Dual clutch system

Abstract

Dual clutch assembly comprising a first clutch assembly (2) comprising a first outer plate carrier (3) with associated first outer plates (4) and a first inner plate carrier (5) with associated first inner plates (6), wherein the first outer plates (4) and the first inner plates (6) form a first plate pack (9), and a second clutch assembly (11) arranged radially within the first clutch assembly (2) comprising a second outer plate carrier (12) with associated second outer plates (13) and a second inner plate carrier (14) with associated second inner plates (15), wherein the second outer plates (13) and the second inner plates (15) form a second plate pack (18), and wherein the first inner plate carrier (5) is rotationally fixed to a first output hub (8) and the second inner plate carrier (14) is non-rotatably connected to a second output hub (17),wherein a first lubricant channel (20) leading to the first lamellar pack (9) and a second lubricant channel (21) leading to the second lamellar pack (18) are provided, wherein both lubricant channels (20, 21) are separate from each other and each lubricant channel (20, 21) can be supplied with lubricant separately via at least one lubricant supply bore (22, 23) provided in the first and second output hubs (8, 17), characterized in that at least one circumferential shielding plate (30) is arranged radially between the second outer lamellar carrier (12) and the first inner lamellar carrier (5), preventing the flow of lubricant from the second lamellar pack (18) and the second outer lamellar carrier (12) provided with openings (29) to the first lamellar pack (9).

Description

[0001] The invention relates to a double clutch device comprising a first clutch device comprising a first outer plate carrier with associated first outer plates and a first inner plate carrier with associated first inner plates, wherein the first outer plates and the first inner plates form a first plate pack, and a second clutch device arranged radially within the first clutch device comprising a second outer plate carrier with associated second outer plates and a second inner plate carrier with associated second inner plates, wherein the second outer plates and the second inner plates form a second plate pack, and wherein the first inner plate carrier is rotationally fixed to a first output hub and the second inner plate carrier is connected to a second output hub.

[0002] Such a dual-clutch transmission serves, in a known manner, to couple the output of a drive unit, such as an internal combustion engine, to a transmission. This is achieved via two separate clutch units, each comprising a multi-plate clutch pack. Each clutch pack typically includes axially movable outer plates on an outer plate carrier and axially movable inner plates on an inner plate carrier. The outer or inner plates usually have a friction surface, so that when the respective clutch pack is compressed by an annular actuating element, such as a pressure cup, a frictional connection is established. This allows torque transmitted via a drive shaft to the outer plate carriers to be transferred via the inner plate carriers to the respective output hub leading to the transmission.The two coupling devices can be operated separately, meaning that one coupling device can be closed while the other is open, and vice versa. In the embodiment of the double coupling device considered here, the two coupling devices are arranged radially; that is, the first coupling device is located radially further outwards than the second coupling device, which lies inside the first. The design and function of such a double coupling device are well known.

[0003] One embodiment of such a dual-clutch system is a wet dual-clutch system. In this wet dual-clutch system, an oil flow is directed through the clutch packs to dissipate heat, as the clutch plates naturally heat up due to friction during engagement. Since a radial clutch design is described here, the oil, which is usually supplied via one of the two output hubs, flows from the radial inner to the radial outer through the two clutch packs; that is, it first flows through the radially inner clutch pack and then on to the radially outer clutch pack. This cools the individual clutch packs and thus the clutch assembly. However, this also means that the disengaged clutch is constantly lubricated, and therefore oil flows through it.This leads to the generation of drag torques, since a certain coupling of the rotating outer plates to the inner plates, which do not actually rotate when the clutch device is open, is achieved via the oil.

[0004] For example, DE 10 2015 219 594 A1 is cited as the state of the art.

[0005] The invention is based on the problem of providing an improved dual-clutch device.

[0006] To solve this problem, in a dual-clutch device of the type mentioned at the outset, it is provided according to the invention that a first lubricant channel leading to the first lamellar pack and a second lubricant channel leading to the second lamellar pack are provided, wherein both lubricant channels are separate from each other and each lubricant channel can be supplied with lubricant separately via at least one lubricant supply bore provided in the first and the second output hub.

