JP5738305B2 - Clutch device - Google Patents

Description

  The present invention relates to a multi-clutch device, particularly a wet twin clutch, wherein the multi-clutch device is used in a power train provided with a prime mover and a transmission arranged following the clutch device. Are coupled directly or indirectly to the input shaft of the prime mover and housed in a bell-shaped clutch case that does not rotate simultaneously with the input shaft of the prime mover. Each of the multi-plate clutches has a friction plate support on the input side and a friction plate support on the output side, and the friction plate supports are alternately arranged in the axial direction. The present invention relates to a multi-clutch device having a plurality of friction plates.

  The wet twin clutch mentioned at the beginning is known from German Offenlegungsschrift 102006049731. In this known wet twin clutch, the operating force generated by the operating device is supported via an input side friction plate support, a support bearing, and a clutch cover firmly coupled to a bell-shaped clutch case. ing. For this purpose, the input side friction plate support, the support bearing and the clutch cover must be designed to be correspondingly strong. Each operating force is related to the torque to be transmitted. Correspondingly, when the torque is increased, a correspondingly higher operating force and in particular a correspondingly stronger design of the clutch cover is required. The ZMS output side member and the clutch input side member are also supported through the clutch cover. The wet twin clutch is operated as a lever. The operating device has a rotary lever that can be operated electrically or hydraulically.

  The object of the present invention is to improve the multi-clutch device mentioned at the outset, to improve the support of the operating force and / or to improve the radial and / or axial bearing and / or The cooling oil guidance is improved and / or the design of the components of the multi-clutch device is further optimized in terms of manufacturing technology.

  In order to solve this problem, according to the first clutch device of the present invention, the clutch device is used in a power train including a prime mover and a transmission arranged following the clutch device. The clutch device comprises at least one, preferably two, multi-plate clutches, each of which has one input-side friction plate support, one output-side friction plate support, A plurality of friction plates provided alternately in the axial direction, and the clutch device further comprises an operating device, and one or more multi-plate clutches are provided with cover bearings on the operating device. Are connected to each other to form a constituent unit, and a clamping element is formed on the housing of the operating device with respect to a bell-shaped clutch case via a tightening element that absorbs the force and moment generated during operation. Preload is applied in the axial direction Te.

  According to an advantageous aspect of the first clutch device of the present invention, the housing of the operating device has an axial convex portion or concave portion, and the clutch and the operating device via the convex portion or concave portion. Is formed on the transmission side in a radial direction by a bell-shaped clutch case, and another radial support is provided between the clutch input hub and one of the plurality of transmission input shafts. This is done via a movable bearing provided.

  According to an advantageous aspect of the first clutch device of the present invention, the multi-plate clutch is arranged to overlap in the radial direction, and the friction plate support on the input side of the multi-plate clutch on the radially outer side is operated. Although it is relatively rotatable in the radial direction via a supporting metal thin plate or supporting pot in the housing of the device, it is supported immovably in the axial direction, so that the power flow of the operating force generated by the operating device is A power flow is provided that is supported by the housing of the operating device via the axially stationary support portion of the friction plate support on the input side on the radially outer side and closed inside the clutch device.

  Furthermore, in order to solve the above-described problem, according to the second clutch device of the present invention, the clutch device is used in a power train that includes a prime mover and a transmission that is arranged following the clutch device. The clutch device comprises at least one, preferably two, multi-plate clutches, each of which comprises one input-side friction plate support and one output-side friction plate And a plurality of friction plates provided alternately in the axial direction, and the clutch device further includes an operation device, one or more multi-plate clutches, and an operation device. Are coupled to each other via a cover bearing to form a constituent unit, and a fixed bearing is disposed between the clutch input hub and one of the plurality of transmission input shafts, A bearing acting exclusively in the radial direction is arranged between one of the transmission input shafts, and an axially flexible torque support member is provided between the housing of the operating device and the bottom of the bell-shaped clutch case. Is provided.

  According to an advantageous aspect of the second clutch device according to the present invention, there is provided a pipe connection portion set in the axial direction or set in the radial direction, and the pipe connection portion is provided in the operating device. A hydraulic medium supply unit on the transmission side is connected.

  Furthermore, in order to solve the above-described problem, according to the third clutch device of the present invention, the clutch device is used in a power train that includes a prime mover and a transmission that is arranged following the clutch device. The clutch device comprises at least one, preferably two, multi-plate clutches, each of which comprises one input-side friction plate support and one output-side friction plate And a plurality of friction plates provided alternately in the axial direction, and the clutch device further includes an operation device, one or more multi-plate clutches, and an operation device. Are coupled to each other via a cover bearing to form a structural unit, and a bearing acting exclusively in the radial direction is disposed between the clutch input hub and one of the plurality of transmission input shafts, Operating equipment In between one of the housing and a plurality of transmission input shaft, supported in the radial direction exclusively through the flexible plate to the bottom of the bell-shaped clutch case it is being performed.

  According to an advantageous aspect of the third clutch device according to the present invention, a pilot bearing is provided between the clutch input hub and the crankshaft.

  Furthermore, in order to solve the above-described problem, according to the fourth clutch device of the present invention, the clutch device is used in a power train that includes a prime mover and a transmission that is arranged following the clutch device. The clutch device includes at least one multi-plate clutch, and the multi-plate clutch includes one input-side friction plate support, one output-side friction plate support, and an axial direction. The clutch device further includes an operating device, and the input friction plate support of the multi-plate clutch and the housing of the operating device are connected via a tension pot. Are connected to each other to form a structural unit, and the tension pot is axially fixed to the input friction plate support via a position fixing ring positioned radially outward. , Having an axial projection, which is at least partially covered in a radial direction on the position fixing ring based on the preload and operating force of the return spring in the assembled state of the clutch device. Thus, loosening of the position fixing ring under the rotational speed is avoided.

  Furthermore, in order to solve the above-described problem, according to the first multi-clutch device according to the present invention, the multi-clutch device includes a prime mover and a transmission arranged subsequent to the multi-clutch device. The multi-clutch device includes two multi-plate clutches that are fitted inward and outward in the radial direction, and each of the multi-plate clutches includes one friction plate support on the input side and one multi-plate clutch. A friction plate support on the output side and a plurality of friction plates provided alternately in the axial direction; and further, the multi-clutch device is provided with an operating device, and the multi-plate clutch and the operating device are Coupled to each other via a cover bearing to form a structural unit, an output friction plate support of a multi-plate clutch radially inward, and a transmission input shaft coupled to the output friction plate support A spring element is disposed between the output friction plate support of the radially inner multi-plate clutch and the output friction plate support of the radially outer multi-plate clutch. The first thrust bearing is disposed, and another thrust is provided between the output friction plate support of the radially outer multi-plate clutch and the input friction plate support of the radially outer multi-plate clutch. A bearing is arranged, and another thrust bearing is arranged between the input friction plate support of the multi-plate clutch on the radially outer side and the clutch cover, and the clutch cover is attached to the bell-shaped clutch case. It is fixed to the bottom in the axial direction.

  Furthermore, in order to solve the above-described problems, according to the second multi-clutch device of the present invention, the multi-clutch device includes a prime mover and a transmission arranged following the multi-clutch device. The multi-clutch device includes two multi-plate clutches that are fitted inward and outward in the radial direction, and each of the multi-plate clutches includes one friction plate support on the input side and one multi-plate clutch. A friction plate support on the output side and a plurality of friction plates provided alternately in the axial direction; and further, the multi-clutch device is provided with an operating device, and the multi-plate clutch and the operating device are Coupled to each other via a cover bearing to form a structural unit, an output friction plate support of a multi-plate clutch radially inward, and a transmission input shaft coupled to the output friction plate support A spring element is disposed between the output friction plate support of the radially inner multi-plate clutch and the output friction plate support of the radially outer multi-plate clutch. The first thrust bearing is disposed, and another thrust is provided between the output friction plate support of the radially outer multi-plate clutch and the input friction plate support of the radially outer multi-plate clutch. A bearing is arranged and a preload is applied in the axial direction to the bell-shaped clutch case in the housing of the operating device via a tightening element that absorbs force and moment during operation.

