Fluid guiding device for a friction plate clutch and clutch unit having a fluid guiding device

Abstract

The invention relates to a fluid guiding device for a friction plate clutch, comprising an inner plate carrier (3) having a carrier section (5), a shoulder section (7) and a shaft section (6), wherein the carrier section (5) has a connection structure (8) for receiving an inner plate (29) in a rotationally fixed and axially displaceable manner, a fluid guiding element (4) which is firmly connected to the inner plate carrier (3) and has an annular collecting section (12) in which fluid which flows in can be collected and a plurality of connection tab sections (13) which are distributed over the circumference, extend in axial direction and each have a radial through-opening (14), wherein the inner plate carrier (3) has a plurality of longitudinal grooves (11) radially on the outside, which extend axially from the shoulder section (7) into the carrier section (5) and are covered by the connection tab sections (13) of the fluid guiding element (4). Furthermore, the invention relates to a clutch unit having such a fluid guiding device.

Description

Technical Field

[0001] This invention relates to a fluid guiding device for a clutch unit and a clutch unit having such a fluid arrangement and a wet friction plate clutch. The friction plate clutch is used in a drive system for torque transmission through frictional engagement between two drive components, such as a drive shaft and / or drive wheels. This friction plate clutch enables switching of the drive system under torque loads at arbitrary speed differences. The wet friction plate clutch comprises multiple friction plates that are cooled or lubricated by an surrounding fluid, such as oil. Background Technology

[0002] A wet clutch unit for a motor vehicle is known from DE 102015220446 B3. This wet clutch unit includes a friction clutch having a first friction disc associated with a drive element and a second friction disc associated with a driven element, the first and second friction discs forming a friction disc assembly. The first friction disc has a first recess, and the second friction disc has a second recess. The first and second recesses overlap radially and axially to form the friction disc assembly-recess. A fluid distributor is rigidly disposed on the drive element, the fluid distributor having a fluid chamber and a fluid guide groove. The fluid chamber extends axially into the friction disc assembly-recess to supply fluid to the friction disc assembly. The fluid guide groove extends axially toward a bearing to supply fluid to the bearing.

[0003] A hydraulic supply device is known from DE 102011086376 B4 for a disc brake operating in a sliding motion within a transmission mechanism module. The hydraulic supply device includes an oil passage through which oil flow is controlled by a valve, providing additional oil at predetermined points during the sliding phase. For this purpose, an inner disc support is provided with a collection groove surrounding a constant diameter. Oil injected into the collection groove enters the planetary gear set and then the disc brake through an elongated hole in the inner disc support.

[0004] A clutch device for a drive system of a motor vehicle is known from EP 3354920 A1. This clutch device includes: a wet friction plate clutch; a support plate against which a disc assembly is axially supported; an axially movable pressure plate for loading the disc assembly; an operating device for the friction plate clutch; and a flow regulator for controlling the volumetric flow rate of oil through the clutch. The inner disc support of the clutch has multiple boreholes in an area overlapping axially with the disc assembly, through which lubricant can flow toward the disc assembly. The flow regulator has an adjustment mechanism adjustable by the operating device, the adjustment mechanism having multiple cover sections for covering the opening area of ​​the passage. This allows for on-demand control of the oil supply.

[0005] A drive system is known from US 8388486 B2, which has a rear drive shaft that can be engaged or disengaged as needed. For this purpose, a controllable clutch is provided in the rear differential device between the differential and the half shaft.

[0006] Generally, adequate lubrication of the friction clutch is important to ensure sufficient lubrication of the components rotating relative to each other and to dissipate the heat generated by friction. Here, only with sufficiently high cooling capacity can high torque be provided at low speeds simultaneously. Summary of the Invention

[0007] The objective of this invention is to provide a fluid guiding device that enables a reliable fluid supply and is easily manufactured. A further objective is to provide a clutch unit with such a fluid guiding device, which provides sufficiently good cooling performance, particularly during the slippery operation of the clutch.

[0008] According to the present invention, a fluid guiding device for a friction disc clutch is provided to achieve the aforementioned objective, comprising: an inner disc carrier having a longitudinal axis and having a carrier section, a shoulder section, and a shaft section, wherein the carrier section has a connecting structure radially externally, the connecting structure having protrusions and recesses distributed on its periphery to receive an inner disc having a compatible mating structure in a rotationally resistant and axially movable manner; and a fluid distribution element axially and securely connected to the inner disc carrier, wherein the fluid guiding element has an annular collection area. The device comprises a section and multiple connecting plate sections distributed on its periphery, in which the incoming fluid is collected. The connecting plate sections extend axially and each has a radially penetrating opening. The inner disc carrier has multiple longitudinal grooves radially on its periphery extending axially from the shoulder section into the carrier section. The connecting plate sections of the fluid distribution element are externally received in or cover the longitudinal grooves of the inner disc carrier, thereby forming fluid channels between the longitudinal grooves and the associated connecting plate sections, through which the fluid can flow.

