COOLING OIL CONNECTION AND DRIVETRAIN WITH THIS

Description

[0001] The present invention relates to a guide element for cooling oil on a rotating component.

[0002] Various methods for distributing cooling oil are known in the prior art. For example, through targeted routing via closed channels arranged in the housing or components, or distribution via rotating components, where the components run through a designated oil sump and / or distribute centrally supplied cooling oil through centrifugal force.

[0003] Problems with the state of the art lie in the uncontrolled turbulence and uncontrolled distribution of the cooling oil.

[0004] DE 10 2011 005 504 A1 discloses a multi-disk switching element in which an oil guide plate is arranged on the side of the piston facing away from the pressure chamber, viewed axially, for actuating the multi-disk switching element.

[0005] The object of the present invention is to provide a cooling oil guide element which can distribute the cooling oil in a targeted manner.

[0006] The problem is solved by a cooling oil guide device and a drive train according to the independent claims.

[0007] According to the invention, a cooling oil guide device for rotating components, wherein an annular oil channel runs in the radial direction, and wherein cooling oil can be supplied from the radial inside and the oil channel is partially open radially outside, characterized in that a sealing region is provided in a radially outer region of the oil channel, that the sealing region has blocking elements and outlet elements, that the blocking elements are arranged radially inside the outlet elements and have at least two passages distributed over the circumference in the radial direction, that outlet channels aligned with the passages and inlets located in the circumferential direction between the outlet channels are formed, and that an annular channel is provided between the blocking elements and the outlet elements in order to connect the inlets to the outlet channels or passages.

[0008] Rotating components, particularly in the area of ​​a vehicle's drivetrain, often require oil to be guided through a shaft or hub. An oil channel is required to carry oil to surrounding components, for example, for cooling purposes. In many cases, however, a targeted distribution of the cooling oil is advantageous, as otherwise oil might reach components that should not be supplied with oil, or only receive small amounts of it. By arranging an oil channel in a ring around the rotating component, the outlet of the cooling oil can be shifted further radially outward.

[0009] To ensure a defined discharge of the cooling oil, a sealing area is provided in the radially outer region of the oil channel. The sealing area comprises several blocking elements arranged circumferentially, preferably on one diameter, and passages with a defined cross-section are formed between the blocking elements. The amount of cooling oil can be defined by the passages, in particular their number and cross-section.

[0010] The blocking elements are surrounded radially on the outside by outlet elements. The outlet elements define outlet channels that are aligned radially with the passages. The cooling oil can be discharged radially outward to surrounding components via the outlet channels. In addition, the outlet elements define inlets that are arranged circumferentially between the outlet channels. At least half as many inlets as outlet channels are provided, although up to a multiple, in particular double, number of inlets can be provided. Preferably, the same number of outlet channels and inlets are provided.

[0011] An annular channel is provided between the blocking elements and the outlet elements, connecting the inlets to the outlet channels, and thus also to the passages. At least one inlet is connected to at least one outlet channel through the annular channel. This also includes connecting one inlet to multiple outlet channels and / or connecting one outlet channel to multiple inlets. An advantageous embodiment provides an annular channel extending around the entire circumference.

[0012] The cooling oil escaping from the outlet channels creates a radially inward vacuum. To prevent the cooling oil from swirling due to the vacuum, inlets are provided through which the atmosphere surrounding the rotating component, such as air, can flow in to compensate for the vacuum. The incoming air exits the outlet channel along with the cooling oil. This creates a kind of centrifugal pump effect.

[0013] Embodiments of a cooling oil guide device are characterized by the fact that the cross-section of the passages decreases radially outward. Due to the physical forces acting on the oil flow, the oil flow would be atomized or swirled after the passages (expansion due to higher, diameter-dependent velocity). To prevent this, the passages are tapered in the radial direction. This prevents expansion of the oil flow. Thus, the oil flow enters the outlet channel with a largely laminar flow.