[0007] In the dual-clutch device according to the invention, lubricant is supplied separately to each clutch assembly, i.e., to each individual clutch unit. This is achieved via separate lubricant channels, which are separated from each other as far as possible, so that a defined lubricant flow to one clutch assembly and to the other clutch assembly is possible.

[0008] The respective lubrication channels, which here take the form of annular channels extending radially from the inside to the outside, are supplied via the respective output hub, to which the respective inner plate carrier of the first and second clutch assembly is connected. For this purpose, at least one lubricant supply bore is provided in both the first and second output hubs. The lubricant is thus guided via the respective output hub into the respective lubricant channel and from there reaches the respective plate pack.

[0009] The separate lubrication channels and their independent lubrication supplies make it possible to selectively supply only one or the other coupling unit with a constant flow of lubricant. This allows for appropriate temperature and lubrication management, ensuring that only the coupling unit requiring lubrication (oil) is supplied. This means that each coupling unit, or rather each clutch pack, can be optimally supplied with lubricant or oil according to its load. The lubricant supply to the respective lubrication channels can be controlled by selectively managing the lubricant supply to the output hub-side lubrication feed bores.

[0010] As described, the two lubrication channels are separated from each other. This does not imply a complete physical separation. Rather, the lubrication channels can communicate with each other to the extent that the two coupling devices are, of course, fluidically coupled to a certain degree. The lubrication channels are therefore not hermetically sealed. However, due to the operating principle of such a dual clutch and the fact that the lubricant primarily flows radially due to the rotation of the components, a significant separation of the lubrication channels can be achieved by assigning each channel a separate lubricant supply bore on its respective output hub, thus introducing the lubricant into each channel at a defined point.This runs in the respective channel with a radial preferred direction towards the respective lamellar package, so that only this is supplied with lubricant.

[0011] To separate the lubricant channels as much as possible, according to the invention, at least one circumferential shielding plate is arranged radially between the second outer plate carrier and the first inner plate carrier. This shielding plate prevents the flow of shear fluid through the second plate pack and the perforated second outer plate carrier to the first plate pack. According to this embodiment of the invention, a closed shielding plate is thus arranged between the two partial couplings, separating the two coupling devices or plate packs from each other in the radial direction. The lubricant flow through the second, radially inner plate pack typically exits through the second outer plate carrier, which is provided with corresponding perforations.The downstream shielding plate then deflects this lubricant flow and directs it laterally, preventing it from flowing further to the first lamellar pack.

[0012] The shielding plate is preferably drawn radially inwards with an edge region so that the edge is arranged directly adjacent to the second outer plate carrier. This prevents lubricant, i.e., oil, from flowing laterally between the second outer plate carrier and the shielding plate into the first lubricant channel leading to the first coupling device after passing through the first plate pack.

[0013] The shielding plate itself is preferably connected to the second outer lamella support or to a connecting component linking the first and second outer lamella supports. The shielding plate is therefore coupled to the outer lamella supports so that it rotates with them.

[0014] Alternatively or additionally to integrating the shielding plate, which prevents radial lubricant flow from the inner second clutch pack to the outer first clutch pack, it is conceivable that the second outer clutch pack carrier is provided with openings only in a carrier section that is axially offset from the first clutch pack. As described, the outer clutch pack carrier is usually provided with openings to allow the lubricant flowing through the clutch pack to escape. While in known dual clutches or coupling devices these openings are designed as longitudinal slots that extend almost over the entire length of the outer clutch pack carrier, in this embodiment according to the invention the openings are only relatively short and are located in a carrier section that is axially offset from the first clutch pack.The lubricant, which is discharged through these offset openings, is consequently discharged at a point where it can no longer flow to the radially outer first lamellar pack. According to this embodiment of the invention, the second outer lamellar carrier itself therefore has a shielding function, since it is closed in the area where it is radially adjacent to the radially outer first lamellar pack, i.e., it has no radial openings.

[0015] Of course, it is conceivable to provide both a shielding plate and the outer louver carrier with the staggered openings.