It is a half sectional view of the twin clutch which concerns on 1st Embodiment. It is the schematic of the internal power flow at the time of operation of the multi-plate clutch K2 arrange | positioned at the radial inside used for the twin clutch shown in FIG. It is the schematic of the support form of the twin clutch shown in FIG. 1 and FIG. FIG. 6 is a half sectional view of a twin clutch according to another embodiment provided with a friction plate support without play. It is the schematic regarding an assembly-type friction board support body. It is the schematic regarding an assembly-type friction board support body. FIG. 5 is a halved cross-sectional view of another embodiment of a twin clutch having an internally closed power flow operated through a double annular piston (“CSC”). FIG. 6 is a half sectional view of a twin clutch according to another embodiment that is compensated for axial play in the oil supply section and is stationary with respect to the transmission shaft. FIG. 5 is a half sectional view of a twin clutch according to another embodiment, which is provided with a radial oil supply portion and is floated in the axial direction. FIG. 6 is a half sectional view of a twin clutch according to another embodiment that is floatingly supported in the axial direction with a flexible plate bearing. FIG. 5 is a half sectional view of a twin clutch according to another embodiment, which is floated in the axial direction, with a flexible plate bearing and with a pilot. It is a half sectional view of the twin clutch which concerns on another embodiment provided with dry type ZMS. It is a half sectional view of the twin clutch which concerns on another embodiment provided with dry type ZMS, and the thrust bearing between the outer side friction plate support body and clutch cover of the outer clutch K1 is abbreviate | omitted. FIG. 5 is a half sectional view of a twin clutch according to another embodiment having a power flow closed inside, a wet ZMS, and a centrifugal pendulum (“FKP”). FIG. 15 is a half sectional view of a twin clutch according to another embodiment having a power flow closed inside, a wet ZMS, and a centrifugal pendulum (“FKP”); The tightening jaws are omitted.

  The invention will be explained in more detail below with reference to the corresponding exemplary embodiments.

  FIG. 1 shows a twin clutch 1 composed of two wet multi-plate clutches K1, K2 fitted inward and outward in the radial direction. In the twin clutch 1, the clutch K1 is disposed on the radially outer side, and the clutch K2 is disposed on the radially inner side. The twin clutch 1 is driven by an output hub 2 of a dual mass flywheel (hereinafter also referred to as ZMS) (not shown) provided in front of the clutch 1. A clutch cover 3 is located between the ZMS and the twin clutch 1. The clutch cover 3 separates the wet chamber 4 from the dry chamber 5. Static sealing of the clutch cover 3 with respect to the transmission housing 7 of a transmission (not shown) subsequently arranged in the power train is advantageous if the O-ring 6 or other fixing sealing element is used. Done through. For the twin clutch 1, sealing is preferably effected via a rotary shaft seal ring 8 as a moving sealing element.

  The output hub 2 of the ZMS is coupled to the clutch hub 9 through a tooth row so as not to be relatively rotatable. The clutch hub 9 is coupled to the friction plate support 10 on the input side of the clutch K1 that is disposed on the outer side in the radially inner and outer fittings. Alternatively, the clutch hub 9 and the input side friction plate support 10 may be integrally formed. The friction plate support 10 on the input side of the multi-plate clutch K1 (= the outer input friction plate support 10) and the clutch hub 9 coupled to the input friction plate support 10 so as not to rotate relative to each other are: A first transmission input shaft 15 (formed as a solid shaft) is supported in the radial direction via a radial bearing 16. The input friction plate support 10 has a dentition range. The input side friction plate 11 of the friction plate set of the outer multi-plate clutch K1 is attached to this dentition range, so that the outer input side friction plate 11 is not relatively rotatable. It is arranged to be movable in the axial direction of the object. The outer input friction plates 11 are alternately arranged with the outer output friction plates 12. The outer input friction plate 11 and the outer output friction plate 12 arranged alternately with the outer input friction plate 11 together form a friction plate set of the clutch K1. The outer friction plate 12 on the output side is coupled to the output friction plate support 13 on the outer side of the outer multi-plate clutch K1 so as to be movable in the axial direction, although it cannot be relatively rotated. The friction plate support 13 on the output side outside the multi-plate clutch K1 has a hub 14. The hub 14 is coupled to a transmission input shaft 15 of a twin clutch transmission (not shown).

  The input side friction plate support 10 of the outer multi-plate clutch K1 is connected to the input side friction plate support 10 of the multi-plate clutch K2 arranged radially inward via a coupling metal thin plate 17 attached to the input side friction plate support 10. It is connected to the friction plate support 18 on the inner input side. The friction plate on the inner side of the multi-plate clutch K2 arranged on the inner side in the radial direction is attached to the dentition range of the inner input friction plate support so as to be movable in the axial direction, although it cannot be relatively rotated. Yes. The friction plates on the inner side of the clutch K2 disposed on the radially inner side are alternately disposed with the friction plates on the inner output side. The inner friction plate on the output side is disposed on the inner friction plate support 19 on the inner side of the multi-plate clutch K2 so as to be movable in the axial direction although it cannot be relatively rotated. The inner output friction plate support 19 has a hub area. In this hub range, the inner friction plate support 19 on the output side is coupled to a second transmission input shaft 20 (formed as a hollow shaft).

  The friction plate support 19 on the output side inside the multi-plate clutch K2 arranged radially inside is thrust bearing 23 by a wave spring 21 (via a coupling piece 22 if necessary due to the structure). Is interposed and is pressed toward the friction plate support 13 on the output side outside the multi-plate clutch K1 disposed on the radially outer side. Instead of a wave spring, another spring element, for example a disc spring set, may be used. The friction plate support 13 on the output side outside the multi-plate clutch K1 arranged on the outer side in the radial direction further includes another thrust bearing 24 on the outer side of the multi-plate clutch K1 arranged on the outer side in the radial direction. It is pressed toward the friction plate support 10 or the clutch hub 9 on the input side. The friction plate support 10 on the input side outside the multi-plate clutch K1 arranged radially outside is further pressed toward the clutch cover 3 with another thrust bearing 25 interposed therebetween. The clutch cover 3 is supported by a transmission housing 7 via a position fixing element 26. As can be seen in particular in FIG. 1, the bearings 23, 24, 25 are preferably formed as thrust (needle roller) bearings. The coupling piece 22 is formed between the inner and outer output friction plate supports so as to allow a flow path for the cooling oil.

  In this embodiment, transmission input shafts 15 and 20 are arranged coaxially and fitted inside and outside. The outer transmission input shaft 20 is supported in the housing 7 via a support bearing 38, and the inner transmission input shaft 15 is supported in the outer hollow shaft 20 via a support portion.

Furthermore, the twin clutch 1 has an operating device 27 formed as a central clutch disengagement mechanism for both the multi-plate clutches K1, K2. The operating device 27 includes a housing 28. The housing 28 is supported on the housing 7 of the transmission via a support spherical surface 29. Dual annular piston type connection mechanism in the present embodiment (hereinafter, referred to as double CSC, CSC is "C oncentric S lave C ylinder (concentric slave cylinder)" refers to that a) is formed as an operating device 27 has two pistons 31 and 32 arranged in an annular shape and concentrically with each other.

  In various embodiments of the operating device 27 shown in FIGS. 1 to 4, both annular pistons 31, 32 slide on each other. Thus, the inner diameter of the piston 31 outside the clutch K1 simultaneously forms a sealing surface for the piston 32 inside the clutch K2. Alternatively, an embodiment in which the pistons 31, 32 are separated from each other by a single annular web or separator capable of sliding the seal member is also possible. Such an alternative embodiment can eliminate the mutual influence exerted on the pistons 31 and 32 by the seal member.

  However, the possible forms of the operating device 27 described above are only a few examples. Instead of the annular piston, a piston with a cross-sectional shape different from the annular ring and / or a plurality of individual pistons distributed along the entire circumference may be provided. Further, instead of the piston / cylinder unit, an electric or electromechanical cutting mechanism may be provided. Furthermore, a mechanical operation device, particularly a lever operation device may be provided.

  In the present embodiment, the piston seal members of the annular pistons 31 and 32 are formed as elastomer seal members. This elastomer seal member is coupled to each piston via a shape-connecting coupling portion. For example, a conical groove provided in the piston can be used as the connecting part. In this groove, the corresponding key of the elastomer seal member or the elastomer seal member itself is coupled. Alternatively, a fitting seal member made of, for example, PTFE is also possible, and an elastomer seal member fixed directly to the piston by elastomer injection molding is also possible.

  The annular pistons 31 and 32 are accommodated by the connection mechanism housing 28. A hole (not shown) provided in the connection mechanism housing 28 serves to operate the pistons 31 and 32 via pressure oil.

  Additionally, the connection mechanism housing 28 undertakes to position the pistons 31 and 32 in the radial direction inside the clutch bell 4, that is, the bell-shaped clutch case 4, via the bearing spherical surface 29.

