synchronizing clutch

Abstract

The invention relates to a synchronous clutch for coupling an auxiliary machine to an internal combustion engine, comprising a first clutch member (16) and a second clutch member (18), which clutch members can be coupled to one another via two friction ring sets. The friction ring sets each have a first and a second friction ring (26, 34, 126, 134), which friction rings can be coupled to one another in a torque-transmitting manner. A preloading device (52) presses the friction ring sets away from one another and into a frictionally locked position, which frictionally locked position can be disconnected again by means of an actuator (80).

Description

Technical Field

[0001] The present invention relates to a synchronizing clutch, particularly for coupling an internal combustion engine with an auxiliary unit, particularly a compressor. Background Technology

[0002] Synchronous clutches are well known in the prior art. In particular, diaphragm clutches are used to couple internal combustion engines with compressors.

[0003] In this and all other applications, diaphragm clutches must be designed in terms of the torque they can transmit. Typically, a higher transmittable torque requires a diaphragm clutch with a larger transmittable torque configuration than a lower transmittable torque. Therefore, there is a conflict between the goal of achieving high transmittable torque and the most compact possible construction of a synchronizing clutch or diaphragm clutch.

[0004] For applications driven by internal combustion engines, it must also be considered that the torque output from such an engine, like overload torque, will fluctuate in an unpredictable manner. Therefore, the design of the synchronizing clutch used with the internal combustion engine must always take these torque fluctuations into account. To ensure reliable torque transmission, such a synchronizing clutch must also be able to transmit undesirable excessive torque. This limits the achievement of a compact synchronizing clutch design. Summary of the Invention

[0005] Therefore, the object of the present invention is to provide a particularly compact synchronous clutch that can ensure reliable torque transmission.

[0006] This objective is achieved through the synchronizing clutch of the present invention.

[0007] The synchronizing clutch can transmit exceptionally high torque for the required structural space via two friction ring sets. In other words, the synchronizing clutch is constructed to be particularly compact due to the torque it can transmit. These advantages are particularly prominent compared to known diaphragm clutches. In its normal, non-operated state, the synchronizing clutch is in the friction-locked position, that is, closed, which is achieved through a preload device. Therefore, the synchronizing clutch is a so-called normally closed clutch. Thus, it can also transmit torque in a non-operated state (a state sometimes referred to as a pressure-free or current-free state).

[0008] The diaphragm clutch is disengaged by an actuator, particularly a piston-cylinder unit, preferably a pneumatically operated unit. This actuator's cessation of operation ensures that the diaphragm clutch's closing resistance (Zustellung) is always present via a preload device that operates without external power.

[0009] According to a preferred embodiment, the first friction ring is an inner friction ring with a conical surface disposed on its radially outer surface, and the second friction ring is an intermediate friction ring having a friction cone on which the conical surface of the second friction ring is disposed. An outer friction ring is further provided, having a conical surface on its radially inner surface and being coupled to the first clutch member substantially non-rotatably and axially slidably. Here, the friction cone of the intermediate friction ring extends between the conical surfaces of the inner and outer friction rings. In the friction-locked position, the conical surface of the outer friction ring and the friction cone of the intermediate friction ring are frictionally locked together.

[0010] As an optional or supplementary solution, the additional first friction ring is an additional inner friction ring with a conical surface disposed on its radially outer surface, and the additional second friction ring is an additional intermediate friction ring having a friction cone, on which the conical surface of the additional second friction ring is disposed. Furthermore, an additional outer friction ring is provided, which has a conical surface on its radially inner surface and is coupled to the first clutch member substantially non-rotatably and axially slidably. The friction cone of the additional intermediate friction ring extends between the conical surfaces of the additional inner friction ring and the additional outer friction ring. In the friction-locked position, the conical surface of the additional outer friction ring is frictionally locked to the friction cone of the additional intermediate friction ring.

[0011] In both of the above-described alternatives, each friction ring assembly therefore comprises three friction rings. Such friction ring assemblies are particularly well-suited for transmitting relatively high torque. Thus, a synchronous clutch can be constructed that reliably transmits particularly high torque while maintaining a compact structure.