[0009] The fluid guiding device offers the advantage of allowing fluid to flow rapidly from the collection section along the connecting plates of the fluid guiding element into the longitudinal grooves of the inner disc carrier towards the disc assembly. The fluid is distributed peripherally due to the peripherally distributed connecting plates. In this sense, the fluid guiding element can also be referred to as a fluid distribution element. The longitudinal grooves in the inner disc carrier provide a continuous geometry that facilitates uniform and rapid fluid flow. Overall, this provides highly efficient passive cooling, making the fluid guiding device particularly well-suited for transmitting high torque, especially in clutch units, at simultaneously low speeds.

[0010] Here, the fluid is used to dissipate heat generated by friction and to lubricate components that come into frictional contact with each other. In this regard, the fluid is also referred to as a coolant or lubricant. Oil is typically used as the fluid. The fluid, which passes through the annular gap between the free end of the collection section and the shaft section, is collected in the annular collection section and flows axially towards the carrier section from there. Preferably, the portion in front of the oil guide plate has a circularly closed oil-collecting geometry that is securely fitted to the inner disc carrier. Therefore, fluid deflected radially outward from the rotating inner disc carrier is collected and flows along the inner wall of the collection section towards the connecting plate section.

[0011] According to one embodiment, the annular collection section may have a radially inwardly pointing constriction at its axial end. This constriction prevents fluid from flowing back from the annular section into the housing cavity, where the inner disc support is rotatably supported. Alternatively or supplementarily, the fluid guiding element may taper axially from the axial end toward the connecting section. Both of these measures contribute to improved flow characteristics, or a larger fluid volumetric flow rate, and thus contribute to efficient cooling.

[0012] The annular collection section of the fluid distribution element is preferably closed around the periphery and extends axially beyond the shoulder section. Here, the annular collection section can protrude beyond the side of the shoulder element by at least 0.1 or 0.2 times the axial length of the carrier section. With this design, the collection section forms a relatively large annular chamber in which the surrounding sprayed oil can be collected and from which it can flow further toward the disc section.

[0013] Following the annular collection section, the fluid distribution element can have a particularly cylindrical connecting section that moves along the outer peripheral surface of the shoulder section of the carrier element. Here, the fluid connecting element can be connected to the carrier element via a force-fitting connecting portion, for example, by means of a press connection, according to a feasible embodiment. Alternatively or supplementarily, the fluid guiding element can also be connected to the carrier element via a form-fitting connecting element, for example, by means of a locking connecting portion. The corresponding locking element can be provided at the cylindrical connecting section and / or at the end of the connecting section.

[0014] The shape of the connecting plate segment is, in principle, arbitrary, but preferably adapted to the design of the longitudinal groove of the inner disc carrier. The connecting plate segment can, for example, be designed as an elongated element extending axially, that is, parallel to the longitudinal axis; this connecting plate segment can also be referred to as a connecting element. According to a feasible design, the connecting plate segment of the fluid distribution element can have a radially outwardly pointing recess. The recess can be designed as an elongated shaped portion or an arch. The recess increases the radial planar moment of inertia, thereby improving stiffness and preventing bending at high speeds. Preferably, the recess or arch has a height lower than the radial height of the connecting structure. A radial gap can be provided between the connecting plate segment and the disc connected to the carrier element.

[0015] Preferably, at least a portion of the radial through-openings in the connecting plate sections are positioned axially offset relative to each other. In this way, oil can flow toward the disk assembly in different axial regions or different transverse planes, thereby achieving a uniform oil distribution and good cooling effect over its overall length. It is particularly advantageous that the through-openings are arranged in the connecting plate sections such that all openings together cover at least half, preferably two-thirds, of the length of the connecting structure for the disks. The number of connecting plates distributed on the periphery can be selected according to requirements; the fluid distribution element can, for example, have two, three, four, or more connecting plate sections, which can be distributed particularly evenly on the periphery. The number and arrangement of the peripherally distributed connecting plate sections preferably correspond to the number and arrangement of the longitudinal grooves in the inner disk carrier.