  Each operation unit of the operation device 27 is coupled to a force transmission device via operation bearings 33 and 34. By this force transmission device, each operation force is transmitted to each of the multi-plate clutches K1, K2. In the present embodiment, each force transmission device has substantially rigid pressing pots 35A and 35B that are in contact with the bearings 33 and 34, respectively. It should be noted here that the pressing pots 35A and 35B have elasticity that causes a certain amount of spring action. However, in relation to the aforementioned operating force of the twin clutch, the pressing pots 35A and 35B can be virtually assumed to be “substantially rigid”. Further, each force transmission device has lever springs 36A and 36B that are in contact with the respective pressing pots 35A and 35B. The lever springs 36A and 36B are attached to friction plate supports provided in the corresponding multi-plate clutches K1 and K2, respectively. The attachment points form pivot points for the lever springs 36A and 36B. The force conversion of the operation force generated by the operation unit is performed by the lever ratio of the lever springs 36A and 36B. Further, each force transmission device has pressing pieces 37A and 37B. The pressing pieces 37A and 37B are in contact with the corresponding lever springs 36A and 36B, and are operatively coupled to the friction plates of the friction plate sets of the multi-plate clutches K1 and K2. The pressing pieces 37A and 37B transmit the operating force to the friction plate set of the multi-plate clutches K1 and K2. The pressing pieces 37 </ b> A and 37 </ b> B are attached to the tooth rows of the input side friction plate supports so as to be movable in the axial direction in a radially outer range, and are centered in the radial direction by the tooth rows. Instead of lever conversion of the operating force, direct operation via the pressure pots 35A and 35B arranged between the operation bearings 33 and 34 and the friction plate set, that is, operation at a lever ratio of 1: 1 is also possible. Is possible.

  A support bearing 30 (also referred to as a cover bearing) is disposed in the outer peripheral surface range of the housing 28 of the operating device 27. The support bearing 30 is coupled to the friction plate support 10 on the input side of the radially outer multi-plate clutch K1 via a tension pot 31. The inner race of the support bearing / cover bearing 30 is provided on the housing 28 via a collar formed on the housing 28, and the outer race of the support bearing / cover bearing 30 is provided on the tension pot 31 on the input side of the multi-plate clutch K1. The operating force returned from the friction plate support 10 is supported so that it can be transmitted to the housing 28. The support bearing 30 for returning the operating force to the connection mechanism housing 28 together with the tension pot 31 is preferably connected to the connection mechanism housing 28 via a bayonet connection.

  During pressurization of one or both pistons, this piston is moved in the direction of the crankshaft (located on the left side of the ZMS output hub 2 in FIG. 1), with the corresponding press pots 35A, Each lever spring 36A, 36B is operated by the interlocking of 35B. The lever springs 36A, 36B further introduce operating force into the friction plate set via the corresponding pressing pieces 37A, 37B. In the clutch K2 arranged radially inward, the operating force is arranged radially outside the input friction plate support 18 and the input side friction plate support of the multi-plate clutch K2 arranged radially inside. Transmission is performed via a coupling piece 17 (also referred to as a coupling metal thin plate) provided between the friction plate support 10 on the input side of the multi-plate clutch K1. The friction plate support 10 on the input side further transmits operating force to the tension pot 31 coupled to the connection mechanism housing 28 via the support bearing 30.

  In the clutch K1 arranged on the radially outer side, the introduced operating force is directly returned to the tension pot 31 via the input friction plate support 10 and eventually returned to the connection mechanism housing 28 via the support bearing 30. It is.

  That is, the double CSC in the present embodiment generates a pressing force that acts on the pressing pots 35A and 35B in the direction of the prime mover, and a correspondingly large reaction force directed in the opposite direction is generated in the housing 28. The operating force is again returned to the housing 28 in the same amount and in the same direction via the tension pot 31 and the support bearing 30. That is, the support bearing 30 transmits the operating force to the connection mechanism housing 28, whereby the internal power flow (force transmission path) is closed inside the clutch 1. The flow of the operating force for operating the multi-plate clutch K2 is schematically shown by the broken line L1 in FIG. That is, in this embodiment, in order to operate the multi-plate clutches K1 and K2, an external force at the time of oil supply in the radial direction becomes unnecessary, or an external force at the time of oil supply in the axial direction is almost equal. It becomes unnecessary. Therefore, the clutch 1 makes it unnecessary to support the operating force for the clutch case 4 or on the engine side.

  The hydraulic medium (operation module) is supplied to the operation device via a pipe joint connected to the clutch case 4.

  The connection mechanism housing 28 has a torque support member inside the clutch case 4 so that bearing friction inside the support bearing 30 does not cause the connection mechanism housing 28 to rotate. As this torque support member, a pipe joint for supplying pressure can be used. Alternatively, a separate support member may be provided for each pin or similar component that engages the bottom of the clutch case when the clutch is assembled.

  In FIG. 3, the radial support portion and the axial support portion of the clutch 1 according to the embodiment shown in FIG. 1 are schematically shown by arrows P1 to P5.

  When viewed in the radial direction, all the components of the twin clutch 1 that rotate at the engine speed are supported on the connection mechanism housing 28 on the transmission side and on the solid shaft 15 on the engine side. An arrow P1 indicates a support point of the friction plate support 10 on the input side of the multi-plate clutch K1 disposed on the radially outer side with respect to the connection mechanism housing 28, and a component member coupled to this component member. The connection mechanism housing 28 is further supported on the case bottom (transmission housing) via the bearing spherical surface 29 as indicated by the arrow P2. The bearing spherical surface 29 forms an angle compensation portion between the solid shaft 15 and the bearing base portion on the transmission side. The solid shaft 15 supports the friction plate support 10 on the input side of the clutch K1 disposed on the radially outer side via the bearing 16 on the engine side, as indicated by the arrow P3. Clutch components 14 and 19 that are rotated by solid shaft 15 and hollow shaft 20 at each transmission input speed are supported radially via a hub / hub range mounted on the shaft.

  Instead of the bearing spherical surface 29, radial support for the outer transmission input shaft may be utilized, preferably by radial needle roller bearings arranged on the outer transmission input shaft.

  The clutch 1 is supported by the clutch cover 3 when viewed in the axial direction. The supporting force is applied by the wave spring 21. Axial bearing points are indicated by arrows P4 and P5. The wave spring 21 is supported by a position fixing ring attached to the hollow shaft 20 and a hub of the friction plate support 19 on the output side of the multi-plate clutch K2. The friction plate support 19 on the output side of the multi-plate clutch K <b> 2 is thrust in the axial range of the friction plate support 13 on the output side or the hub range 14 of the friction plate support 13 on the output side via the spacer disk 22. Guide to needle roller bearing 23. The friction plate support 13 on the output side of the multi-plate clutch K1 is further supported by the friction plate support 10 on the input side of the clutch K1 via a thrust needle roller bearing 24. The input friction plate support 10 is supported by the clutch cover 3 via another needle roller bearing 25. As a result, the clutch system 1 is always positioned on the clutch cover 3. An axial vibration and an error can be compensated via the wave spring 21. Instead of the thrust needle roller bearings 23, 24, 25, a thrust washer may be used. The above-described form of the thrust bearing of the clutch 1 according to the present embodiment is not related to the above-described closed power flow, that is, it may be used in another form of operating force transmission path. It constitutes a separately usable solution for twin (wet) clutches.

  FIG. 4 shows another embodiment of the multi-clutch device according to the present invention. This embodiment completely corresponds to the above-described embodiment with respect to the idea of the operating force transmission path. Accordingly, all the above-described features relating to the operating device in the embodiment shown in FIGS. 1 to 3 and the embodiment shown in FIG. 4 match each other. Furthermore, in this embodiment as well, a bearing spherical surface 29 is also provided, whereby the operating housing 28 is supported radially on the transmission housing 7 and the axial offset is compensated. However, the embodiment shown in FIG. 4 differs from the previously described embodiment in terms of the elements used to dampen the rotational irregularities coming from the internal combustion engine, ie ZMS and / or centrifugal pendulum. Therefore, according to the embodiment shown in FIG. 4, not only the ZMS 39 but also the centrifugal pendulum 40 is arranged in the clutch case 4, that is, in the wet chamber itself. This wet chamber is partitioned from the dry chamber 5 by a clutch cover 41. In this embodiment, the clutch cover 41 is not provided for thrust-supporting the clutch. Rather, the clutch cover 41 constitutes a separating member between the wet chamber 4 and the dry chamber 5 exclusively by the sealing devices 6 and 8.