[0012] In the preface to this specification, the concepts of first friction ring and inner friction ring are used synonymously. The same applies to the additional first friction ring and the additional inner friction ring. Second friction ring and intermediate friction ring are also understood to be synonymous. Furthermore, this also applies to the additional second friction ring and the additional intermediate friction ring.

[0013] According to a preferred embodiment, the preload device is positioned between the first and second friction ring groups, particularly between the two inner friction rings, and is applied to them to move them away from each other in opposite directions.

[0014] At least one spring element is preferred as a pretensioning device, and disc spring assemblies are particularly advantageous here due to their high force and compact structure.

[0015] In the friction-locked position, the inner friction rings, loaded by spring elements to separate from each other—that is, the inner friction ring and the other inner friction ring—are axially pressed against the outer ring via their respective conical surfaces and correspondingly arranged intermediate rings, more precisely against the conical surfaces of the correspondingly arranged outer rings. These outer rings, in turn, rest against arranged axial stops. In this way, the transmittable torque can be determined by the spring stiffness of the spring elements.

[0016] Preferably, the first and second friction ring groups are constructed in a mirror-symmetrical manner. The axis of rotation extends perpendicular to the plane of symmetry of the friction ring groups. This configuration allows for a compact structure. Furthermore, the symmetrical structure enables the synchronous clutch to achieve advantageous wear resistance, resulting in a particularly long service life. The friction rings can also be constructed as identical components, that is, as an inner friction ring, an outer friction ring, and an intermediate friction ring, respectively.

[0017] According to one embodiment, the inner friction ring and / or the additional inner friction ring and / or the outer friction ring and / or the additional outer friction ring are coupled to the first clutch member via a sleeve that is axially slidably supported on the first clutch member. Here, the sleeve and the first clutch member are connected in a way that prevents relative rotation. This results in reliable torque transmission.

[0018] A first axial stop may be provided on the sleeve for the outer friction ring, which restricts axial movement of the outer friction ring in a direction extending distal from the other outer friction ring, and / or a second axial stop may be provided on the sleeve for the other outer friction ring, which restricts axial movement of the other outer friction ring in a direction extending distal from the other outer friction ring. Preferably, both the first and second axial stops are provided. Thus, the outer friction ring is always positioned between these axial stops and thereby reliably rotatably connected to the sleeve.

[0019] At least in the friction-locked position, the outer friction ring advantageously rests against the first axial stop and the other outer friction ring rests against the second axial stop. The outer friction rings and the other outer friction ring are thus also positioned axially. This is primarily to prevent unwanted noise.

[0020] The sleeve may have internal teeth that mesh with external teeth provided on the first clutch member, wherein the teeth of the internal and external teeth extend substantially along the axis of rotation. This extension of the teeth creates axial slip capability of the sleeve. Furthermore, a reliable coupling between the sleeve and the first clutch member, preventing relative rotation, is ensured.

[0021] According to one embodiment, the first or second clutch component is the shaft of an auxiliary unit, particularly the compressor shaft. The compressor, including the compressor shaft or coupled to the compressor shaft, is then reliably driven via a synchronizing clutch.

[0022] According to one option, the second or first clutch component is a driven wheel or driven cover. Preferably, the driven wheel or driven cover is connected to the internal combustion engine in a transmission manner. The internal combustion engine thus constitutes a torque source.

[0023] The internal friction ring, or the other internal friction ring, may be configured with a first support ring, wherein the internal friction ring or the other internal friction ring rests against an axial stop provided on the first clutch member via the first support ring. Here, the first support ring can act in the axial direction of the load via a spring element. Therefore, the torque that can be transmitted by the synchronous clutch can be adjusted via the first support ring in such a way that the support ring overcomes the axial force generated by the spring element to a large or small degree.

[0024] The first support ring advantageously passes through the outer friction ring or the other outer friction ring at least partially in the axial direction via a pin and an opening. This ensures a compact structure for the synchronizing clutch.