[0014] Cooling oil guide devices according to embodiments are characterized in that the cross-section of the outlet channels decreases radially outward. In addition to the air flowing in via the inlets to compensate for the resulting negative pressure, the outlet channels can also be provided with an outwardly tapered cross-section. As with the previously described passages, the preferably continuously reduced cross-section can counteract an expansion of the oil flow. This leads to an oil flow exiting the outlet channel that is as laminar as possible. Thus, turbulence or atomization of the oil flow is reduced or avoided, thereby facilitating or enabling a defined supply.Embodiments of a cooling oil guide device are characterized in that the outlet channels have a separation edge on at least one side of their radially outer edge, which has an angle of less than or equal to 90°. In order to keep the widening of the oil flow as small as possible when exiting the outlet channel, a separation edge is provided on at least one side of the outer edge of the outlet channel. Preferably, the separation edge is provided on several, in particular all, sides of the radially outer edge of the outlet channel. Due to the separation edge, the oil flow detaches directly from the wall of the outlet channel, and an oil flow that is as laminar as possible is maintained with little or no widening. In order for the flow to separate, the separation edge has an acute angle of less than or equal to 90°.

[0015] Cooling oil guide devices are characterized in embodiments by the inlets having a radius on at least one side of their radially outer edge. For the incoming air, however, it is advantageous for the edges of the radially outer edge of the inlets to be rounded. The rounded inlets achieve a more uniform air flow and reduce turbulence in the air stream.

[0016] Embodiments of a cooling oil guide device are characterized in that the outlet elements are rounded on their side facing the annular channel in order to keep the air flow from the inlets via the annular channel to the outlet channels as laminar as possible. By keeping the air flow as laminar as possible and avoiding turbulence, additional turbulence in the oil flow due to turbulent air flow can be avoided or reduced.

[0017] Embodiments of a cooling oil guide device are characterized in that the blocking elements at the passages have guide elements that protrude radially into the annular channel to direct an air flow in the annular channel toward the outlet channels. The air flowing in through the inlets is intended to exit again via the outlet channels together with the oil flow. To guide the air flow accordingly and minimize turbulence, guide elements projecting into the annular channel are provided. The guide elements change, preferably continuously, the direction of the open cross-section of the annular channel toward the outlet channel.

[0018] A further aspect of the application is a drive train of a vehicle, which is characterized by the provision of a cooling oil guide device according to the description. Such a cooling oil guide device allows for the targeted distribution of cooling oil.

[0019] Embodiments of a drive train are characterized in that the cooling oil guide device is provided in a hybrid module. Particularly in a hybrid module, where, for example, an electric machine enclosing rotating components must be cooled, a reliable supply of cooling oil is important. This can be ensured by a cooling oil guide device according to the invention.

[0020] Drivetrains according to embodiments are characterized in that the cooling oil guide device is provided in a clutch arrangement. Wet clutches, in particular, require a reliable supply of cooling oil, especially when actuated, which can be ensured by a cooling oil guide device according to the invention.

[0021] Embodiments of a cooling oil guide device for a clutch arrangement, wherein a clutch is provided which can be actuated via a piston movable in the axial direction in order to change between an actuated and an open position, wherein the piston is arranged radially inside the clutch, wherein the piston separates a pressure chamber and a compensation chamber from one another, wherein the compensation chamber is delimited by a compensation chamber cover which is fixed in the axial direction and a sealing cover coupled to the piston, and wherein the compensation chamber cover and the sealing cover overlap radially outward in the axial direction and are connected via a sealing element so as to be movable relative to one another in the axial direction, are characterized in that an overflow opening is provided in the sealing cover, which connects the compensation chamber to an oil channel provided between the sealing cover and the piston,that the oil channel is open on the outside in the radial direction, and that a control edge is provided on a component which is not axially movable relative to the piston, through which an oil flow emerging from the oil channel is guided at least largely through the clutch when the clutch is closed and past the clutch when the clutch is open.

