4 or FIG. 5. Cover grooves are shown there, which are open radially outwards. If the fluid pressure is increased in such an arrangement in the space area 56 for engaging the lockup clutch, this increased fluid pressure is of course also present at the inlet and outlet areas of the fluid channels of the fluid channel arrangement 84 . This is a relatively high fluid pressure, which must be sufficient, for example, to bring the lockup clutch into a completely slip-free state. In the space 58 between the clutch piston 50 and the housing cover 14, however, there is a significantly lower pressure, in particular if the passage openings 150 described above are not provided in the clutch piston. However, this results in the fact that in the embodiment with fluid channels open radially outward, a relatively large force is applied between the friction lining 52 and the component on which it then rubs, which acts on the friction lining in the direction away from this component. If, however, the fluid channels are in connection with the space area 58 by opening radially inwards, in which a fluid pressure which is then significantly lower than the space area 56 prevails, the fluid pressure within the fluid channels 86 is correspondingly lower, with the result that there is also a clear one smaller the friction lining 52 is generated by the force pushing away on this frictionally engaging component, so that ultimately the pressure required to maintain a certain engagement state can also be lower in the space region 56 . Regarding these considerations, however, it should be stated that they are based on the fact that both end regions of a fluid channel are open on the same radial side, and not, as shown in FIGS. 4 and 5, a through opening through the clutch piston 50 is provided. In this respect, FIGS. 4 and 5 have only been used to explain the advantage described above with regard to the construction of a torque converter with the two spatial areas 56 , 58 .

The foregoing are various possibilities of arranging the friction surface or friction linings or friction rings have been shown, either alone or combined with each other for a self-induced flow in the Area of rubbing surfaces can take care of without a Forced fluid passage from one fluid space to one other fluid space would be required. This enables the construction of hydrodynamic coupling devices with relatively little funding  a pressure pump for the working fluid, since pressure loss is avoided can be. The various fluid channel arrangements shown are only by way of example. So it is of course possible that the shown each rectilinear channel sections curved or corrugated run or that more than two such channel areas side by side extend horizontally through the respective friction rings. Furthermore, it is of course possible with all the illustrated friction rings Grooves formed on a surface of channels or channel areas to design completely through the material, or only one To design partial depth so that on one axial side Material of a friction ring still seals such groove-like channels. There are then, if necessary, provide passage openings in the remaining material, which is the axial passage of a fluid to another fluid channel arrangement or allow another fluid channel arrangement area.

By the present invention, which is not only as hydrodynamic Torque converter, but also as a hydraulic clutch without Stator can be formed, it is ensured that despite possible Cooling the friction surface arrangement, a fluid passage from the fluid space, which in the indented or partially indented state of the over bridging clutch has an increased fluid pressure to a fluid space that has a lower fluid pressure in this operating state, does not occur. The ability to drain the heated working fluid it is ensured that a gradual warming of the whole Systems in the event of prolonged slip operation of the lock-up clutch will not occur. This fluid discharge can take place in such a way that a joint connection of the fluid space with lower fluid pressure and that connection channel arrangement, via which from the fluid space higher fluid pressure working fluid is discharged, is provided so that especially for torque converters with 2-line system in fluid exchange can be provided in a simple manner. Of course, the present invention also applies to a torque  ment converter with 3-line system applicable, in which then the two independently controllable fluid lines, which in lead the room in which the turbine wheel is arranged, the Fluid can be supplied or removed.

Furthermore, it should also be pointed out that the principle of the present invention can of course also be used in a lock-up clutch in which the piston for producing the lock-up state cannot be moved towards the housing cover 14 , but in the opposite direction to one with the housing cover 14 or the housing 12 rotatably connected abutment element can be pressed. In this case too, a friction surface arrangement, as described above, can be used between the piston 50 and the abutment element, which is then again configured such that it passes a fluid through to the fluid space in which a reduced fluid pressure prevails does not exist is.