[0016] The connecting section radially covers the longitudinal groove of the inner disc support, thereby forming a substantially closed channel between the corresponding longitudinal groove and the associated connecting section, through which fluid flows toward the opening. In an embodiment relating to the radially outwardly pointing, longitudinally extending vault of the connecting section, this creates a basin shape in which oil flows toward the opening. For targeted oil flow toward the corresponding opening, it is advantageous that the connecting section covers the longitudinal groove to the maximum extent possible. To this end, the connecting section can cover, for example, at least 90% of the net area of ​​the associated longitudinal groove in a radial view.

[0017] According to one design, the oil guiding element can be manufactured as a sheet metal deformable part made of metal. Alternatively, the oil guiding element can also be made of plastic, which offers advantages in molding technology, such as the inclusion of clamping or locking features.

[0018] The inner disc bearing can be manufactured as a forging and / or by machining. Here, the longitudinal grooves and connecting structures can be manufactured by deformation or by cutting.

[0019] The longitudinal groove is preferably arranged circumferentially between two recesses in the connecting structure. The maximum width of the connecting piece section can, for example, be less than the circumferential spacing between three or two adjacent recesses in the connecting structure. The bottom of the longitudinal groove of the inner disc carrier is preferably located at a smaller radius than the deepest region of the connecting structure for the inner disc. In other words, relative to the outer circumferential surface of the disc carrier, the engaging element for the disc can extend radially outward, while the groove is formed radially inward. The depth of the longitudinal groove can, for example, be between 0.5 and 1.5 times the radial height of the connecting structure. The longitudinal groove preferably extends at least 75% of the axial extension of the connecting structure for the disc. The groove can have radially inwardly oriented grooves at its ends in the shoulder section, so that fluid can flow well from the collection section into the groove. The longitudinal groove can be particularly axially closed at its oppositely positioned ends.

[0020] The inner disc carrier can have a centrally located longitudinal bore and multiple radially extending openings distributed around its periphery towards the longitudinal groove. This allows for additional oil supply to the disc from the central internal opening of the disc carrier. Depending on the operating conditions, the openings also prevent fluid blockage in the fluid passages. Here, fluid can flow from the longitudinal groove through the radial openings into the central longitudinal bore and then re-enter the fluid circulation, where it can lubricate other components, such as bearings or seals, if necessary. The central longitudinal bore can have an internal annular groove, wherein the radially extending openings are formed in the carrier section in the axially overlapping area of ​​the internal annular groove and the external longitudinal groove.

[0021] The solution further comprises a clutch unit for a drive system of a motor vehicle, the clutch unit including: a wet friction plate clutch having an outer disc carrier in which a disc assembly consisting of an outer disc and an inner disc is arranged; a support plate against which the disc assembly is axially supported; an axially movable pressure plate for applying an axial load to the disc assembly; an operating device for operating the friction plate clutch by axial movement of the pressure plate; and a fluid guiding device according to one or more embodiments of the above-mentioned embodiments, wherein the inner disc carrier is rotatably supported relative to the outer disc carrier about a rotation axis, wherein the connecting structure between the inner disc of the disc assembly and the inner disc carrier is anti-rotationally and axially movable, so that when the inner disc carrier rotates, fluid flows from the collection section along the inner wall of the fluid distribution element toward the connecting plate section to lubricate the disc assembly.

[0022] The clutch unit enables the drive system to be engaged or disengaged as needed. The device can be designed into the drive system of vehicles with driven axles, all-wheel-drive vehicles, hybrid vehicles, and / or electric vehicles. The clutch unit can be located at any point in the drive system along the power path between the drive source and the wheels, for example, in front of, in, or behind the transmission, and / or in front of, in, or behind the helical gear transmission, and / or in front of, in, or behind the distributor transmission unit (PTU), and / or within the longitudinal drive shaft, or in front of, in, or behind the differential transmission, and / or within the half-shaft.

[0023] The clutch unit according to the invention has the advantage of providing high torque at low speeds due to its efficient oil injection system. A fluid distribution device assists in utilizing the full potential of the controllable clutch. Oil received in the collection section of the fluid guiding element is guided towards the longitudinal groove, where it can flow further outward toward the disc assembly due to centrifugal force through boreholes in the connecting plate section. The oil can return to the oil pan through corresponding boreholes in the outer disc carrier. The flowing oil can also cool and lubricate other moving mechanical components, such as bearings or seals.