[0025] In the friction-locked position, the first support ring and / or the axial stop disposed on the first clutch component may be spaced apart from the sleeve along the axis of rotation. This spacing also signifies a defined clearance, representing a distance that the components of the synchronizing clutch, particularly one or more friction rings, must traverse in order to move from the disengaged or ventilated position to the friction-locked position.

[0026] In the disengaged position, the first support ring and / or the axial stop disposed on the first clutch member can abut against the sleeve along the axis of rotation, particularly the axial stop acting on the sleeve via the intervening first support ring. In the disengaged position, also known as the ventilated position, the aforementioned members thus occupy a defined position. Furthermore, the abutment against the axial stop prevents undesirable noise generation.

[0027] The additional internal friction ring, or the internal friction ring itself, may be configured with a second support ring, wherein the additional internal friction ring, or the internal friction ring itself, is coupled via the second support ring to an actuator that operates in the axial direction. This actuator is used to move the synchronous clutch from a friction-locked position (occupied in the non-operated state of the synchronous clutch due to the action of the spring element (normally closed clutch)) to a disengaged position. For this purpose, an operating unit applies an operating force to the internal friction ring, or the additional internal friction ring itself, in the axial direction via the second support ring.

[0028] The second support ring may, corresponding to the first support ring, pass at least partially through the additional outer friction ring or the outer friction ring in the axial direction. This ensures a compact structure for the synchronizing clutch.

[0029] Preferably, the actuator includes an annular piston to which fluid can be loaded via an annular pressure chamber. The operating unit is therefore either hydraulic or pneumatic. Such operating units have proven feasible in the prior art and are reliable in operation.

[0030] As an alternative, the synchronizing clutch can also be adjusted via an electric actuator.

[0031] In the friction-locked position, the second support ring can be spaced apart from the sleeve along the axis of rotation, producing the effects and advantages already described with respect to the first support ring.

[0032] In the disconnected position, the second support ring can rest against the sleeve along the axis of rotation. This also produces the effects and advantages already described regarding the first support ring.

[0033] According to one embodiment, the inner friction ring and / or the outer friction ring and / or the intermediate friction ring and / or the additional inner friction ring and / or the additional outer friction ring and / or the additional intermediate friction ring are multiple formed sheet metal parts or a single formed sheet metal part. Such friction rings can be manufactured simply and economically. Alternatively, the friction rings can also be manufactured using sintering or 3D printing methods.

[0034] One alternative configuration specifies that the inner friction ring and / or outer friction ring and / or intermediate friction ring and / or the additional inner friction ring and / or the additional outer friction ring and / or the additional intermediate friction ring have L-shaped cross-sections extending in the radial plane, and each has a tapered leg and a radial leg extending radially outward or radially inward from the tapered leg. This configuration allows the friction rings to be nested within each other in a narrow space, thereby achieving a compact structure for the synchronous clutch.

[0035] Here, the radial legs of the intermediate friction ring and / or the other intermediate friction ring may have external teeth on their radially outer sides, and these external teeth mesh with internal teeth provided on the second clutch member. This internal tooth can be readily designed, in particular, on the inner surface of the drive cover (Antriebsglocke). This is only one possible arrangement. This achieves reliable coupling between the second clutch member and the correspondingly configured friction rings.

[0036] The radial legs of the inner friction ring and / or the other inner friction ring may also have internal teeth on their radially inner side, and these internal teeth mesh with external teeth provided on the first clutch member or on a sleeve coupled to the first clutch member (which has already been partially described above). This achieves reliable coupling between the first clutch member and the correspondingly configured inner friction ring.