Claims (46)

1. hydrodynamic coupling device, in particular torque converter, the interior ( 24 ) of which can be separated by a coupling element ( 50 ) of a lock-up clutch ( 48 ) and a friction surface arrangement ( 53 ) into a first fluid space ( 56 ) and a second fluid space ( 58 ), the Coupling element ( 50 ) with intermediate arrangement of the friction surface arrangement ( 53 ) can be pressed onto a housing ( 12 ) or a component connected to it, and wherein in the friction surface arrangement ( 53 ) a fluid channel arrangement ( 84 ) is seen in which working fluid from the first fluid space ( 56 ) can occur and from which working fluid can only exit to the first fluid space ( 56 ), furthermore working fluid can be supplied to the first fluid space ( 56 ) through a first connecting channel arrangement ( 60 , 62 , 64 ) and through a second connecting channel arrangement ( 72 , 74 , 76 ) working fluid can be directed to and / or out of the second fluid space ( 58 ), characterized d By a third connection channel arrangement ( 78 , 80 , 82 ), through which working fluid can be drained from the first fluid space ( 56 ) at least when the coupling element ( 50 ) with the intermediate arrangement of the friction surface arrangement ( 53 ) on the housing ( 12 ) or with it connected component is pressed. 2. Hydrodynamic coupling device according to claim 1, characterized in that in the first fluid space ( 56 ) a turbine wheel ( 26 ) is arranged rotatably about an axis of rotation (A) and that the first connection channel arrangement ( 60 , 62 , 64 ) and the third connection channel arrangement ( 78 , 80 , 82 ) are in communication with the first fluid space ( 56 ) on axial sides of the turbine wheel ( 26 ), in particular a turbine wheel shell ( 28 ), which are opposite to the axis of rotation (A), the third connection channel arrangement ( 78 , 80 , 82 ) in a region ( 66 ) between the turbine wheel ( 26 ), in particular a turbine wheel shell ( 28 ) of the same, and the coupling element ( 50 ) in connection with the first fluid space ( 56 ). 3. Hydrodynamic coupling device according to claim 2, characterized in that the third connecting channel arrangement (78, 80, 82) in a turbine wheel hub (30) at least one substantially radially extending first fluid passage opening (78). 4. Hydrodynamic coupling device according to one of claims 1 to 3, characterized by an output shaft ( 32 ), in which a substantially in the direction of an axis of rotation (A) extending second fluid passage opening ( 72 ) is formed, which at least part of the second connecting channel arrangement ( 72 , 74 , 76 ). 5. Hydrodynamic coupling device according to one of claims 1 to 4, characterized in that the second connecting channel arrangement ( 72 , 74 , 76 ) and the third connecting channel arrangement ( 78 , 80 , 82 ) are connected to one another in a radially inner region. 6. Hydrodynamic coupling device according to claim 4 and claim 5, characterized in that the third connecting channel arrangement ( 78 , 80 , 82 ) opens into the second fluid passage opening ( 72 ). 7. Hydrodynamic coupling device according to one of claims 1 to 6, characterized in that in the coupling element ( 50 ) at least one inlet opening ( 90 ) for guiding working fluid into the fluid channel arrangement ( 84 ) is provided. 8. Hydrodynamic coupling device according to one of claims 1 to 7, characterized in that in the coupling element ( 50 ) at least one outlet opening ( 94 ) for guiding working fluid from the fluid channel arrangement ( 84 ) into the first fluid space ( 56 ) is provided. 9. Hydrodynamic coupling device according to claim 8, characterized in that an inlet opening ( 90 ) and an outlet opening ( 94 ), which are assigned to the same fluid channel section ( 86 ) of the fluid channel arrangement ( 84 ), are offset from one another in the circumferential direction. 10. The hydrodynamic coupling device according to one of claims 1 to 9, characterized in that the friction surface arrangement ( 53 ) can be moved in the circumferential direction with respect to at least one assembly of the coupling element ( 50 ) and housing ( 12 ) or component connected thereto, and that the fluid channel arrangement ( 84 ) a groove-like channel assembly (86) which of the friction surface (53) is open on one cooperating with the at least one friction surface assembly (98). 11. Hydrodynamic coupling device according to one of claims 1 to 10, characterized in that the fluid channel arrangement ( 84 ) comprises at least a fluid channel region ( 86 ) which extends in the wesentli Chen only in the circumferential direction. 12. Friction surface arrangement, in particular for a hydrodynamic coupling device ( 10 ) according to one of the preceding claims, wherein in the friction surface arrangement ( 53 ) a fluid channel arrangement ( 84 ) is provided, into which working fluid can enter from a fluid space ( 56 ) and only to that same fluid space ( 56 ), characterized in that the fluid channel arrangement ( 84 ) extends at least in some areas essentially only in the circumferential direction, or / and that the fluid channel arrangement ( 84 ) has an outer peripheral surface area ( 106 ) and an inner peripheral surface area ( 96 ) of the friction surface arrangement ( 53 ) against fluid passage. 