[0024] For operating the clutch, a controllable operating device is preferably provided, which can move the pressure plate toward or away from the disc assembly (i.e., in the sense of being closed) or away from the disc assembly (i.e., in the sense of being open). The operating device can, in principle, have any arbitrary design to generate the clamping force. For example, an electric motor-driven or hydraulic actuator can be used. An electric motor-driven actuator can include a rotary drive and a ball bearing ramp, which convert rotational motion into axial motion.

[0025] A further solution lies in a transmission mechanism for a drivetrain of a motor vehicle, comprising: a differential transmission mechanism designed to distribute the introduced torque to two output members; and a clutch unit as described above, wherein the shaft section of the inner disc carrier is anti-rotationally connected to one of the two output members. Such a transmission mechanism can, when needed, transmit the torque introduced by the longitudinal drive shaft to the corresponding axle, or disengage the drive shaft, wherein all intermediate positions of the friction clutch are also feasible. Attached Figure Description

[0026] The preferred embodiments will now be explained with reference to the accompanying drawings. Here are some examples:

[0027] Figure 1 shows a three-dimensional exploded view of the fluid guiding device according to the present invention;

[0028] Figure 2 shows the fluid guiding device from Figure 1 together with the disk assembly in a longitudinal sectional view;

[0029] Figure 3 The fluid guiding device from Figure 2 is shown in detail, along with the marked oil flow.

[0030] Figure 4 The fluid guiding device along with the disk assembly from Figure 1 is shown in cross-section or axial view;

[0031] Figure 5 shows, in three dimensions, the clutch unit according to the invention together with the fluid guiding device according to Figure 1;

[0032] Figure 6 shows the transmission mechanism along with the clutch unit from Figure 5 in a longitudinal sectional view. Detailed Implementation

[0033] The following figures, 1 to 2, are described together. Figure 3 A fluid guiding device 2 according to the invention is shown, which is used for friction plate clutches, and particularly for drive systems of motor vehicles.

[0034] The fluid guiding device 2 has an inner disc carrier 3 and a fluid guiding element 4. The inner disc carrier has a longitudinal axis A3, and the inner disc carrier and the fluid guiding element are securely connected to each other. The inner disc carrier 3 includes a carrier section 5 for the inner disc, a shaft section 6 for anti-rotational connection with a drive element, and a shoulder section 7 disposed between them. The carrier section 5 has a connecting structure 8 radially externally, which has protrusions 9 and recesses 10 distributed on its periphery. The inner disc with a matching mating structure can be anti-rotationally and axially pushed to the connecting structure. In addition, the inner disc carrier 3 has a plurality of longitudinal grooves 11 on its radially external circumferential surface, which extend axially from the shoulder section 7 into the carrier section 5. The inner disc carrier 3 can be manufactured as a formed part, for example by forging, wherein, as an alternative or supplementary option, it can also be manufactured by machining, cutting, such as turning, drilling, or milling. The fluid guiding element 4 can be manufactured, for example, as a deformable sheet material made of metal or plastic.

[0035] The fluid guiding element 4 has an annular collection section 12 and a plurality of peripherally distributed connecting plate sections 13, in which the incoming fluid is collected. These connecting plate sections extend axially and each has a radially penetrating opening 14. The connecting plate sections are generally indicated by reference numeral 13, with each connecting plate also having 13, 13′, 13″, and 13″′. The same applies to the openings 14. As is particularly evident in Figure 2, the connecting plate sections 13 are externally received in the longitudinal groove 11 of the inner disc carrier 3, or rather, radially outwardly cover the longitudinal groove. Here, the inner disc carrier 3 and the fluid guiding element 4 work together advantageously such that cooling oil can flow easily from the collection section 12 along the inner wall 15 of the fluid guiding element 4 into the longitudinal groove 11 of the carrier element, or along the connecting plate sections 13 and through the openings 14 of the fluid guiding element 4 toward the disc assembly. Figure 3 Arrow P indicates the flow direction. A continuous geometry is achieved through the longitudinal grooves 11 in the inner disc support 3, allowing the cooling oil to flow well towards the disc assembly. Further preferred details are described below.

[0036] The annular collection section 12 has a radially constricted portion 16 at its axial end, which supports the oil in the annular chamber 17 and thus prevents backflow of the oil. As can be seen particularly in Figure 2, the wall of the collection section 12 tapers from the radially constricted portion 16 toward the connecting plate section 13. The annular collection section 12 extends laterally across the shoulder section 7 toward the shaft section 6 in an axial direction. Here, the length of the collection section 12 can be, for example, at least 0.1 or 0.2 times the length of the connecting plate section 13.