[0022] A clutch within the meaning of the application is a device for mechanically transmitting or separating a torque from an input side to an output side. In particular, a clutch has one or more friction components that are brought into contact or separated with one another or with a pressure plate. A clutch can be designed, for example, as a single-disk clutch, multi-plate clutch, or cone clutch. The clutch is actuated by an axially movable piston. In order to move the piston, it has a pressure chamber on one side which can be pressurized with a fluid, preferably oil. A compensation chamber is provided on the other side of the piston. To ensure proper function, the compensation chamber is filled with oil, preferably without being pressurized.

[0023] The expansion chamber is partially defined by an expansion chamber cover, which is fixed axially relative to the clutch. The expansion chamber is further defined by a sealing cover, which is connected to the piston and can move with it. To ensure that the expansion chamber remains closed even during relative movement between the expansion chamber cover and the sealing cover, the expansion chamber cover and the sealing cover overlap axially. A sealing element is provided between the expansion chamber cover and the sealing cover to prevent or minimize oil leakage from the expansion chamber.

[0024] The seal cover and the piston are connected to one another in such a way that an oil channel is formed between the seal cover and the piston, which is open radially outwards. At least one overflow opening is provided on the seal cover, which connects the compensation chamber with the oil channel. The overflow opening ensures that no or excessive oil pressure builds up in the compensation chamber, particularly compared to the pressure chamber, and at the same time the oil flowing out through the overflow opening can be used as cooling oil for other components, such as the clutch. The overflow opening can, for example, be designed as an annular gap extending over the entire circumference, or as several openings distributed over the circumference.

[0025] When the clutch is engaged, it is preferably supplied with cooling oil to ensure sufficient heat dissipation and thus avoid overheating and increased wear. When the clutch is disengaged, however, it is advantageous if no or only small quantities of cooling oil are supplied to the clutch in order to reduce the drag torque caused by the cooling oil present between the friction elements of the clutch. For this purpose, a control edge is provided on an axially non-movable part, which is arranged in the axial direction between the axial end positions of the radially outer opening of the oil channel when the clutch is disengaged or closed. The oil flow escaping from the oil channel due to centrifugal force can thus be fed to the clutch in a targeted manner through the control edge or can be guided past the clutch to supply other components, such as an electrical machine or the like.Depending on the design, the control edge can also divide the oil flow so that the oil flow is only partially directed past the clutch, rather than completely. The control edge is preferably designed as a circumferential, inwardly projecting protrusion.

[0026] Embodiments of a cooling oil guide device are characterized by the fact that the control edge is provided on the expansion chamber cover. Due to the axially fixed arrangement with respect to the clutch and the spatial proximity of the expansion chamber cover to the seal cover and thus to the oil channel, the control edge is advantageously provided on the expansion chamber cover. This spatial proximity ensures that the oil flow can be controlled almost entirely by the control edge, since there is little or no expansion or atomization of the oil flow.

[0027] Other embodiments of a cooling oil guide device are characterized by the fact that the control edge is provided on an inner support of the clutch. This advantageously simplifies the production of the expansion chamber cover and, if necessary, saves weight.

[0028] Cooling oil guide devices according to embodiments are characterized in that the overflow opening is provided in the radially inner region of the sealing cover. By providing the overflow opening in the radially inner region, it is ensured that the compensation chamber is sufficiently filled with oil, since it fills from the radial outside with centrally supplied oil due to centrifugal force.

[0029] Embodiments of a cooling oil guide device are characterized in that the control edge is designed as a radially inwardly projecting projection, which, at least on one side, axially delimits an annular space with radial passages distributed over the circumference. The radially inwardly projecting projection allows the oil flow coming from the radial inside to be reliably supplied to different areas according to the switching position of the piston. Advantageously, an annular space is provided adjacent to the projection. The supplied cooling oil can be directed to the clutch or other components in a targeted manner via the passages in the annular space.

[0030] Cooling oil guide devices according to embodiments are characterized in that the control edge is provided in an axial end region or two annular spaces adjacent in the axial direction are separated from one another by the control edge.

[0031] For a simpler component geometry, it is advantageous if the projection is located in an axial end area. This allows the oil flow to be guided radially past the component in one of the piston's switching positions.