13. The friction surface arrangement according to claim 12, characterized in that the fluid channel arrangement ( 84 ) has at least one entry region ( 88 , 92 ), in which working fluid can enter through a coupling element ( 50 ) of a lock-up clutch ( 48 ) of the hydrodynamic coupling device ( 10 ) , and has at least one outlet region ( 92 , 88 ) from which working fluid can pass through the coupling element ( 50 ). 14. Friction surface arrangement, in particular for a hydrodynamic coupling device according to one of claims 1 to 11, wherein in the friction surface arrangement ( 53 ) a fluid channel arrangement ( 84 ) is provided, into which working fluid can enter from a fluid space ( 56 ) and only to the same fluid space ( 56 ), characterized in that the fluid channel arrangement ( 84 ) has at least one fluid channel ( 86 ) which is open to a radial end region of the friction surface arrangement ( 53 ) with a first end region ( 88 ) and with a second end region ( 92 ) is. 15. The friction surface arrangement according to claim 14, characterized in that the at least one fluid channel ( 86 ) is essentially symmetrical with respect to a radial line (R). 16. The friction surface arrangement according to claim 14 or 15, characterized in that the at least one fluid channel ( 86 ) extends essentially in a straight line. 17. The friction surface arrangement according to claim 14 or 15, characterized in that the at least one fluid channel ( 86 ) has a region of curvature ( 176 ) between its end regions ( 88 , 92 ). 18. The friction surface arrangement according to claim 17, characterized in that the at least one fluid channel ( 86 ) runs essentially rectilinearly in its end regions ( 88 , 92 ). 19. Friction surface arrangement according to one of claims 14 to 18, characterized in that the fluid channel arrangement ( 84 ) has at least two radially staggered fluid channels ( 86 , 86 '), the end regions ( 88 , 92 ) of one ( 86 ) of the at least two fluid channels ( 86 , 86 ') are open to the radial end region of the friction surface arrangement ( 53 ) in the circumferential direction between the end regions ( 88 , 92 ) of the other ( 86 ) of the at least two fluid channels. 20. The friction surface arrangement as claimed in claim 19, characterized in that the end regions ( 88 , 92 ) of one ( 86 ) of the at least two fluid channels ( 86 , 86 ') have an opening angle in the range from 60 ° -70 °, preferably approximately 65 °, lock in. 21. The friction surface arrangement according to claim 19 or 20, characterized in that the end regions ( 88 , 92 ) of the other ( 86 ') of the at least two fluid channels ( 86 , 86 ') have an opening angle in the range of 65 ° -75 °, preferably approx. 70 °, include. 22. Friction surface arrangement according to one of claims 17 to 21, characterized in that the one ( 86 ) of the at least two fluid channels ( 86 , 86 ') has a radius of curvature (R _K3 ) in the region of 6-8 cm in its region of curvature ( 176 ), preferably about 6.8 cm. 23. Friction surface arrangement according to one of claims 17 to 22, characterized in that the other ( 86 ') of the at least two fluid channels ( 86 , 86 ') has a radius of curvature (R _K2 ) in the range of 12-14 cm in its area of curvature ( 176 ) , preferably about 12.8 cm. 24. The friction surface arrangement as claimed in claim 14 or 15, characterized in that the at least one fluid channel ( 86 ) has a central region ( 200 ) which extends essentially in the circumferential direction and then respective regions of curvature ( 202 , 204 ) to the central region ( 200 ). 25. The friction surface arrangement according to claim 24, characterized in that at least one of the curvature areas ( 202 , 204 ) extends in a substantially straight line, the channel section forming an end area of the first and second end areas ( 88 , 92 ). 26. The friction surface arrangement according to claim 24 or 25, characterized in that at least one of the curvature regions ( 202 , 204 ) forms an end region of the first and second end regions. 27. Friction surface arrangement according to claim 25 or 26, characterized in that the first and / or the second end region of the at least one fluid channel ( 86 ) with respect to a tangential line (T) an angle (α) in the range of 40 ° -60 °, preferably approx 50 °, and / or has a radius of curvature (R _K1 ) in the range of 12-23 cm, preferably approximately 17.5 cm, in at least one region of curvature. 28. The friction surface arrangement according to claim 14, characterized in that the at least one fluid channel ( 86 ) is curved radially outwards near one of its end regions. 29. Friction surface arrangement according to one of claims 14 to 28, characterized in that at least two fluid channels ( 86 ) are connected to one another by a connecting channel arrangement ( 174 ). 30. Friction surface arrangement according to one of claims 12 to 29, characterized in that the fluid channel arrangement ( 84 ) has a plurality of fluid channels ( 86 ) which follow one another in the circumferential direction. 31. The friction surface arrangement according to claim 30, characterized in that the plurality of fluid channels ( 86 ) comprises a plurality of fluid channel groups (G), a distance (I) between the fluid channels ( 86 ) in a fluid channel group (G) being smaller than a distance (W3) between individual fluid channel groups (G). 32. Friction surface arrangement according to one of claims 14 to 31, characterized in that at least one fluid channel ( 86 ) in its first and second end regions ( 88 , 92 ) is open to a radially inner end region of the friction surface arrangement ( 53 ). 