  The ZMS 39 has a ZMS metal sheet 42 on the primary side. In this embodiment, the ZMS thin metal plate 42 is formed in a pot shape, and has a pilot pin 43 in the radially inner range. The pilot pin 43 engages in the recess 44 of the crankshaft 45 and centers the ZMS metal thin plate 42 on the primary side. This primary side ZMS metal thin plate 42 has a pocket-like region in the radially outer region. Within this range, spring elements are accommodated. The end region of the energy storage 46 that does not contact the pocket is operatively coupled to the secondary ZMS flange 47. The secondary side ZMS flange 47 is coupled to a substantially cylindrical metal sheet 48 with a tooth row via a rivet 49. The metal thin plate with teeth row 48 serves as a friction plate support on the input side of the clutch K1 disposed on the radially outer side.

  The input-side friction plate support 48 is coupled to the input-side friction plate support 51 of the multi-plate clutch K <b> 2 disposed on the radially inner side via a coupling metal thin plate 50. Further, the thin metal plate 50 is coupled to the centrifugal pendulum 40 (in this embodiment, integrally formed), whereby the ZMS 39 and the centrifugal pendulum 40 are combined together into the toothed metal thin plate 48 (advantageously. Via rivets 49) and correspondingly connected in parallel.

  The metal thin plate with teeth row 48 is coupled to a support bearing 53 via a tension pot 52. This support bearing 53 is arranged in the connection mechanism housing 28 (as already described above).

  The friction plate support 54 on the output side of the multi-plate clutch K1 is disposed on the solid shaft 15 so as not to be relatively rotatable. The friction plate support 55 on the output side of the multi-plate clutch K2 is disposed on the hollow shaft 20 so as not to be relatively rotatable. The friction plate support 55 on the output side of the multi-plate clutch K2 is coupled with the position fixing element 21A and the coupling element 22 via the wave spring 21 through the thrust bearings on the output side friction plate support. A preload is applied toward 54. A load is applied to the primary side ZMS flange 42 (also referred to as a “ZMS metal thin plate”) on the output side friction plate support 54 of the multi-plate clutch K1 under the intervention of another thrust bearing. A drive plate 56 is fixedly disposed on the primary ZMS metal thin plate 42. The drive plate 56 is coupled to the flexible plate 58 via a screw fastening member 57. The flexible plate 58 is coupled to the crankshaft 45 via another screw fastening member 59.

  The operation device 27 also has an operation unit. In this embodiment, this operating unit is formed as a piston / cylinder unit. As already described above, this piston / cylinder unit acts on each friction plate set of the multi-plate clutches K1, K2 via a force transmission device comprising a pressing pot, a lever spring, and a pressing piece.

  That is, the clutch 100 shown in FIG. 4 is coupled to the internal combustion engine via the flexible plate 58. The drive plate 56 and the primary ZMS sheet metal 42 are directly (preferably oil-tight) coupled to each other, and are interposed between the drive plate 56 and the primary ZMS sheet metal 42 in the axial direction. The mounted clutch cover 41 is accommodated together with the rotary shaft seal 8.

  The components on the primary side of the ZMS 39 are directly supported on the crankshaft 45 via the pilot pins 43.

  In this embodiment, the secondary side flange 47 of the ZMS 39 simultaneously forms an end friction plate of the multi-plate clutch K1.

  The friction plate support 48 on the input side of the multi-plate clutch K1 is formed as a variation that is riveted (as already mentioned).

  An embodiment of this riveted friction plate support is shown in FIGS.

  FIG. 5 shows in detail a sectional view of the prefabricated friction plate support 134 (corresponding to the input side friction plate support of FIG. 4). The friction plate support 134 is formed by a flange member 113a, a support disk 136, and coupling elements 190 distributed between the flange member 113a and the support disk 136 in the axial direction and distributed over the entire circumference. . In the illustrated embodiment, the coupling element 190 is formed from a thin metal plate member 191 that has been bent in advance. The thin metal plate member 191 has a plurality of rivet pins 192 and 193 extending in the axial direction. These rivet pins 192 and 193 are guided through corresponding openings 194 and 195 provided in the flange member 113a or the support disk 136, and are riveted to the flange member 113a or the support disk 136 on the outside. The circumferentially oriented end of the sheet metal member 191 is chamfered or bent radially inward to form a toothed side 196, thereby crossing the sheet metal member 191. When viewed from the surface, the tooth side profile is formed. A friction plate 138 is attached to the tooth side profile deformed portion. For this purpose, the friction plate 138 has a complementary outer profile 197, whereby the friction plate 138 is centered with respect to the friction plate support 134. The applied torque is transmitted to the friction plate 138. The friction plates 138 are alternately laminated with friction plates 140 that are attached to the friction plate support 142 on the outlet side so as to be movable while being restricted in the axial direction, although they cannot rotate relative to each other.

  FIG. 6 shows an assembly-type friction plate support 135a formed alternatively to the above-described friction plate support. The friction plate support 135a has a coupling element 198 formed corresponding to the coupling element 190 of FIG. The coupling element 198 is riveted between the end friction plate 172a and the support disk 136. In addition, FIG. 6 shows a coupling element 190a with a pin 186 extending in the axial direction. The coupling element 190a is used, for example, in place of the coupling element 190 of FIG. 5 at a plurality of circumferential positions, and the pin 186 entrains the friction ring 187 in the circumferential direction with respect to the housing of the clutch unit. By controlling 185, the friction plate support 134 can act on the friction device 185.

  According to the embodiment shown in FIG. 4, the individual toothed metal sheets have two different lengths and are distributed alternately over the entire circumference. The shorter metal sheet with teeth is riveted to the combined metal sheet 50 of the friction plate supports 48 and 51 on the input side of the multi-plate clutches K1 and K2. The longer sheet metal sheet with teeth is connected to a tension pot 52 that returns the operating force to the connection mechanism housing 28. By this stepped metal sheet with teeth, the centrifugal pendulum is coupled to the secondary side flange of the ZMS without rotational play. Thus, the tension pot 52 is coupled to the friction plate support 48 on the input side of the multi-plate clutch K1 so as to transmit the force in a shape-connected manner, and the generated operation force can be received.

  In FIG. 7, it is operated via a double annular piston-type connection mechanism as a CSC that is stationary with respect to the housing, integrated into the clutch via a cover bearing, to form an internally closed power flow. A wet twin clutch is shown. The basic structure corresponds to the embodiment shown in FIG. As described in more detail below, the piston of the connection mechanism of the double annular piston type introduces the connection force to the friction plate sets of the multi-plate clutches K1 and K2 via the adjusting disk in this embodiment. In the inner clutch K2, the operating force is transmitted to the outer friction plate support of the outer clutch through the outer friction plate support (= input friction plate support) and the intermediate web (= coupled metal thin plate 214). From there, the force is returned to the cover bearing 221 via the position fixing ring 229 and the clutch cover 220 (= tensile pot). This cover bearing 221 returns the force to the CSC via the position fixing ring 230 and thus closes the power flow. In the outer clutch K1, after the friction plate set, the force is provided between the outer friction plate support 211, the position fixing ring 229, the clutch cover 220, the cover bearing 221, and the cover bearing 221 and the CSC housing. It returns via the fixed position fixing ring 230. Therefore, no force is introduced into the periphery during operation.

  FIG. 7 shows a rear side of a prime mover (in this embodiment, an internal combustion engine with a crankshaft) having an input shaft 200 (not shown) of a power train used for an automobile, for example, a passenger car or a truck. The part is shown in detail. The input shaft 200 is coupled to the input side member 201 of the ZMS. The input side member 201 supports a startering gear 202. Further, in the radially outer range of the input side member 201, an accommodation range 203 that is substantially closed with respect to the spring element 204 (arc spring in a general form) is provided. A ZMS output member 205 is engaged in the arc spring 204. The ZMS output member 205 is riveted to the additional punch mass body 206. The ZMS output member 205 is coupled to the flange area 207 radially inward. The flange range 207 has a tooth row radially inward. This tooth row meshes with a tooth row located radially outward of the clutch hub 208. A tooth row between a flange 207 provided on the output side of the ZMS and a clutch hub 208 as an input side member of a wet twin clutch, which will be described in more detail below, is a ZMS (engine) And a separation plane between the wet twin clutch (transmission assembly) coupled to the transmission. The separation plane is set with the possibility of movement in the axial direction at the same time as the non-rotatable coupling. The clutch hub 208 is formed with a bearing seat for the radial bearing 209 (in this embodiment, a needle roller bearing sleeve) radially inward. The clutch hub 208 is axially supported on the inner transmission input shaft 210 via a bearing 209. The bearing outer ring of the bearing 209 is fixedly attached to the clutch hub 208, and the rolling elements roll directly on the corresponding peripheral surface of the transmission input shaft 210.