[0037] Alternatively, it is possible that the radial legs of the outer friction ring and / or the other outer friction ring have internal teeth on their radially inner sides, and these internal teeth mesh with external teeth disposed on the first clutch member or on a sleeve coupled to the first clutch member. This achieves reliable coupling between the first clutch member or sleeve and the correspondingly configured outer friction ring. Attached Figure Description

[0038] Further features and advantages of the invention will become apparent from the following description with reference to the accompanying drawings. The drawings show:

[0039] Figure 1 This is a schematic diagram of a cargo truck having an internal combustion engine, an auxiliary unit, and an intermediately connected synchronizing clutch according to the invention;

[0040] Figure 2 This is a schematic cross-sectional view of the first embodiment of the synchronous clutch according to the present invention in the friction-locked position;

[0041] Figure 3 yes Figure 2 A schematic cross-sectional view of the synchronous clutch in the disengaged position;

[0042] Figure 4 This is a schematic cross-sectional view of a second embodiment of the synchronous clutch according to the present invention. Detailed Implementation

[0043] Figure 1 The illustration schematically shows a portion of the cargo truck, namely the internal combustion engine 10, which not only drives the cargo truck but also drives the auxiliary unit 12, such as the compressor.

[0044] A synchronizing clutch 14 is provided in the transmission system between the internal combustion engine 10 and the auxiliary unit 12. The synchronizing clutch is configured to reliably transmit high torque primarily during torque fluctuations and / or load fluctuations.

[0045] Figure 2 The synchronizing clutch shown in detail includes a first clutch member 16, which is so-called, in particular in the form of an auxiliary unit 12, on the shaft, and this first clutch member can be said to constitute the output side of the synchronizing clutch 14.

[0046] Drive-side components: a so-called second clutch component 18, which is currently designed as a multi-piece unit (this is not mandatory); a drive gear 20 and a drive cover 22 connected to the drive gear, which may also be referred to as a drive wheel.

[0047] The first clutch component 16 is rotatably supported in the clutch component 18 via a slewing bearing 24, or conversely, the second clutch component 18 is rotatably supported on the first clutch component 16.

[0048] Multiple conical friction rings act between clutch components 16 and 18; these friction rings will be described later. For example, from... Figure 2 As can be seen from the text, the construction of these friction rings is mirror-symmetric about the radial plane of the relative rotation axis A and has a first friction ring group ( Figure 2 (left side of the middle) and the second friction ring group ( Figure 2 (Right side of the middle)

[0049] In this embodiment, each friction ring group has three friction rings.

[0050] The first friction ring assembly includes a first friction ring 26, which in the illustrated embodiment is an inner friction ring 26. Therefore, the same reference numerals are used for the first friction ring and the inner friction ring. The first friction ring 26 has a tapered surface 28 on its radially outer surface.

[0051] In addition, an outer friction ring 30 is provided, which has a conical surface 32 on its radial inner side.

[0052] Furthermore, the first friction ring assembly has a second friction ring 34 with a tapered surface, which in the illustrated embodiment is an intermediate friction ring 34. Therefore, the same reference numerals are used for the second friction ring and the intermediate friction ring.

[0053] The intermediate friction ring 34 has a friction cone 35, and the cone surface 34a of the second friction ring 34 is disposed on the friction cone and the friction cone extends between the cone surfaces 28 and 32 and preferably has its slope.

[0054] The second friction ring group, designed as a mirror image of the radial axis of the first friction ring group, includes an additional first friction ring 126, which in the illustrated embodiment is an additional inner friction ring 126. This additional inner friction ring has a tapered surface 128 on its radially outer surface. The same reference numerals are used for the additional first friction ring and the additional inner friction ring.

[0055] In addition, an additional outer friction ring 130 is provided, which has a conical surface 132 on its radial inner surface.

[0056] The second friction ring assembly also has an additional second friction ring 134 with a conical surface 134a, which in the illustrated embodiment is an additional intermediate friction ring 134. Therefore, the same reference numerals are used for the additional second friction ring and the additional intermediate friction ring.

[0057] The components, surfaces, and sections of the second friction ring assembly are designed according to the first friction ring assembly, and the reference numerals in the drawings are 100 more than those in the first friction ring assembly.

[0058] exist Figure 2 As can be seen, the two friction ring assemblies are set up one after another along the rotation axis A.