33. friction surface arrangement, in particular for a hydrodynamic coupling device according to one of claims 1 to 11, wherein in the friction surface arrangement ( 53 ) a fluid channel arrangement ( 84 , 84 ') is provided, into which working fluid can enter from a fluid space ( 56 ) and only to that same fluid space ( 56 ) can emerge, characterized in that the friction surface arrangement ( 84 , 84 ') has a friction surface carrier ( 180 ) and on both sides thereof a friction surface element ( 52 , 52 '), wherein in a first ( 52 ) of the friction surface elements ( 52 , 52 ') a first fluid channel arrangement area ( 84 ) is provided and in a second ( 52 ') of the friction surface elements ( 52 , 52 ') a second fluid channel arrangement area ( 84 ') is provided, in the friction surface carrier ( 180 ) a ver Connection opening arrangement ( 182 ) is provided, via which the first fluid channel arrangement area ( 84 ) and the second fluid channel arrangement area ( 84 ') with each other he is in fluid exchange connection. 34. Friction surface arrangement according to claim 33, characterized in that the first fluid duct arrangement region ( 84 ) and the second fluid duct arrangement region ( 84 ') form a radial end region, preferably a radially outer region, of the first friction surface element ( 52 ) and the second friction surface element ( 52 '), respectively. are open. 35. Friction surface arrangement according to claim 34, characterized in that the first fluid channel arrangement area ( 84 ) and the second fluid channel arrangement area ( 84 ') each have at least one fluid channel ( 86 , 86 ') which is in an end area ( 88 , 88 ') to the radial end area of the respective friction surface element ( 52 , 52 ') is open and is connected via another end region ( 92 , 92 ') to the respective other fluid channel arrangement region ( 84 ', 84 ). 36. Friction surface arrangement according to claim 35, characterized in that at least one of the fluid duct arrangement regions ( 84 , 84 ') has at least one ring-like connection duct arrangement ( 184 ') into which the connection opening arrangement ( 182 ) opens. 37. Friction surface arrangement according to claims 35 and 36, characterized in that the at least one fluid channel ( 86 ') opens with its other end region ( 92 ') into the connecting channel arrangement ( 184 '). 38. The friction surface arrangement according to claim 33, characterized in that one ( 84 ) of the fluid channel arrangement regions ( 84 , 84 ') is open at a radial end region, preferably radially outer region, of the associated friction surface element ( 52 ) and that the other fluid channel arrangement region ( 84 ') ) via a further connection opening arrangement ( 90 ) in a clutch element ( 50 ) which can be brought into frictional engagement thereof, a lock-up clutch arrangement ( 48 ) is or can be brought into fluid exchange connection with the fluid space ( 56 ). 39. Friction surface arrangement according to claim 38, characterized in that the one fluid channel arrangement region ( 84 ) has at least one fluid channel ( 86 ) which is open in one end region ( 88 ) to the radially outer end region of the associated friction surface element ( 52 ) and via its other end region rich ( 92 ) in connection with the other fluid channel arrangement area ( 84 '). 40. Friction surface arrangement according to claim 38 or 39, characterized in that the other fluid channel arrangement area ( 84 ') has an annular connection channel arrangement ( 184 ', 186 '), into which the connection opening arrangement ( 182 ) and / or the further connection opening arrangement ( 90 ) opens . 41. Friction surface arrangement according to one of claims 38 to 40, characterized in that the connection opening arrangement ( 182 ) and the further connection opening arrangement ( 90 ) each have at least one fluid passage connection opening ( 182 , 90 ) and in that the number of fluid passage connection openings ( 182 ) of the connection opening arrangement ( 182) to (90) of the further connecting port assembly (90) differs from the number of fluid passage connecting openings. 42. Friction surface arrangement according to one of claims 12 to 41, characterized in that the fluid channel arrangement ( 84 ) has in at least one longitudinal region thereof a cross-sectional profile which tapers in the direction of a channel base. 43. Friction surface arrangement according to claim 42, characterized in that the tapering cross-sectional profile is formed by channel walls ( 206 , 208 ) extending essentially in a straight line towards the channel base. 44. Friction surface arrangement according to claim 42 or 43, characterized in that at least one channel wall ( 206 , 208 ) delimiting the fluid duct transition merges into a friction surface region ( 212 ) of the friction surface arrangement ( 53 ) in a region of curvature ( 210 ). 45. Hydrodynamic coupling device, in particular hydrodynamic torque converter or fluid coupling, comprising a friction surface arrangement ( 53 ) according to one of claims 12 to 44. 46. friction element, in particular for a hydrodynamic coupling device, comprising a ring-like friction lining carrier ( 180 ) and on at least one side of the friction lining carrier ( 180 ) a friction surface arrangement ( 53 ) according to one of claims 12 to 44.