[0037] The fluid guiding element 4 may have a particularly columnar connecting section 18 between the protruding collection section 12 and the connecting piece section 13, which is placed on the outer peripheral surface 19 of the shoulder section 7 by press connection. It goes without saying that other connecting measures for connecting the fluid guiding element 3 to the inner disc carrier 3 may also be provided, such as form-fitting and / or material-fitting connecting parts.

[0038] The connecting plate section 13, extending axially away from the annular base, each has a recessed portion 20 that arches radially outward from the radius of the base; this recessed portion can also be referred to as an arch. The recessed portion, or arch, provides high stiffness, preventing the connecting plate from bending even at high speeds. The height of the arch is preferably designed such that the connecting plate remains in contact with the clutch disc at all times. A radial through-hole 14 towards the disc is arranged in the arch 20.

[0039] Here, particularly in Figures 1 and 2, it can be seen that the radial through openings 14 are arranged axially offset relative to each other in the connecting plate sections 13. In this way, oil can flow toward the disc assembly in different axial regions or different transverse planes. Of the four connecting plate sections 13, 13′, 13″, and 13″′ shown here, opening 14 is axially adjacent to the annular section, opening 14′ is axially offset from the annular section by a distance, another opening 14″ is approximately located in the middle region of the connecting plate, and one opening is adjacent to the end of the connecting plate.

[0040] The connecting section 13 forms a cover for the longitudinal groove 11 of the inner disc carrier 3, thereby forming a substantially closed channel 21 between the longitudinal groove 11 and the connecting section 13, through which fluid flows toward the opening 14. Oil flows along the basin shape formed by the radially outwardly pointing, longitudinally extending dome 20 and then escapes from the corresponding opening 14 due to centrifugal force. For targeted oil flow toward the corresponding opening, the connecting section 13 covers the longitudinal groove 11 to a maximum extent, for example, at least 90%.

[0041] Multiple connecting segments distributed on the periphery are formed by longitudinal grooves 11 distributed around the periphery, and these connecting segments collectively form the connecting structure 8 of the inner disc carrier 3. Each connecting segment is formed as a longitudinal tooth, which has teeth and tooth gaps between the teeth. The longitudinal grooves 11 are arranged circumferentially adjacent to the recesses 10 of the connecting structure 8. In other words, the bottom of the longitudinal grooves 11 of the inner disc carrier 3 is at a radius R11 smaller than the deepest region (R10) of the recesses 10. Here, the depth of the longitudinal grooves can, for example, be between 0.5 and 1.5 times the radial height of the connecting structure 8. The longitudinal grooves 11 have closed ends in the axial direction, wherein the longitudinal grooves can extend at least 75% of the axial length of the connecting structure 8. The width of the longitudinal grooves 11, or the connecting segment 13, can, for example, be smaller than the periphery spacing between three or two recesses 10 adjacent in the circumferential direction. At the end of the shoulder side, the longitudinal groove 11 can have a radially inwardly pointing groove 22 in the shoulder section 7, so that fluid can flow particularly well from the collection section 12 into the groove 11.

[0042] The inner disc carrier 3 can have a central longitudinal opening 23 and a plurality of radially through openings 24 distributed around the periphery towards the longitudinal groove 11. Excess oil can then flow radially inward to prevent oil blockage in the fluid channels, or, depending on the operating conditions, additional oil supply to the disc can be achieved from the central internal opening 23 of the disc carrier. The central longitudinal opening 23 can have an internal annular groove 25, wherein the radially through openings 24 are formed in the carrier section 5 in the axially overlapping area of ​​the internal annular groove 25 and the external longitudinal groove 11. In this way, the radial openings 24 can be manufactured easily, especially without the need for a separate drilling process.

[0043] Figure 5 shows the clutch unit 26 according to the invention together with the fluid guiding device 2 according to the invention in a perspective view. Further details of the clutch can be seen from Figure 6, which shows a longitudinal sectional view of the clutch.

[0044] The clutch unit 26 includes a wet friction plate clutch 27 and an operating device 28 for controlling the torque that can be transmitted by the friction plate clutch.