  The clutch hub 208 is rigidly coupled in the axial direction to the input friction plate support 211 of the multi-plate clutch K1 disposed radially outward in the inner and outer fittings in the radial direction (in this embodiment, in a relatively non-rotatable manner) Welding). A sleeve-like component 212 is additionally sandwiched between the input friction plate support 211 and the clutch hub 208. This structural member 212 provides a running surface for the rotary shaft seal ring that seals the seal portion between the clutch cover 213 and the ZMS output flange 207.

  The outer input friction plate support 211 is coupled to the input friction plate support 215 inside the clutch K2 disposed radially inward in the inner and outer fittings through the coupling metal thin plate 214. Each coupling between the two input friction plate supports 211, 215 and the coupling metal sheet 214 corresponds to the coupling already described above.

  The output friction plate support 216 of the outer multi-plate clutch K1 is axially connected to the inner transmission input shaft 210 through the axial insertion teeth formed in the flange range, although it is not relatively rotatable. It is movably connected.

  Similarly, the output friction plate support 217 of the multi-plate clutch K2 arranged on the radially inner side cannot be rotated relative to the outer transmission input shaft 218 via the axial insertion teeth formed in the flange range. These are connected so as to be movable in the axial direction. In this embodiment, the associated tooth row is formed in the hub range welded to the output friction plate support 217 of the clutch K2. In addition, the hub range has a convex portion or a concave portion that forms the flow path 217a, so that the cooling oil passes between the output friction plate supports of the multi-plate clutches K1 and K2. It comes to flow.

  In addition, a spring element, for example a wave spring 219, is arranged between the hub range 217 and the hollow shaft 218, so that the hub range / output friction plate support of the multi-plate clutch K2 and one thrust bearing. Is applied to the output friction plate support of the multi-plate clutch K1 and the clutch hub 208 via another thrust bearing. Further, the clutch hub 208 is supported in the axial direction on the housing 222 of the CSC in combination with the cover bearing 221 via the input friction plate support 211 of the multi-plate clutch K1 and the tension pot 220. . The CSC housing 222 is fastened to the bottom 224 of a bell-shaped clutch case via a substantially rigid component 223 formed in a pot shape. The component member 223 functions like a clamping jaw or a thin metal plate jaw for chucking a workpiece in a processing machine. Alternatively, a preload may be elastically applied to the component member 223 formed in a pot shape. The component 223 corresponding to the clamping jaw / sheet metal jaw serves to clamp the oil supply 225 which continues to guide the oil to the CSC and to the piston / cylinder unit provided therein.

  The piston / cylinder unit provided in the CSC is coupled to substantially rigid pressing pots 226 and 227 via operation bearings. When appropriate pressure is applied to the piston / cylinder unit, the pressing pots 226 and 227 act on the friction plate sets of the multi-plate clutches K1 and K2 at a lever ratio of 1: 1.

  Adjustment disks 228 and 229 for adjusting the gaps of the friction plate sets of the multi-plate clutches K1 and K2 are provided between the substantially rigid pressing pots 226 and 227 and the operation bearing. As shown in the example of the press pot 227 of the multi-plate clutch K2 arranged on the radially inner side, a tongue piece can be formed from the press pot, whereby the adjustment disc is positioned in the radial direction.

  The radial guide of the pressing pot 227 of the multi-plate clutch K2 is performed through a neck region formed on the combined metal thin plate 214. This neck range is formed corresponding to the cylindrical range of the pressing pot 227.

  Further, the combined metal thin plate 214 has a tongue piece. The tongue piece supports a return spring that applies a load to the pressing pot 227 in the cutting direction of the multi-plate clutch.

  The radial guide of the pressing pot 226 of the multi-plate clutch K1 is performed through a cylindrical range formed in the tension pot 220. A return spring for applying a preload to the pressing pot 226 in the cutting direction is supported between one end face of the neck region formed on the thin metal plate 214.

  In summary, as can be appreciated with respect to the embodiment shown in FIG. 7, the CSC forms a unit that can be assembled with the clutch. The clutch / CSC system unit is axially fixed to the case bottom of the clutch case via a thin metal plate jaw. A preload is applied to the thin metal plate jaws in the axial direction during assembly. In addition, the thin metal plate jaws absorb the force and moment introduced from the clutch to the CSC through the cover bearing during operation. In addition, the sheet metal jaws support the pressing force introduced into the CSC in the axial direction at the oil delivery section.

  The clutch / CSC system unit is supported on the bottom of the case in the radial direction via a centering collar provided on the CSC. The force supported via the centering collar is introduced into the CSC housing via the cover bearing. On the opposite side, the clutch is supported on the inner transmission input shaft via a radial bearing formed as a movable bearing.

  In order to adjust the air gap, in this embodiment, the distance between the contact surface of the position fixing ring provided on the clutch cover and the contact surface of the adjustment disk provided on the connection mechanism bearing is measured. . In addition, there is a gap between the contact surface of the position fixing ring provided in the groove provided in the outer friction plate support of the outer clutch and the contact surface of the adjustment disk provided in the pressing pot. Measured. The difference obtained by subtracting the required gap in the friction plate set from this measured amount is the thickness of the adjustment disk required.

  FIG. 8 shows an embodiment of a wet twin clutch that is stationary with respect to the transmission shaft and compensates for axial play in the oil supply.

  The embodiment of the wet twin clutch shown in FIG. 8 is a ZMS having an input side member 201, an arc spring 204, an output side member 205, a connecting portion of an additional mass body 206 and a flange range 207. Regarding the configuration, the wet twin clutch, the operation of the wet twin clutch, the main features of the transmission input shaft, and the case bottom also correspond to the embodiment already described in conjunction with FIG. Yes.

  However, the ZMS flange range 207 'having an inner tooth row coupled to the outer tooth row provided on the clutch hub 208' of the wet twin clutch is made shorter in the axial direction. This is because the rotary shaft seal ring provided on the cover 213 is in direct contact with the outer peripheral surface of the clutch hub 208 ′ and seals the wet chamber against the dry chamber.

  Further, the structure shown in FIG. 8 is different from the structure shown in FIG. 7 in terms of the idea of support. This is because the clutch hub 208 'is supported on the inner transmission input shaft 210' via the fixed bearing 209 'both in the radial direction and in the axial direction. In order to assemble the fixed bearing 209 ', the clutch hub 208' has a clutch hub cover 208 ". A bearing outer ring of the fixed bearing 209 ′ is sandwiched between the cover 208 ″ and the clutch hub 208 ′. The inner ring of the bearing 209 'is fixed between a shaft shoulder provided on the shaft 210' and a position fixing ring. The input friction plate support 211 of the outer multi-plate clutch K1 is coupled to the clutch hub 208 'in accordance with the embodiment shown in FIG. Corresponding to the embodiment of FIG. 7, the tension pot 220 is also coupled to the CSC housing 222 via the cover bearing 221.

  The configuration of the piston / cylinder unit provided in the CSC and the configuration of the operation bearing, the adjustment disk, and the operation pot correspond to those described in conjunction with FIG.

  Further, the axial support of the wet clutch using the wave spring and the two thrust bearings for the clutch hub 208 'is formed in accordance with that described in conjunction with FIG.

  However, in this embodiment, a flexible thin metal plate 300 (hereinafter referred to as a “flexible plate”) is provided in place of the structural member 223 acting as a clamping jaw / thin metal plate jaw. The flexible plate 300 acts as a “soft” torque support member both in the axial direction and in the radial direction. Further, the CSC housing 222 is connected to an oil supply path provided in the transmission housing via a plurality of pipes 301 (at least one pipe per piston / cylinder unit). The length of the tube is dimensioned to allow axial movement of the CSC housing 222. Correspondingly, the flexible plate never transmits force in the axial direction.

  A radial bearing 302 is provided between the CSC housing 222 and the outer transmission input shaft 218 for radial support of the system unit comprising the clutch and the CSC.

  In summary, as can be appreciated with respect to the embodiment shown in FIG. 8, the clutch / CSC system unit is axially positioned on the inner transmission input shaft via a fixed bearing. In order to be able to assemble the position fixing ring to the fixed bearing, the clutch further has a hub cover. The hub cover fixes the position of the fixed bearing to the clutch and separates the wet chamber from the dry chamber. Furthermore, pressure oil is supplied to the CSC via a plurality of tubes extending in the horizontal direction. These tubes (one tube per partial clutch) are sealed on both sides to the CSC and bell-shaped clutch case via a seal member. The tube has play in the axial direction, which makes it possible to compensate for axial shaft / clutch movement. In this embodiment, the flexible plate is soft in the axial direction and follows the movement of the clutch. In the circumferential direction, the flexible plate is rigidly formed and supports the frictional moment of the connection mechanism bearing on the case bottom. In this embodiment, the flexible plate does not necessarily have to be formed as a rotationally symmetric component, and may be formed as a thin metal plate tongue piece that is screwed to the CSC and the case bottom.