[0032] In particular, if the axial distance between the different positions for supplying the cooling oil, which depend on the switching position of the piston, is greater than the axial stroke of the piston, the cooling oil can also be distributed over a larger axial area by means of an annular space or annular spaces provided on both sides of the projection or their passage openings.

[0033] Embodiments of a cooling oil guide device are characterized in that at least one spacer is provided between the sealing cover and the piston, and in that the spacer has at least one continuous recess running in the radial direction to form the oil channel. In order to simplify the positioning of the piston and the sealing cover relative to one another and to keep the oil channel reliably open even in the event of any deformation of the components, for example due to pressure, at least one spacer is preferably provided. The spacer determines the extent of the oil channel in the axial direction. Furthermore, the connection between the piston and the sealing cover can be made via the spacer(s). In order to form the oil channel, the spacer and / or the spacers have recesses between one another which are radially continuous.

[0034] Cooling oil guide devices are characterized, according to embodiments, by the spacer being provided in the radially outer region. By providing a spacer in the radially outer region, the geometry of the oil channel outlet can be adjusted, for example, to minimize the widening of the escaping oil flow, thereby simplifying separation by the control edge.

[0035] A further aspect of the application is a drive train which is characterized in that a clutch arrangement with a cooling oil guide device according to one of the described embodiments is provided.

[0036] Another aspect of the application is a hybrid module for a drive train, which is characterized in that a clutch arrangement with a cooling oil guide device according to the description is provided, and in that a control edge is provided on a component that is not axially movable relative to the piston, through which an oil flow emerging from the oil channel is guided at least largely through the clutch when the clutch is closed and past the clutch when the clutch is open to a rotor of an electric machine of the hybrid module.

[0037] The invention is explained in more detail below with reference to the figures. Identical or similar components are designated by identical reference numerals. The figures show in detail: Fig. 1a shows an embodiment of a cooling oil guide device with an open clutch. Fig. 1b shows an embodiment of a cooling oil guide device according to Fig. 1a with the clutch closed. Fig. 2a shows an embodiment of a cooling oil guide device with the clutch open. Fig. 2b shows an embodiment of a cooling oil guide device according to Fig. 2a with the clutch closed. Fig. 3 shows a piston with a sealing cover according to an embodiment. Fig. 4 shows a section along the line AA of an embodiment according to Fig. 3 represents.

[0038] Fig. 1a, 1b , 2a und 2b Each shows a section of a hybrid module for a drive train with exemplary embodiments of a cooling oil guide device, primarily showing the components of a clutch assembly. Due to the largely rotationally symmetrical design, only one half is shown.

[0039] The clutch arrangement comprises a clutch 1, which can be designed in particular as a friction clutch. In the example shown, the input side of the clutch 1 is connected to an inner carrier 8. The inner carrier 8 is connected to an input shaft. In the illustrated embodiment, the output side of the clutch 1 is connected to a rotor carrier 17. A rotor 11 of an electric machine is provided on the rotor carrier 17, and the rotor carrier 17 is connected to a housing of a torque converter in the illustrated embodiment. Other designs are also possible, for example, in which the rotor carrier is connected directly to an output or intermediate shaft.

[0040] An axially movable piston 2 is provided to actuate the clutch 1. In order to pressurize the piston 2, a pressure chamber D is provided which, in the exemplary embodiment shown, is delimited by the piston 2, the housing of the torque converter, a seal arranged therebetween, and an intermediate shaft connected to the housing. The pressure chamber D can be pressurized by the intermediate shaft. A compensation chamber G is located axially opposite the piston 2, which compensation chamber is also supplied with oil to lubricate the components and to compensate for the oil pressure in the pressure chamber D when the clutch is not actuated. In the exemplary embodiment shown, the compensation chamber G also contains an elastic return element, such as one or more springs, for the piston 2, by means of which the piston 2 is returned to its initial position, in this case an open position, when the clutch is not actuated.

[0041] In the illustrated embodiment, the expansion chamber G is defined by the intermediate shaft, via which the oil supply is also provided, a compensation chamber cover 3 connected to the intermediate shaft, and the piston 2 or a sealing cover 4 connected to the piston 2. A sealing element 5 is provided on the sealing cover 4 and rests against the expansion chamber cover 3.