[0059] The inner friction rings 26 and 126 and the outer friction rings 30 and 130 are L-shaped in cross-section and each has a tapered leg and a radial leg extending radially inward from the tapered leg. For clarity, only the inner friction ring 26, the tapered leg 40, and the radial leg 42 are given reference numerals. The intermediate friction rings 34 and 134 are also L-shaped and have tapered legs constituting the friction cones 35 and 135 and radial legs 46 and 146 extending radially outward from the tapered legs.

[0060] The radial legs 42 of the inner friction rings 26 and 126 and the outer friction rings 30 and 130 have internal teeth 48 on their radially inner sides (reference numerals are only provided on the radial legs 42 for clarity). This internal tooth 48 is an axial tooth, which is axially slidably disposed on the outer tooth 50 of the sleeve 52.

[0061] The sleeve 52 also has an internal toothed portion 54, which is configured as an axial toothed portion and engages with the external toothed portion 56 of the first clutch member 16. The sleeve 52 is axially slidable but fixedly coupled to the clutch member 16 in the direction of rotation via the teeth 54 and 56.

[0062] The external teeth 58 on each radial leg 46 of the intermediate friction rings 34, 134 are axially slidable but fixedly connected to the second clutch member 18 along the direction of rotation because they engage with the internal teeth 60 of the drive cover 22.

[0063] Single, multiple, or all friction rings can be formed sheet metal parts.

[0064] A pre-tightening device 62 is disposed in the annular space between the inner friction rings 26 and 126. The pre-tightening device is configured in the form of a disc spring assembly.

[0065] The preload device 62 is used to press the synchronous clutch into place when the synchronous clutch is not operated from the outside (normal position). Figure 2The friction-locked position (closed synchronous clutch) is shown. The preload device 62 is used to axially press the friction ring assemblies apart.

[0066] In the friction-locked position, the first axial stop 64, abutting against the outer friction ring 30, is laterally fastened to the sleeve 52. The second axial stop 164 serves as a travel limiter for another outer friction ring 130, which... Figure 2 The position shown is abutting against the axial stop 164 on the outside.

[0067] An axial stop 66 is provided on the side of the sleeve 52 on the first clutch component 16, and the support ring 68 is located on... Figure 2 In the position shown, acting on the axial stop, the support ring has an annular radial segment 70 and a plurality of axial pins 72 extending from the radial segment. A second support ring 168, designed to be identical to the first, is arranged in a mirror-symmetrical manner, and this second support ring is also axially slidably fitted onto the clutch member 16.

[0068] Pins 72 and 172 extend through corresponding openings 74 and 174 into the outer friction rings 30 and 130 until they reach the inner friction rings 26 and 126 and abut against the outer surface of their radial legs 42. Thus, the stop 66 forms a stop for the inner friction ring 26 via the support ring 68.

[0069] The support ring 168 can be operated by an actuator 80 in the form of a piston-cylinder unit. A pneumatically operable annular piston 82 is fixedly supported on an auxiliary unit along with its housing. A slewing bearing 86 couples the annular piston 82 to the support ring 168.

[0070] exist Figure 2 In the position shown, actuator 80 is not operated or at least weakly operated such that it does not exert spring pressure on preload device 62, thus placing the synchronous clutch in a friction-locked position. In this friction-locked position, the friction cones 35 of the intermediate friction rings 34, 134 are clamped between cone surfaces 28, 32, so that torque is transmitted and circumferential sliding between the friction rings does not occur.

[0071] As can be seen, in the friction-locked position, the sleeve 52 is spaced apart from the support rings 68 and 168 by a gap b at both axial ends.

[0072] If the annular pressure chamber 90 of actuator 80 is filled and actuator 80 is activated, then the synchronous clutch reaches... Figure 3 The disconnection location is shown.