  As described above, the clutch is supported on the inner transmission input shaft via the fixed bearing in the radial direction, and is provided between the cover bearing on the opposite side, the outer transmission input shaft, and the CSC housing. It is supported via a needle roller bearing.

  FIG. 9 shows an embodiment of a wet twin clutch floatingly supported in the axial direction with a radial oil supply.

  The embodiment shown in FIG. 9 matches the embodiment shown in FIG. 8 in many aspects. Therefore, only the difference between the clutch unit shown in FIG. 8 and the clutch unit shown in FIG. 9 will be described below. The range from the crankshaft 200 to the clutch hub 208 'is the same in the embodiment shown in FIG. 8 and the embodiment shown in FIG. The first main difference is that the bearing between the clutch hub 208 ′ and the transmission input shaft 210 ″ located inside is formed as an axially movable bearing. This is because the bearing outer ring of the bearing 400 is securely fastened between the clutch hub cover 208 ″ and the clutch hub 208 ′, but the bearing inner ring of the bearing 400 is positioned on the transmission input shaft 210 ″. It is because it is not fixed.

  Furthermore, the embodiment of FIGS. 8 and 9 is consistent in that a flexible plate 300 is provided that couples the CSC housing 222 to the case bottom 224. However, in this embodiment, different oil supply portions extending in the radial direction are provided between the oil guide portion on the transmission side and the CSC via the pipelines 401 and 402 arranged in the radial direction. In the radial direction, the CSC housing 222 is supported by the outer transmission input shaft 218 via the radial needle roller bearing 302 again.

  In summary, in the embodiment shown in FIG. 9, the clutch / CSC system unit is supported on the inner transmission input shaft in the radial direction via a movable bearing. On the opposite side, the clutch is supported in the radial direction via a cover bearing and a needle roller bearing provided between the outer transmission input shaft and the CSC housing. Furthermore, the wet twin clutch according to this embodiment is suspended in a floating manner in the axial direction between the flexible plate 300 and the springs 403 and 404 that are necessary for generating the basic friction in the dual mass flywheel. Furthermore, the hydraulic oil is supplied to the clutch via two conduits in the radial direction. Both pipes are formed so as to be able to absorb the axial movement of the clutch. Each pipe line is composed of, for example, two divided pipes. The pipe piece located in the CSC housing is assembled together with the system unit, and then the second split pipe is introduced through the opening provided in the bell-shaped clutch case and connected to the first split pipe. The connecting portions of the pipe pieces are sealed with each other and formed so as to be able to absorb the pressing force acting in the longitudinal direction of the pipe (not shown). In order to separate the wet chamber from the dry chamber, in this embodiment, an additional seal member is located between the opening of the clutch case and the second divided pipe.

  FIG. 10 shows another twin clutch embodiment that is axially floated with flexible plate bearings.

  The embodiment shown in FIG. 10 includes a wet twin clutch provided with a clutch hub 208 supported on an inner transmission input shaft 210 via a movable bearing 209 as already described in conjunction with FIG. Have. Furthermore, the embodiment shown in FIG. 10 has a coupling flange 207 with the output side member 205 of the ZMS. The coupling flange 207 corresponds to the coupling flange described with reference to FIG. Further, a sleeve-like component 212 which is also described with reference to FIG. 7 is provided. Further, the features of the clutch cover 213 and the wet twin clutch, particularly the axial support via the wave springs 219 coupled to the thrust needle roller bearings for the clutch hub 208 are also operated via the pressure pots 226 and 227. This also corresponds to that described in conjunction with FIG. This is because, in particular, the radial support member is not provided between the CSC housing 222 and the outer transmission shaft 218 in both the embodiment shown in FIG. 7 and the embodiment shown in FIG. Is also accepted.

  However, the embodiment shown in FIG. 7 and the embodiment shown in FIG. 10 are different from each other in the embodiment shown in FIG. 7 in that the CSC housing is provided with the axially attached portion 228. While the CSC housing 222 is supported by the clutch case 224 in the radial direction at 228, the embodiment shown in FIG. 10 is provided with a flexible plate 500 that couples the CSC housing 222 to the case bottom 224. It is different in point. The joint between the flexible plate 500 and the bottom of the case is located radially outside the wet twin clutch diameter to facilitate proper assembly.

  Corresponding to the embodiment shown in FIG. 9, in order to supply the hydraulic medium to the CSC, an oil supply unit through a plurality of pipes 501 and 502 is provided. A pipe 501 on the transmission housing side is screwed to the transmission housing. Further, the tube 502 on the CSC side is fixed to the CSC housing 222 through screw fastening. The tubes 501 and 502 are relatively movable in the axial direction and are relatively sealed. Both tubes 501 and 502 are extended substantially in the radial direction.

  In summary, in the embodiment shown in FIG. 10, the clutch / CSC system unit is supported in the radial direction on the inner transmission input shaft via the movable bearing on the engine side. On the opposite side (transmission side), the clutch is supported in the clutch case in the radial direction via the cover bearing and the flexible plate. The oil guide member on the CSC side is coupled to the CSC via screw fastening and sealed. The second guide piece (transmission housing side) is screwed to the clutch case on the outside via a flange and sealed via an O-ring. Even in this embodiment, the oil supply section is formed so as to be soft in the axial direction, thereby absorbing the axial movement of the clutch. Further, as already described in conjunction with FIG. 9, the system unit floats between the flexible plate and the spring provided on the dual mass flywheel.

  FIG. 11 shows another twin clutch embodiment that is axially floated with flexible plate bearings. In addition to the axial floating bearing and the flexible plate bearing, the bearing is effected via a pilot provided between the crankshaft and the clutch. All the configurations of the embodiment shown in FIG. 11 are the same as the configurations shown in FIG. In the embodiment of FIG. 11, a pilot 600 formed as an extension of the clutch hub 208 is provided. A movable bearing (for example, a radial needle roller bearing) is disposed between the pilot 600 and the crankshaft 200.

  FIG. 12 shows another wet twin clutch embodiment with dry ZMS.

  According to the embodiment shown in FIG. 12, a ZMS having an arc-shaped spring located on the radially outer side and an arc-shaped spring disposed on the radially inner side is shown. This ZMS can be used particularly in an internal combustion engine having significantly noticeable rotational irregularities. However, as a matter of course, the ZMS is not limitedly formed with respect to the configuration of the twin clutch and the coupling portion between the ZMS and the twin clutch, or the operation device of the twin clutch. Rather, it is only important that a ZMS and another torsional vibration damping system including an input side member 201 and an output side member 205 'are provided between the crankshaft 200 and the wet twin clutch. An output flange 207 ″ is coupled to an input hub 700 that generally corresponds to the embodiment shown in FIG. The configuration of the input friction plate support 701 also corresponds to the input friction plate support 13 described in conjunction with FIG. Further, the input hub 700 and the input friction plate support of the clutch K1 coupled to the input hub 700 are connected to the transmission input shaft 703 on the inner side via the radial bearing 702 corresponding to the radial bearing 16 shown in FIG. Is supported in the radial direction. A wet chamber 704 containing a wet twin clutch is supported by the case bottom 705 and the clutch cover 706. A rotary shaft seal ring is provided between the clutch cover 706 and the input hub 700. The rotating shaft seal ring rotates on a rotating surface 707 provided on the outer peripheral surface of the clutch hub. The rotating surface 707 is disposed radially following the axial insertion row between the ZMS output flange 707 ″ and the clutch hub 700.

  The output friction plate support 708 of the outer multi-plate clutch K1 and the corresponding output flange are formed so as to substantially correspond to the output friction plate support 13 and the output flange 14 in the embodiment shown in FIG. Has been. Further, the input friction plate support of the multi-plate clutch K2 disposed on the radially inner side is also formed substantially corresponding to the input friction plate support 18 of the multi-plate clutch K2. In the embodiment shown in FIG. 12, a combined metal thin plate 709 formed differently than the combined metal thin plate 17 shown in FIG. 1 is provided between the input friction plate supports of both the multi-plate clutches K1, K2. used. The bonded metal thin plate 709 is formed substantially flat and has a tongue piece 709a extruded from the bonded metal thin plate 709. The tongue piece 709a is used as a support finger for the return spring 710 of the pressing pot 711 of the multi-plate clutch K2 on the radially inner side. Furthermore, in the embodiment shown in FIGS. 7 and 8, the combined thin metal plate 214 has a cylindrical neck range used as a guide for the pressing pot of the clutch K <b> 2. In the embodiment shown in FIG. 12, this cylindrical neck area has been removed. Guide is provided through a cylindrical end face region of a substantially flat bonded sheet metal. In the embodiment shown in FIGS. 7 and 8, the cylindrical neck region was also used as a support location for the return spring of the pressing pot of the outer clutch K1. Instead of this cylindrical neck area, an annular element 712 is provided. The annular element 712 is supported by the thin metal plate 709 and is centered in the radial direction on the input friction plate support of the inner clutch K2 via the position fixing ring 713. In addition to the cylindrical range, It has a range extending in the radial direction. In this range, the return spring 713 of the pressing pot 714 of the outer clutch K1 is supported. A circular wire spring element is disposed between the return spring 713 and the press pot 714 or between the return spring 710 and the press pot 711 of the clutches K1 and K2. The circular wire spring element supports each end face range of the spring.