[0042] The sealing cover 4, together with the piston 2, encloses an oil channel K extending essentially in a radial direction. An overflow opening 6 is provided at the radially inner end of the sealing cover 4, which connects the compensation chamber G with the oil channel K. The overflow opening 6 can be designed as a circumferential annular gap or formed by one or more recesses distributed over the circumference. The oil channel K is open at its radially outer end to discharge escaping oil as cooling oil to radially surrounding components.

[0043] In the figures, an oil flow caused by the cooling oil guide device is shown by arrows.

[0044] The described basic structure is the same for all shown embodiments, especially the Fig. 1a, 1b , 2a und 2b , the same, although other embodiments are also possible.

[0045] Fig. 1a shows the embodiment in a non-actuated state of the clutch 1, in which the piston 2 is not subjected to pressure.

[0046] In the example shown, the expansion chamber cover 3 has a section at its radially outer end that extends axially toward the piston 2. In the axial end region of the expansion chamber cover 3, a radially inwardly projecting control edge 7 is provided, which is arranged in the region of the oil channel K, preferably in the axially adjacent region around the sealing cover 4. As a result, at least the majority of the oil flow is guided past the expansion chamber cover 3 and thus past the clutch 1 radially surrounding the expansion chamber cover 3. When not actuated, the clutch 1 does not require any supply of cooling oil. By supplying no cooling oil, or only small amounts, any drag torque occurring between the input and output sides of the clutch 1 is avoided or at least reduced, thereby reducing losses.

[0047] In the illustrated embodiment of a hybrid module, the oil flow is guided past the clutch 1 to the rotor 11 of an electric machine, which surrounds the clutch assembly, to ensure its cooling. Cooling of the electric machine is necessary regardless of whether a drive connected to the input side of the clutch 1, such as an internal combustion engine, is connected to the rest of the drive train via the clutch 1 or not. In the illustrated embodiment, the cooling oil strikes a rotor carrier 17 for the rotor 11 of the electric machine and is distributed by the rotor carrier 17 over the axial extent of the rotor 11.

[0048] Fig. 1b corresponds to the embodiment according to Fig. 1a , with clutch 1 shown in an actuated state. Due to the pressurized pressure chamber D, piston 2 is displaced into its actuated position. Thus, oil channel K is also displaced axially relative to compensating cover 3 and the control edge 7 provided thereon.

[0049] The oil flow therefore strikes the expansion chamber cover 3 and is guided by the control edge 7 toward an annular space provided on the expansion chamber cover 3, adjacent to the control edge 7. In the area of ​​the annular space, passage openings 9 are provided on the expansion chamber cover 3, through which the cooling oil can be guided to radially surrounding components. In the illustrated embodiment, the cooling oil is guided through the passage openings 9 to the inner carrier 8 of the clutch 1 and from the inner carrier 8 through the clutch 1. Downstream of the clutch 1, the cooling oil is passed on from the rotor carrier 17 to the electric machine, in particular the rotor 11.

[0050] The control edge 7 thus directs the oil flow in the desired axial direction or prevents it from flowing into other areas. Depending on the positioning of the control edge 7, embodiments are also possible in which the oil flow, particularly in the case of a strongly expanding oil jet, is divided by the control edge 7 in order to constantly supply all components with cooling oil, but to change the flow distribution depending on the switching position of the piston 2.

[0051] In the Fig. 2a und 2b Another embodiment of the cooling oil guide device is shown. The basic structure is the same as the embodiment in Fig. 1a und 1b equal. Also Fig. 2a a non-actuated state and Fig. 2b an actuated state of the piston 2 or the clutch 1. The difference is that the compensation chamber cover 3 does not have an area extended axially in the direction of the piston 2, but the control edge 7 is provided on the inner carrier 8 of the clutch 1.

[0052] The control edge 7 in Fig. 2a und 2b is also arranged in an axial area adjacent to the outlet of the oil channel K in the direction of movement of the piston 2. This allows, analogously to the above description, Fig. 1a und 1b the oil flow is directed past clutch 1 or through clutch 1.