[0045] The friction disc clutch 27 includes: an inner disc carrier 3, to which an inner disc 29 is connected in an anti-rotational manner and axially movable; and an outer disc carrier 30, to which an outer disc 31 is connected axially movable and anti-rotational. The outer disc 31 and the inner disc 29 are arranged alternately along the axial direction and together form a disc assembly 32. The disc assembly 32 is axially supported against a support section 33 of the outer disc carrier 30 in a first axial direction. A pressure plate 34 is provided for loading the disc assembly 32, and the pressure plate is axially movable by a controllable operating device 28. The outer disc carrier 30 is rotatably supported about a rotation axis A3 by a first bearing 59 in the housing 44 and a second bearing 60 on the journal section of the inner disc carrier 3.

[0046] The operating device 28 is designed, or rather, controlled, to allow the torque to be variably set as needed by the friction clutch 27. Here, the friction clutch 27 can achieve any intermediate position besides the open and closed positions. In the open position, no torque is transmitted between the inner and outer disc supports 30, while in the closed position, the disc supports rotate together around the axis of rotation and transmit the full torque. For example, the torque to be transmitted can be determined in the electronic control unit (ECU) based on continuously sensed driving state parameters of the vehicle. The ECU can then transmit a corresponding control signal to the operating device 28, which in turn loads the pressure plate 34, thereby allowing the friction clutch 27 to transmit the desired torque.

[0047] An axial bearing 35 is provided between the operating device 28 and the friction plate clutch 27, which enables axial force transmission from the operating device to the pressure plate 34 while simultaneously rotating and decoupled. The operating device 28 includes a ball ramp mechanism and a drive unit. The ball ramp mechanism has a support ring 36 and an adjusting ring 37. The support ring supports a fixed component axially, and the adjusting ring is opposite the support ring 36 and can be driven to rotate about the rotation axis A3. Ball grooves 38 and 39, distributed peripherally, are respectively arranged in the opposing end faces of the support ring 36 and the adjusting ring 37. These ball grooves have variable depths peripherally and receive balls. To operate the ball ramp unit, an electric motor (not shown) is used as the drive device, which can twist the adjusting ring 37 relative to the support ring 36 via a gear transmission mechanism 38. The gear transmission mechanism 38 includes a drive wheel 40 that can be rotated by the electric motor and is drivenly connected to an output wheel 41. The output wheel 41 is connected to the adjusting ring 37, and the adjusting ring is designed as a single piece.

[0048] When the drive wheel 40 rotates by means of an electric motor, the output wheel 41 and therefore the adjusting ring 37 twist relative to the support ring 36. Depending on the direction of rotation of the motor shaft, the adjusting ring 37 can rotate in a first rotation direction or in a second, opposite rotation direction. Starting from a starting position where the two rings 36, 37 are axially close to each other, the twisting of the adjusting ring 37 relative to the support ring 36 in the first rotation direction causes the balls held in the ball grooves to move to a lower depth region, thereby moving the adjusting ring axially toward the clutch 27. The adjusting ring 37 is axially supported against a pressure plate 34 via an axial bearing 35, which loads the disc assembly. In this way, the clutch 27 is closed. In the fully closed state, the disc assembly is loaded to the maximum extent, thereby transmitting full torque between the inner disc support 3 and the outer disc support 30. If the electric motor and therefore the adjusting ring 37 are twisted in the opposite second rotational direction, the balls held in the ball grooves move to a region with a greater groove depth, wherein the adjusting ring can be axially loaded or moved toward the support ring by a spring device (not shown). In this way, the clutch 28 can be disengaged again.

[0049] The clutch unit 26 provides excellent cooling to the disc assembly even at low speeds and high torque. Such a clutch unit can, in principle, be used anywhere in the drivetrain of a motor vehicle. One application example of the clutch unit 26 according to the invention is in the transmission mechanism 42 of FIG. 6, as described below.

[0050] The transmission mechanism 42 includes a differential transmission mechanism 43 having a fixed housing 44 in which a differential housing 45 is rotatably supported by two bearings 46, 47 about a rotation axis A45. A ring gear 48 is provided to introduce torque into the differential housing 45, and is securely connected to the differential housing, for example by means of a welded or threaded connection. In the differential housing 45, a plurality of differential gears 49 are rotatably supported on pins 50 about a pivot. Two differential gears 49 rotate together with the differential housing 45 and mesh with a first driven gear and a second driven gear 51, 52, respectively, which are arranged coaxially with the rotation axis A45. The two driven gears 51, 52, which can also be referred to as half-shaft gears, each have longitudinal teeth 53 (splines) into which corresponding mating teeth of the drive shaft for torque transmission can be engaged. The two driven wheels 51 and 52 are axially supported relative to the differential housing 45 by a sliding disc connected in the middle.