[0016] The axially offset openings on the second outer lamella carrier are preferably located in an area that, viewed axially, lies behind the connecting component linking the first and second outer lamella carriers. The lubricant is therefore discharged in an area where the first, radially outer lamella pack is axially shielded by the connecting component, which is typically ring- or disc-shaped. Thus, the first lamella pack lies axially in front of this connecting component, while the lubricant is discharged axially behind this component.

[0017] The invention is explained below with reference to exemplary embodiments and the drawings. The drawings are schematic representations and show: Fig. 1 a schematic representation of a dual clutch device of a first embodiment according to the invention, Fig. 2 a schematic representation of a second outer lamella carrier of the dual clutch assembly Fig. 1 in a side view, and Fig. 3 a schematic representation of a double clutch device of a second embodiment according to the invention.

[0018] Fig. Figure 1 shows a dual-clutch device 1 according to the invention, comprising a first clutch assembly 2 with a first outer plate carrier 3 with associated first outer plates 4 and a first inner plate carrier 5 with associated first inner plates 6. The outer plates 4 are, for example, steel plates, while the inner plates 6 are friction plates with a friction lining. The first outer plate carrier 3 is connected to a drive shaft 7 driven by an internal combustion engine or the like. The first inner plate carrier is connected to an output hub 8, which is coupled to an output shaft leading to a transmission (not shown in detail here).

[0019] The first outer and inner lamellae 4, 6 form a first lamella pack 9, wherein the respective lamellae are arranged axially movable on the outer and inner lamella carriers 3, 5. They can be axially pressed together by means of an actuating element 10, here for example a pressure pot, so that a frictional connection is created and the first coupling device 2 can be closed as required.

[0020] Furthermore, a second coupling device 11 is provided, comprising a second outer lamella carrier 12 with associated second outer lamellae 13, which are again steel lamellae. Also provided is a second inner lamella carrier 14 with inner lamellae 15 arranged thereon, which are likewise friction lamellae with a friction lining.

[0021] The second outer lamella carrier 12 is coupled to the first outer lamella carrier 3 via a connecting component 16, so that a rotation of the first outer lamella carrier 3 automatically leads to a rotation of the second outer lamella carrier 12 as well. The second inner lamella carrier 14 is coupled to a second output hub 17, which also leads to the gearbox (not shown in detail).

[0022] Here too, the second outer and inner lamellae 13, 15 form a second lamella pack 18, which, if required, can be axially pressed together via an actuating element 19, here again exemplarily a pressure pot, due to the axially movable bearing of the outer and inner lamellae 13, 15 on the outer and inner lamella carrier 12, 14, so that a frictional connection is established here too and the coupling device 11 is closed.

[0023] Depending on the opening and closing state, a torque introduced via the drive shaft 7 can be transmitted either via the first clutch assembly 2 to the first output hub 8 or via the second clutch assembly 11 to the second output hub 17. The basic design and function of such a dual-clutch assembly 1 are known.

[0024] For the individual supply of a lubricant either to the first clutch assembly 2 or to the second clutch assembly 11, respectively to the first lamellar pack 9 or the second lamellar pack 18, two separate, largely isolated lubricant channels 20, 21 are provided. A targeted lubricant supply, i.e., an oil supply to the first clutch assembly 2, can be made via the first lubricant channel 20, and a corresponding lubricant supply to the second clutch assembly 11 via the second lubricant channel 21.

[0025] To supply each of the channels separately with lubricant, the two output hubs 8, 17 each have separate lubricant supply bores 22, 23. Preferably, a plurality of such lubricant supply bores 22, 23 are arranged distributed around the circumference of the output hubs 8, 17, so that the lubricant can be guided as comprehensively as possible into the respective lubricant channel 20, 21, which are circumferential annular channels.

[0026] The lubricant supply is shown by the respective arrows A and B. It preferably occurs via the corresponding output shafts leading to the gearbox, which have corresponding supply bores.