[0053] Fig. 3 shows a piston 2 with sealing cover 4 according to an embodiment. Analogous to the Fig. 1a, 1b , 2a und 2b A sealing element 5 is provided on the sealing cover 4 in order to seal a compensation chamber G. An overflow opening 6 is provided radially inward, through which cooling oil can flow into the oil channel K formed between the sealing cover 4 and the piston 2. In order to keep the oil channel K safely open during operation, spacers 10 are provided in the example shown, since deformations can occur due to forces occurring during operation.

[0054] The spacers 10 can be arranged in the radially outer region, as shown. However, embodiments are also possible in which the spacers 10 are provided at other positions. Embodiments are also possible in which the spacers 10 extend largely over the radial extent of the sealing cover 4, or in which several spacers 10 are provided with different diameters.

[0055] The spacers 10 can, as in Fig. 3 shown, in one piece or together with the sealing element 5. Alternatively or additionally, the spacers 10 can also be formed by separate components or formations on the sealing cover 4 and / or piston 2, as well as combinations thereof. The spacers 10 must enable the oil channel K, which is why the spacers 10 cannot be designed in the circumferential direction as a closed ring over the thickness of the oil channel K in order to provide a radially continuous oil channel K.

[0056] In the illustrated embodiment, a separation edge 15 is provided at the outer end of the oil channel K. The separation edge 15 is provided to ensure that the oil flow exiting the oil channel K is as laminar as possible and to prevent or at least reduce widening, turbulence, and atomization of the cooling oil. The separation edge 15 can also be used to slightly offset or direct the oil flow in the axial direction if necessary.

[0057] The axial clearance of the oil channel K depends, among other things, on the amount of cooling oil to be delivered. The clearance is preferably in the range of 0.5 mm to 2 mm, although designs with a larger clearance, such as 3 mm or 4 mm, are also possible.

[0058] Fig. 4 shows a section along line AA in Fig. 3 , which represents the spacers 10 and the outer area of ​​the oil channel K.

[0059] Viewed from the radial inside, the spacers 10 have blocking elements 12 and outlet elements 13. The blocking elements 12 are provided circumferentially and block an inner region of the oil channel K from the outside, with at least one, in the example shown, several, preferably evenly distributed passages 14 being provided between the blocking elements 12. The passages 14 can limit the amount of cooling oil escaping.

[0060] In the exemplary embodiment, a plurality of outlet elements 13 are provided in the radially outer edge of the oil channel K, distributed over the circumference. The outlet elements 13 are spaced apart from one another in order to form outlet channels A and inlets E. The outlet channels A are preferably arranged in alignment with the passages 14. The inlets E are arranged in the circumferential direction between the outlet channels A. The number of inlets E is at least half as large as the number of outlet channels A or a multiple thereof; preferably, the number is the same, as in the example shown. A blocking element 12 is located radially inwardly opposite the inlets E. Between the blocking elements 12 and the outlet elements 13, an annular channel R is provided, which connects at least one inlet E with an outlet channel A. In the example shown, the annular channel R runs circumferentially.

[0061] In the illustrated embodiment, guide elements 16 are provided on the blocking elements 12, which reduce the cross-section of the passages 14 in the radial outward direction to prevent expansion of the cooling oil. The guide elements 16 prevent atomization of the cooling oil during its transition from the passage 14 into the outlet channel A and maintain a largely laminar flow of the oil stream.

[0062] The oil flow is conveyed radially outwards by the rotation of the components. Due to the increasing diameter, the conveyed volume of the oil flow creates a negative pressure, which leads to undefined suction of ambient atmosphere, such as air, in a free annular gap and mixing of this air with the oil, thereby increasing turbulence and atomization of the escaping oil. To prevent this, inlets E are provided through which air can flow inwards. The air is specifically fed to the outlet channel A via the annular channel R connected to the inlet E. This results in mixing of the cooling oil flowing in through the passage 14 with the sucked-in air without significant turbulence occurring.