[0051] The housing 44 is constructed in multiple parts and includes: a housing section 54 on the transmission side where the differential transmission mechanism 43 is housed, and a housing section 55 on the clutch side where the clutch unit 26 is housed. The two housing sections are connected to each other by flanges, but are not limited thereto. An intermediate plate 56 is provided between the two housing sections 54 and 55, in which the bearing 46 of the differential housing 45 is housed. The inner disc support 3 of the clutch unit 26 is connected to the drive wheel 51, which is adjacent to the clutch and extends through a through opening 57 in the intermediate plate 56. An operating device 28 is axially arranged between the intermediate plate 56 and the clutch unit 26, wherein a support ring 36 axially supports the intermediate plate. The intermediate plate 56 has a sleeve-shaped protrusion 58, or flange, in the region of the fluid guiding element 4, which extends into the annular chamber 17 of the fluid guiding element with axial overlap with the collecting section 12. This creates an oil labyrinth structure, which allows the sprayed oil to be well guided from the sleeve protrusion into the annular chamber 17 and from there into the channel 21.

[0052] The transmission mechanism 42 is able to provide high torque at low speeds and transmit it to both half-shafts simultaneously thanks to the efficient lubrication system of the clutch unit 26. Here, the fluid distribution device 2 has an advantageous effect in utilizing the full potential of the controllable clutch. The oil flowing through the clutch also cools and lubricates other moving mechanical components, such as the bearings or seals of the clutch unit 26 or the transmission mechanism.

[0053] List of reference numerals in the attached diagram:

[0054] 2. Fluid guiding device

[0055] 3. Inner disc bearing components

[0056] 4 fluid guiding elements

[0057] 5 load-bearing sections

[0058] 6-axis section

[0059] 7 shoulder section

[0060] 8 connection structure

[0061] 9 protrusions

[0062] 10 concave

[0063] 11 longitudinal grooves

[0064] 12 collection sections

[0065] 13 connecting sections

[0066] 14 through openings

[0067] 15 Inner Wall

[0068] 16 contraction sections

[0069] 17 Circular Chamber

[0070] 18 connecting sections

[0071] 19 outer perimeter

[0072] 20 sunken sections

[0073] 21 channels

[0074] 22 trenches

[0075] 23 Longitudinal opening

[0076] 24 radial openings

[0077] 25 Annular Groove

[0078] 26 clutch units

[0079] 27 Friction Plate Clutch

[0080] 28 Control Devices

[0081] 29 inner disc

[0082] 30 outer disc bearing

[0083] 31 outer disc

[0084] 32-disc set

[0085] 33 Support Plate

[0086] 34 pressure plate

[0087] 35 axial bearing

[0088] 36 support rings

[0089] 37 Adjustment Ring

[0090] 38 ball grooves

[0091] 39 ball grooves

[0092] 40 drive wheels

[0093] 41 Output Wheel

[0094] 42 Transmission Mechanism Device

[0095] 43 Differential transmission mechanism

[0096] 44 casing

[0097] 45 differential housing

[0098] 46 bearing

[0099] 47 bearing

[0100] 48 ring gears

[0101] 49 Differential Gear

[0102] 50 sales

[0103] 51 Driven wheel

[0104] 52 driven wheels

[0105] 53 longitudinal teeth

[0106] 54 Shell Section

[0107] 55 Shell Section

[0108] 56 intermediate plate

[0109] 57 through opening

[0110] 58 protrusions

[0111] 59 bearing

[0112] 60 bearing

[0113] Axis A

[0114] R is the radius.

Claims

1. A fluid guiding device for a friction plate clutch, comprising: The inner disc carrier (3) has a rotation axis (A3) and a carrier section (5), a shoulder section (7) and a shaft section (6), wherein the carrier section (5) has a connecting structure (8) radially externally, the connecting structure having protrusions (9) and recesses (10) distributed on the periphery, so as to receive the inner disc (29) with a matching mating structure in a rotationally resistant and axially movable manner. A fluid guiding element (4) is axially and firmly connected to the inner disc support (3). The fluid guiding element (4) has an annular collection section (12) and a plurality of connecting plate sections (13) distributed on the periphery. The collection section is capable of collecting the incoming fluid. The connecting plate sections extend in the axial direction and each connecting plate section has a radial through opening (14). Its features are, The inner disc carrier (3) has a plurality of longitudinal grooves (11) radially outward on its periphery, which extend axially from the shoulder section (7) into the carrier section (5). The connecting piece section (13) of the fluid guiding element (4) covers the longitudinal grooves (11) of the inner disc carrier (3), thereby forming channels (21) for the fluid between them. The fluid guiding element (4) has a connecting section (18) that moves on the outer peripheral surface (19) of the shoulder section (7) of the inner disc carrier (3).