  Corresponding to the embodiment shown in FIG. 7, the CSC housing 715 is centered radially on the case bottom 705 via an axially extending attachment 715a, corresponding to a clamping jaw / sheet metal jaw. It is fastened in the axial direction to the bottom of the case by the functioning member 716 functioning as described above.

  The cover bearing 717 is attached to the CSC housing 715 in the axial direction along with a slope formed on the bearing inner ring via a circular wire tightening ring, thereby forming a power flow inside the operation force. be able to. In the embodiment shown in FIG. 7, a snap ring with a square cross section is used for the CSC housing.

  There is no additional radial bearing between the CSC housing 715 and the hollow shaft 718.

  In summary, the configuration shown in FIG. 12 has the following characteristics.

  1. In the torque flow, the first play location is located behind the friction plate set of the outer clutch K1. Since this play location is located behind the friction system, there is no rattling noise during operation here.

  2. A return pressing spring is supported via an open circular wire ring or a closed circular wire ring. As a result, the rolling characteristics of the spring during operation of the clutch become better. This reduces the basic hysteresis of the operating system.

  3. The return pressing spring of the outer clutch K1 is supported by a ring formed over the entire circumference formed in the tension pot. This ring is centered via a fixed ring on the outer friction plate support of the inner clutch.

  4). A plurality of fingers are located in the inner diameter region in the thin metal sheet or web that couples the input friction plate supports of both clutches to each other. These fingers support a return pressing spring of an inner clutch.

  5. To center the thrust needle roller bearing (alternatively a sliding disc), (at least three) protrusions are extruded from a sheet metal.

  6). A cover bearing centered on the CSC via a bearing inner ring of the clutch supports the operating force generated in the axial direction via a snap ring provided on the CSC. The snap ring may have a square or circular cross section. When a circular wire snap ring is used, a slight stress peak occurs in CSC than when a square snap ring is used.

  7). The CSC annular piston has play (excluding the piston seal member) with respect to the CSC housing, and the ratio of the piston guide length to the piston inner diameter is set to be less than 0.5. This not only allows the piston to move axially within the housing but also allows it to tilt, so that the piston assumes the cardan function. When the clutch is tilted with respect to the CSC due to errors and dynamic effects during operation, the piston of the CSC compensates for or follows this tilt.

  8). Cooling oil is supplied to the clutch between the outer friction plate supports of the clutch. This oil flows through a pressing piece having a radially extending groove. The oil then flows through an opening in the inner friction plate support of the inner clutch and then reaches the pressure chamber of the inner clutch.

  9. The input friction plate support of the outer clutch and the output friction plate support of both partial clutches are spaced apart from each other via a thrust needle roller bearing (or a thrust washer or a sliding disk). When using needle roller bearings, a minimum axial preload must be generated for unobstructed operation. This minimum preload is generated via a wave spring or compression spring which is located and supported between the hub of the inner clutch and the position fixing ring or step of the outer transmission input shaft. Unlike the configuration shown in FIG. 12, the preload spring may be located on the inner diameter portion of the hub as shown in FIG.

  10. A thrust bearing for spacing the output friction plate support is supported through a step integrated into the outer clutch hub.

  11. Hereinafter, as shown and described in conjunction with FIG. 13, the preload of the wave spring can also be received via the clutch cover bearing, so that the outer friction plate support of the outer clutch K1 (wet chamber) A thrust bearing with the clutch cover (separate) is functionally unnecessary.

  FIG. 13 shows another wet twin clutch embodiment with dry ZMS. In this embodiment, the thrust bearing between the outer friction plate support of the outer clutch K1 and the clutch cover is omitted. This is because the thrust bearing is functionally unnecessary as described above. In other respects, the embodiments shown in FIGS. 12 and 13 are consistent with each other.

  FIG. 14 shows another wet twin clutch embodiment with an internally closed power flow, wet ZMS, and a centrifugal pendulum (“FKP”). This embodiment is very well consistent with the embodiment shown in FIGS. 4-6, so the following description will be limited only to the differences from these embodiments.

  The embodiment shown in FIG. 14 has a CSC housing 800. The CSC housing 800 has an attachment portion 801 in the axial direction. The CSC housing 800 is centered in the radial direction on the case bottom 802 via the attachment portion 801. No other radial support point is provided between the CSC housing 800 and the transmission input shaft 803. In the axial direction, the CSC housing 800 is axially clamped to the case bottom 802 via an element 804 (having a screw fastening member 805 located radially outward) corresponding to the clamping jaws / sheet metal jaws. On the outer peripheral surface of the CSC housing 800, a snap ring 806 having a circular cross section is provided. The snap ring 806 serves as a contact surface for the bearing inner ring of the cover bearing 807. The cover bearing 807 is coupled to the input friction plate support of the clutch K1 via a tension pot 808. This input friction plate support is coupled to the input friction plate support of the clutch K2 via a coupling metal thin plate. The clutches K1, K2 are operated at a 1: 1 lever ratio via a substantially rigid pressing pot. An operation bearing and an adjustment disk are arranged between the pressing pot and the piston / cylinder unit of the CSC. The characteristics of the input friction plate support and the output friction plate support of the clutches K1 and K2, and the characteristics of the operation pot, the adjustment disk, and the operation bearing correspond to those described in conjunction with FIG.

  However, the output friction plate support 809 of the multi-plate clutch located on the radially inner side is different in structure from the output friction plate support 45 of the clutch K2 shown in FIG. 4 as described below.

  The output friction plate support 809 has a radially extended portion as a coupling portion with the coupling flange 810 in addition to a cylindrical portion having an axial insertion dentition for mounting individual friction plates. have. This part couples the output flange 809 to the hollow transmission input shaft 803 via an axial insertion row. In the embodiment shown in FIG. 14, the radially extended range is arranged on the engine side of the friction plate set. On the other hand, in the embodiment shown in FIG. 4, the range extended in the radial direction is arranged on the transmission side of the friction plate set. Further, the output friction plate support 809 has a through hole 811 through which cooling oil can flow through the friction plate set of the clutch K2. In order to be able to guide the cooling oil flow with its direction adjusted, a thin metal plate 812 disposed between the coupling flange 810 and the cylindrical portion of the output friction plate support 809 is provided. .

  Other features of this embodiment are described in the description of FIGS.

  FIG. 15 shows another wet twin clutch embodiment with internally closed power flow, wet ZMS, and centrifugal pendulum (“FKP”). In this embodiment, the thin metal plate jaws or tightening jaws 804 shown in FIG. 14 are omitted. The preload for sealing the joint between the CSC housing and the case bottom is, for example, provided on the ZMS and / or provided on a prefabricated friction plate support and / or on the crankshaft and the ZMS / clutch input It can also be achieved by an appropriate selection of preloads in the axially acting friction spring provided on the sheet metal bonded to the side member.

  The present invention has been described above exclusively with respect to multi-clutch devices. It is suggested here that the present invention, in particular the use of a component unit consisting of a clutch and an operating device and a clamping jaw / sheet metal jaw, can also be used in connection with a single clutch.