[0027] The respective lubricant flow is shown by flow lines C in the region of the first lubricant channel 20 and flow lines D in the region of the second lubricant channel 21. The lubricant supplied via the lubricant supply bores 22 initially flows radially in the space between the first inner plate carrier 5 and a support plate 24, which is arranged on the second inner plate carrier 14. The lubricant then flows laterally past the radially more inwardly located second coupling assembly 11, i.e., past the second plate pack 18. Since rotating components are present within the coupling system, in particular the outer plate carriers 3, 12, which rotate continuously, as well as the respective inner plate carrier of the closed coupling assembly, a primarily radial flow direction inevitably results.This causes the lubricant to flow laterally along the second clutch assembly 11 to the first clutch assembly 2. The lubricant, flowing radially upwards from below towards the first inner plate carrier 5, passes through radial openings 25 in the first inner plate carrier 5 and reaches the first plate pack 9, where it flows between the plates 4 and 6 to cool them. The lubricant can then exit the first clutch assembly 2 again via corresponding radial, elongated openings 26 in the outer plate carrier 3.

[0028] Lubricant is supplied to this area only when the coupling device 2 is closed, so that it is actively cooled when friction occurs and heat is generated. However, if the coupling device 2 is open, no active lubricant supply takes place, so that the drag torque between the separated, vented inner and outer plates 4, 6 is reduced, since only a small amount of lubricant is present between the plates, which could lead to a coupling generating a drag torque.

[0029] The lubricant flow shown via the flow line D in the second lubricant channel 21 initially flows radially between the support plate 24 and the second inner lamellar carrier 14 to the second coupling device 11.

[0030] The lubricant then flows to the second inner lamella carrier 14 and through it via corresponding openings 27 to the second lamella pack 18. It then flows to the second outer lamella carrier 12. Unlike the first outer lamella carrier 3, which has a plurality of openings 26 arranged axially and circumferentially or of openings 26 in the form of elongated holes, the second outer lamella carrier 12 has corresponding openings 29 only on a carrier section 28 that is axially offset from the first lamella pack 9, as shown in Fig. Figure 2 is shown as an example. The remaining area of ​​the second lamellar carrier 12 is closed, specifically the area radially adjacent to the first coupling device 2 or the first lamellar pack 9. This causes the lubricant to flow axially sideways from the second lamellar pack 18 along the inside of the second outer lamellar carrier 12, after the outer lamellar carrier 12 is closed on the other side. The lubricant reaches the openings 29 and flows out of the lamellar pack area through them. Fig. However, as shown in Figure 1, these openings 29 are axially offset from the first lamellar pack 9. They are located in an area "behind" the ring- or disc-shaped connecting element 16, i.e., in an area that is separated from the actual lamellar pack area by the connecting element 16. This ensures that the lubricant flowing through the second lamellar pack 18 does not reach the first lamellar pack 9.

[0031] This design makes it possible to selectively supply the second lamellar pack 18 with lubricant only when necessary, i.e., when the second coupling device 11 and thus the second lamellar pack 18 is closed. When it is open, no active lubricant supply takes place. Any drag torque between the separated, airtight lamellars 13, 15 is significantly reduced, as only a small amount of lubricant is present in the lamellar area.

[0032] The supply of lubricant via the lubricant bores 22, 23 into the first or the second lubricant channel 20, 21 can be achieved via a corresponding upstream valve unit, which regulates the lubricant supply to the corresponding output hubs, depending on the desired or given closing state of the coupling devices 2, 11.

[0033] Fig. Figure 3 shows an alternative embodiment of a double clutch device according to the invention, wherein, where necessary, the same reference numerals are used for identical components. The construction is identical to that shown in Figure 3. Fig. 1. This means that the dual-clutch unit 1 from Fig. 3 also comprises a first coupling device 2 and a second coupling device 11. The first coupling device 2 has an outer plate carrier 3 with axially movable outer plates 4 and an inner plate carrier 5 with axially movable inner plates 6. The second coupling device also has an outer plate carrier 12 with axially movable outer plates 13 and an inner plate carrier 14 with axially movable inner plates 15. Two separate lubricant supply channels 20, 21 are provided, which are supplied with lubricant via separate lubricant supply bores 22, 23 formed on the output hubs 8, 17.

[0034] The basic structure corresponds to the exemplary embodiment as described. Fig. 1, as well as the function. For here too, the two lamellar packages 9, 18 can be actively supplied with lubricant separately via the respective lubricant channel 20, 21 as required.