2. The fluid guiding device according to claim 1, Its features are, The fluid guiding element (4) and the inner disc carrier (3) are connected by axial pressure connection.

3. The fluid guiding device according to claim 1, Its features are, The connecting piece section (13) of the fluid guiding element (4) has a sunken portion (20) pointing radially outward.

4. The fluid guiding device according to any one of claims 1 to 3, Its features are, The annular collection section (12) of the fluid guiding element (4) extends axially beyond the shoulder section (7) and has a radially constricted portion (16) at its axial end and tapers axially toward the connecting section (18).

5. The fluid guiding device according to any one of claims 1 to 3, Its features are, At least a number of radial through openings (14) of the connecting section (13) are arranged axially offset relative to each other.

6. The fluid guiding device according to any one of claims 1 to 3, Its features are, The fluid guiding element (4) has at least three connecting segments (13) that are evenly distributed around the periphery.

7. The fluid guiding device according to any one of claims 1 to 3, Its features are, The connecting section (13) covers at least 90% of the net area of ​​the corresponding longitudinal groove (11) in the radial view.

8. The fluid guiding device according to any one of claims 1 to 3, Its features are, The longitudinal grooves (11) are respectively arranged in the circumferential direction between the two recesses (10) of the connecting structure (8). The maximum width of the connecting piece section (13) is less than the periphery spacing between the three adjacent recesses (10) in the circumferential direction of the connecting structure (8).

9. The fluid guiding device according to any one of claims 1 to 3, Its features are, The bottom of the longitudinal groove (11) of the inner disc carrier (3) is on a radius (R11) smaller than the deepest region of the connecting structure (8) for the inner disc (29).

10. The fluid guiding device according to any one of claims 1 to 3, Its features are, The longitudinal groove (11) has a radially inwardly pointing groove (22) in the shoulder section (7) and / or closes in the axial direction at the end opposite to the shoulder section (7).

11. The fluid guiding device according to any one of claims 1 to 3, Its features are, The inner disc support (3) is manufactured as a forging, wherein the longitudinal groove (11) and the connecting structure (8) are formed by forging.

12. The fluid guiding device according to any one of claims 1 to 3, Its features are, The inner disc support (3) has a central longitudinal bore (23) and a plurality of radial through openings (24) distributed on the periphery relative to the longitudinal groove (11).

13. The fluid guiding device according to claim 12, Its features are, The central longitudinal bore (23) has an inner annular groove (25), wherein the radial through opening (24) is formed in the axial overlap region of the inner annular groove (25) and the outer longitudinal groove (11).

14. A clutch unit used in the drive system of a motor vehicle, comprising: A wet friction plate clutch (27) having an outer disc carrier (30) in which a disc assembly (32) consisting of an outer disc and an inner disc is arranged. Support plate (33), the disk assembly (32) is axially supported against the support plate; A pressure plate (34) capable of axial movement, used to apply an axial load to the disk assembly (32); and A control device (28) is used to operate the friction plate clutch (27) by means of the axial movement of the pressure plate. The feature is that it is a fluid guiding device (2) according to any one of claims 1 to 13. The inner disc support (3) is rotatably supported relative to the outer disc support (30) about the rotation axis (A3), and the connection structure (8) between the inner disc (29) of the disc assembly (32) and the inner disc support (3) is anti-rotationally connected and axially movable, so that when the inner disc support (3) rotates, oil flows from the collection section (12) along the inner wall of the fluid guiding element (4) toward the connecting piece section (13) to lubricate the disc assembly (32).

15. The clutch unit according to claim 14, Its features are, The inner disc support (3) is rotatably supported in the housing (44), wherein the housing (44) has a sleeve protrusion (58) that extends axially into the annular chamber (17) of the fluid guiding element (4), thereby forming a fluid labyrinth structure.

16. A transmission mechanism for use in the drive system of a motor vehicle, comprising: A differential transmission mechanism (43) is designed to distribute the introduced torque to two output components (51, 52). The feature is that the clutch unit (26) is as described in claim 14 or 15. The shaft section (6) of the inner disc carrier (3) is connected to one of the two output components (51, 52) in an anti-rotational manner.

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