[0063] The oil flow is shown in Fig. Analogous to the Fig. 1a, 1b , 2a und 2b outlined with arrows. In addition, Fig. 4 The flow of the sucked-in air is shown by dashed arrows.

[0064] As it continues radially outward, the cross-section of the outlet channel A changes in such a way that compression of the escaping oil flow is largely avoided, since this would otherwise lead to expansion and thus strong turbulence or atomization of the oil flow after exiting the oil channel K. The cross-sectional shape preferably changes continuously in order to maintain a largely laminar oil flow.

[0065] In addition, in the illustrated embodiment, additional separation edges 15 are provided at the end of the outlet channel A to reduce or prevent turbulence and maintain a laminar oil flow. Turbulence of the oil flow should be avoided as much as possible, especially in the direction of the clutch 1, since this would supply an uncontrolled amount of cooling oil, which could potentially lead to increased drag torque.

[0066] The tear-off edge 15 can be as in Fig. 3 run in the circumferential direction and / or as in Fig. 4 in the axial direction. The separation edge 15 can preferably be manufactured in one piece, as shown, although other variants are also possible. The edges at the inlets E are preferably rounded to enable the most even air flow possible.

[0067] The invention is not limited to the described embodiments. As explained above, only individual advantageous features may be provided, or various features from different examples may be combined. Bezugszeichen

[0068] 1 Clutch 2 Piston 3 Expansion chamber cover 4 Sealing cover 5 Sealing element 6 Overflow opening 7 Control edge 8 Inner support 9 Passage opening 10 Spacer 11 Rotor 12 Locking element 13 Outlet element 14 Passage 15 Breakaway edge 16 Guide element 17 Rotor support AOutlet channel DPressure chamber EInlet GCompensation chamber KOil channel RRring channel

Claims

1. Cooling oil conducting device for rotating components, wherein an annular oil duct (K) extends in the radial direction, and wherein cooling oil is able to be fed from radially inside and the oil duct (K) is partially open radially on the outside, characterized in that a sealing region is provided in a radially outer region of the oil duct (K), that the sealing region has blocking elements (12) and exit elements (13), that the blocking elements (12) are disposed radially within the exit elements (13) and in the radial direction have at least two passages (14) distributed over the circumference, that exit ducts (A) which are co-aligned with the passages (14), and inlets (E) which lie in the circumferential direction between the exit ducts (A), are formed by the exit elements (13), and that an annular duct (R) for connecting the inlets (E) to the exit ducts (A), or the passages (14), respectively, is provided between the blocking elements (12) and the exit elements (13).

2. Cooling oil conducting device according to Claim 1, characterized in that the cross section of the passages (14) decreases in the radial direction towards the outside.

3. Cooling oil conducting device according to one of the preceding claims, characterized in that the cross section of exit ducts (A) decreases in the radial direction towards the outside.

4. Cooling oil conducting device according to one of the preceding claims, characterized in that the exit ducts (A) on their radially outer periphery on at least one side have a breakaway edge (15) which has an angle of less than or equal to 90°.

5. Cooling oil conducting device according to one of the preceding claims, characterized in that the inlets (E) on their radially outer periphery on at least one side have a radius.

6. Cooling oil conducting device according to one of the preceding claims, characterized in that the exit elements (13) are radiussed on their side facing the annular duct (R) in order to keep an air flow from the inlets (E) via the annular duct (R) to the exit ducts (A) as laminar as possible.

7. Cooling oil conducting device according to one of the preceding claims, characterized in that the blocking elements (12) at the passages (14) have directing elements (16) which protrude radially into the annular duct (R) in order to direct an air flow in the annular duct (R) in the direction of the exit ducts (A).

8. Drivetrain of a vehicle, characterized in that a cooling oil conducting device according to one of the preceding claims is provided.

9. Drivetrain according to Claim 8, characterized in that the cooling oil conducting device is provided in a hybrid module.

10. Drivetrain according to one of Claims 8 and 9, characterized in that the cooling oil conducting device is provided in a clutch assembly.