[0035] Unlike the design according to Fig. 1. For radial separation or shielding of the first coupling device 2 from the second coupling device 11, an axially extending, circumferential shielding plate 30 is provided, which, viewed radially, is arranged between the second outer lamella carrier 12 and the first inner lamella carrier 5. The shielding plate 30, whose free edge 31 is radially angled or bent inwards so that it runs as close as possible to the second outer lamella carrier 12, is attached at its other end in the example shown to the connecting component 16, meaning that the shielding plate 30 rotates with the outer lamella carriers 3, 12.

[0036] The outer lamella carrier 2 has the usual radial openings 29, here in the form of circumferentially distributed elongated holes, which are also present in an area where the outer lamella carrier 12 is radially adjacent to the first coupling device 2. This is because the closed, non-perforated shielding plate 30 prevents the lubricant from flowing further to the first coupling device 2. Instead, the lubricant flows, as in Fig. 3 shown, axially to the side and emerges virtually “behind” the disc- or ring-shaped connecting component 16.

[0037] Here, a separate shielding plate 30 is provided for radial shielding, whereas in the design according to Fig. 1 for radial shielding the second outer lamella carrier 12 is perforated with the openings 29 only in a certain area which, viewed radially, is not adjacent to the first coupling device 2.

[0038] Of course, it is conceivable to also use the dual-clutch transmission 1 out of 1. Fig. 1 a shielding plate 30, as in Fig. 3 shown, to integrate. Reference symbol list 1 dual clutch system 2 Coupling device 3 outer slat carriers 4 Outer slat 5 internal slat carriers 6 inner slat 7 Drive shaft 8 Output hub 9 slat package 10 Actuating elements 11 Coupling device 12 outer slat carriers 13 Outer slat 14 internal slat carriers 15 inner slat 16 Connecting component 17 Output hub 18 slat package 19 Actuating element 20 Lubricant channel 21 Lubricant channel 22 Lubricant supply bore 23 Lubricant supply bore 24 support plate 25 Breakthrough 26 Breakthrough 27 Breakthrough 28 Carrier section 29 Breakthrough 30 Shielding plate 31 edge

Claims

[1] Dual clutch assembly comprising a first clutch assembly (2) comprising a first outer plate carrier (3) with associated first outer plates (4) and a first inner plate carrier (5) with associated first inner plates (6), wherein the first outer plates (4) and the first inner plates (6) form a first plate pack (9), and a second clutch assembly (11) arranged radially within the first clutch assembly (2) comprising a second outer plate carrier (12) with associated second outer plates (13) and a second inner plate carrier (14) with associated second inner plates (15), wherein the second outer plates (13) and the second inner plates (15) form a second plate pack (18), and wherein the first inner plate carrier (5) is rotationally fixed to a first output hub (8) and the second inner plate carrier (14) is fixed to a second output hub (17),wherein a first lubricant channel (20) leading to the first lamellar pack (9) and a second lubricant channel (21) leading to the second lamellar pack (18) are provided, wherein both lubricant channels (20, 21) are separate from each other and each lubricant channel (20, 21) can be supplied with lubricant separately via at least one lubricant supply bore (22, 23) provided in the first and second output hubs (8, 17), characterized by , that at least one circumferential shielding plate (30) is arranged radially between the second outer lamella carrier (12) and the first inner lamella carrier (5), preventing the flow of lubricant through the second lamella pack (18) and the second outer lamella carrier (12) which has openings (29) to the first lamella pack (9). [2] Dual clutch device according to claim 1, characterized by, that the shielding plate (30) is connected to the second outer lamella carrier (12) or to a connecting component (16) connecting the first and the second outer lamella carrier (3, 12). [3] Dual clutch device according to one of the preceding claims, characterized by , that the second outer lamella carrier (12) is provided with openings (29) only in a carrier section (28) that is axially offset to the first lamella package (9). [4] Dual clutch device according to claim 3, characterized by , that the openings (29) are provided in an area which, viewed axially, lies behind the connecting component (16) connecting the first and the second outer lamella carrier (3, 12).

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