DESCRIPTION OF SYMBOLS 1 Twin clutch 2 Output hub 3 Clutch cover 4 Wet chamber or bell-shaped clutch case 5 Dry chamber 6 O-ring 7 Transmission housing 8 Rotating shaft seal ring 9 Clutch hub 10 Input side friction plate support 11 Input side friction Plate 12 Output friction plate 13 Output friction plate support 14 Hub 15 First transmission input shaft 16 Radial bearing 17 Thin metal plate 18 Input friction plate support 19 Output friction plate support 20 2 Transmission input shaft 21 Wave spring 21A Position fixing element 22 Coupling piece 23 Thrust bearing 24 Thrust bearing 25 Thrust bearing 26 Position fixing element 27 Operating device 28 Housing 29 Bearing spherical surface 30 Support bearing 31 Piston or tension pot 32 Piston 33 Operation bearing 34 Operation bearing 35A, 35B Press pot 36A, 36B Insulator spring 37A, 37B Press piece 38 Support bearing 39 ZMS
40 Centrifugal pendulum 41 Clutch cover 42 ZMS metal thin plate 43 Pilot pin 44 Recess 45 Crankshaft 46 Energy store 47 ZMS flange 48 Input side friction plate support 49 Rivet 50 Bonded metal thin plate 51 Input side friction plate support 52 Tensile pot 53 Support Bearing 54 Output Side Friction Plate Support 55 Output Side Friction Plate Support 56 Drive Plate 57 Screw Fastening Member 58 Flexible Plate 59 Screw Fastening Member 100 Clutch 113a Flange Member 134 Friction Plate Support 135a Friction Plate Support 136 Support Disc 138 Friction plate 140 Friction plate 142 Friction plate support 172a End friction plate 185 Friction device 186 Pin 187 Friction ring 190 Coupling element 190a Coupling element 191 Metal thin plate member 192 Ribe Top pin 193 Rivet pin 194 Opening 195 Opening 196 Tooth side surface 197 Outer profile 198 Coupling element 200 Input shaft or crankshaft 201 Input side member 202 Startering gear 203 Housing range 204 Arc spring 205 Output member 206 Additional shear mass 207 Flange range 207 'Flange range 207''Output flange 208 Clutch hub 208' Clutch hub 208 '' Clutch hub cover 209 Radial bearing 209 'Fixed bearing 210 Transmission input shaft 210' Transmission input shaft 210 '' Transmission input shaft 211 Input inside Friction plate support 212 Sleeve-shaped component 213 Clutch cover 214 Bonded metal thin plate 215 Input friction plate support 216 Output friction plate support 217 Output friction plate support or hub range 217a Road 218 Outer transmission input shaft 219 Wave spring 220 Clutch cover or tension pot 221 Cover bearing 222 CSC housing 223 Component 224 Case bottom 225 Oil supply portion 226 Press pot 227 Press pot 228 Adjustment disk or attachment portion 229 Position fixing ring or Adjustment disk 230 Position fixing ring 300 Flexible plate 301 Pipe 302 Radial bearing 400 Bearing 401 Pipe line 402 Pipe line 403 Spring 404 Spring 500 Flexible plate 501 Pipe 502 Pipe 600 Pilot 700 Input hub 701 Input friction plate support body 702 Radial bearing 703 Transmission Input shaft 704 Wet chamber 705 Case bottom 706 Clutch cover 707 Rotating surface 707 '' ZMS output flange 708 Output friction plate Holding body 709 Bonded metal thin plate 709a Tongue piece 710 Return spring 711 Press pot 712 Ring element 713 Position fixing ring or return spring 714 Press pot 715 CSC housing 715a Attached part 716 Component member 717 Cover bearing 718 Hollow shaft 800 CSC housing 801 Attached part 802 Case bottom 803 Transmission input shaft 804 Element or metal thin plate jaw or tightening jaw 805 Screw fastening member 806 Snap ring 807 Cover bearing 808 Tension pot 809 Output friction plate support 810 Connection flange 811 Through hole 812 Metal thin plate K1 Multi-plate clutch K2 Multi-plate clutch L1 Flow of operating force P1 Bearing P2 Bearing P3 Bearing P4 Bearing P5 Bearing

Claims (8)

In the clutch device,
The clutch device is used in a power train that includes a prime mover and a transmission that is arranged following the clutch device;
Clutch device comprises at least one multi-plate clutch, multi-plate clutch comprises a friction plate support one input side, a friction plate support one output side, provided alternately in the axial direction A plurality of friction plates, and the clutch device further includes an operation device,
One or more multi-plate clutch, to the operation device is coupled via a cover bearing, forms a constructional unit,
The housing of the operating device against the bell of the clutch case, and preload is applied in the axial direction through the tightening element to absorb the forces and moments occurring during operation, thereby, provided in the clutch case A clutch device , wherein an oil supply portion and an oil supply portion provided inside a housing of the operating device are tightly tightened . The housing of the operating device has an axial convex or concave part,
A component unit consisting of a clutch and an operating device is supported in a radial direction by a bell-shaped clutch case on the transmission side via the convex portion or the concave portion,
The clutch device according to claim 1, wherein the other radial support is provided via a movable bearing provided between the clutch input hub and one of the plurality of transmission input shafts. The multi-plate clutch is arranged to overlap in the radial direction,
The friction plate support on the input side of the radially outer multi-plate clutch is supported by the housing of the operating device via a support metal thin plate or a support pot in a radial direction but is immovably supported in the axial direction. Thus, the power flow of the operating force generated by the operating device is supported by the housing of the operating device via the axially stationary support portion of the friction plate support on the input side on the radially outer side, 3. A clutch device according to claim 1 or 2, wherein a closed power flow is provided inside the clutch device. In the clutch device,
The clutch device is used in a power train that includes a prime mover and a transmission that is arranged following the clutch device;
Clutch device comprises at least one multi-plate clutch, multi-plate clutch comprises a friction plate support one input side, a friction plate support one output side, provided alternately in the axial direction A plurality of friction plates, and the clutch device further includes an operation device,
One or more multi-plate clutches and an operating device are coupled together via a cover bearing to form a component unit;
A fixed bearing is disposed between the clutch input hub and one of the plurality of transmission input shafts;
A bearing acting exclusively in the radial direction is arranged between the housing of the operating device and one of the plurality of transmission input shafts,
A flexible torque support member is provided in the axial direction between the housing of the operating device and the bottom of the bell-shaped clutch case ,
A pipe connection portion that is set in the axial direction or is set in the radial direction is provided, and the pipe connection portion connects the hydraulic medium supply portion on the transmission side to the operating device,
When the pipe connecting portion is set in the axial direction, the pipe connecting portion is configured by a pipe formed to have play in the axial direction with respect to the housing of the operating device and the clutch case. ,
When the pipe connection portion is oriented in the radial direction, the pipe connection portion is constituted by two pipe lines formed so as to absorb the axial movement of the clutch , Clutch device. In the clutch device,
The clutch device is used in a power train that includes a prime mover and a transmission that is arranged following the clutch device;
Clutch device comprises at least one multi-plate clutch, multi-plate clutch comprises a friction plate support one input side, a friction plate support one output side, provided alternately in the axial direction A plurality of friction plates, and the clutch device further includes an operation device,
And one or more multi-plate clutch, and operating devices are coupled to each other via the cover bearing to form a configuration unit,
Between the clutch input hub and one of the plurality of transmission input shafts, a bearing acting exclusively in the radial direction is arranged,
Between the housing of the operating device and one of the plurality of transmission input shafts, radial support is performed exclusively via a flexible plate for the bottom of the bell-shaped clutch case ,
A pipe connecting portion set in the radial direction is provided, and the pipe connecting portion connects a hydraulic medium supply portion on the transmission side to the operating device,
2. The clutch device according to claim 1, wherein the pipe connecting portion includes two pipe lines formed so as to absorb the axial movement of the clutch. The clutch device according to claim 5 , wherein a pilot bearing is provided between the clutch input hub and the crankshaft. In the multi-clutch device,
The multi-clutch device is used for a power train that includes a prime mover and a transmission arranged following the multi-clutch device,
The multi-clutch device includes two multi-plate clutches fitted inward and outward in the radial direction, and each of the multi-plate clutches has one friction plate support on the input side and one friction plate support on the output side. And a plurality of friction plates provided alternately in the axial direction, and the multi-clutch device further comprises an operating device,
The multi-plate clutch and the operating device are coupled to each other via a cover bearing to form a constituent unit,
A spring element is disposed between the output friction plate support of the radially inner multi-plate clutch and the transmission input shaft coupled to the output friction plate support. an output friction plate support member, between the output friction plates support the radially outer multiple disc clutch, a first thrust bearing is arranged, the output friction plates support the radially outer multiplate clutch In addition, another thrust bearing is arranged between the input friction plate support of the multi-plate clutch on the radially outer side,
The housing of the operating device against the bell of the clutch case, preload has been added in the axial direction through the tightening element to absorb the forces and moments during operation, thereby, provided in the clutch case oil A multi-clutch device characterized in that a supply portion and an oil supply portion provided inside a housing of the operating device are tightly tightened . The first thrust bearing is disposed between the output friction plate support of the radially inner multi-plate clutch and the output friction plate support of the radially outer multi-plate clutch with a spacer interposed therebetween. The multi-clutch device according to claim 7, wherein:

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