[0073] The annular piston 82 presses the second support ring 168 and thus the inner friction ring 126 against the preload device 62 toward the inner friction ring 26. The support ring 168 then axially contacts the sleeve 52 via the radial section 70 and slides the sleeve toward the axial stop 66 until the sleeve 52 contacts the support ring 68 located between the axial stop 66 and the sleeve 52 on its opposite axial end side. The clearance b is no longer present, and the precise positions of all friction rings relative to each other are predetermined. This ensures that no torque is transmitted via the friction rings now radially spaced apart, and that a small traction torque is transmitted when necessary.

[0074] although Figure 3 The axial contact of the inner friction rings 26 and 126 is shown; however, this is not necessary if the sleeve 52 indirectly forms an axial stop for the inner friction ring via the support ring 168.

[0075] Figure 4 The illustrated embodiment is designed to be slightly more compact because the inner friction rings 26, 126 and the outer friction rings 30, 130 form a U-shape that surrounds the cross-section on the radially outer side, wherein the "U" is open along the axial direction and the open sides of the inner friction rings 26, 126 and the outer friction rings 30, 130 face each other, thereby creating a compact internal chamber 94 in which the preload device 62 is disposed.

[0076] Radial legs 42 and 70 extend radially inward from the lower leg of the corresponding U until they reach sleeve 52.

[0077] In addition, components or sections marked with already adopted reference numerals correspond to... Figure 2 and 3 Those components or sections are shown. For clarity, in Figure 4 Not all components and sections are marked with reference numerals.

[0078] It is worth mentioning that: Figure 4 An intermediate ring 92 is provided between the slewing bearing 86 and the support ring 168.

[0079] The invention can also be designed with only two friction rings in each friction ring group, in which case either the inner friction rings 26 and 126 or the outer friction rings 30 and 130 can be omitted. Then, it may be necessary to modify the corresponding stop or preload device 62 on other components. In this case, only the first and second friction rings for each friction ring group remain.

[0080] If, for example, the inner friction rings 26 and 126 are omitted, then the intermediate friction rings 34 and 134 must be equipped with radial side legs 42, so that the preload device 62 is engaged to press the intermediate friction rings 34 and 134 in opposite directions. Then the actuator 80 must accordingly—possibly while still under tension—act either on the intermediate friction rings 34 and 134 or on the outer friction rings 30 and 130.

[0081] If the outer friction rings 30 and 130 are omitted, then axial stops 64 and 164 must be provided on the second clutch component 18 in order to restrict the movement of the intermediate friction rings 34 and 134 separating from each other.

[0082] All friction rings, along with sleeve 52, can also be configured in the exact opposite way; that is, sleeve 52 operates within toothed section 60 and also has an axial stop 66 within toothed section 60. Intermediate friction rings 34 and 134 mesh with toothed section 56. (Regarding...) Figure 2 The cross-section shows that the friction rings are completely upside down. In reality, the geometry of these friction rings is, of course, different, as they are designed as annular rings. According to the claims, this reversal of the position / shape of the friction rings and sleeve is tantamount to the first clutch component 16 becoming the second clutch component, and the second clutch component 18 becoming the first clutch component.

Claims

1. A synchronizing clutch, comprising: A first clutch component (16) is rotatable about a rotation axis (A). A second clutch component (18) is rotatable about the rotation axis (A). A first friction ring assembly, the first friction ring assembly having: • A first friction ring (26), having a conical surface (28) and being substantially non-rotatable and axially slidable coupled to a first clutch member (16), and • A second friction ring (34), which has a conical surface (34a) and is coupled to the second clutch member (18) in a substantially non-rotatable and axially slidable manner. The second friction ring assembly has: • An additional first friction ring (126), having a conical surface (128) and being substantially non-rotatable and axially slippery coupled to the first clutch member (16), and • An additional second friction ring (134), which has a conical surface (134a) and is substantially non-rotatable and axially slidable coupled to the second clutch member (18), The first friction ring group and the second friction ring group are arranged sequentially along the rotation axis (A). The first clutch component (16) and the second clutch component (18) are disengaged in the disengaged position along the rotational direction oriented about the rotational axis (A) and frictionally coupled in the frictionally engaged position along the rotational direction. In the frictionally engaged position, the conical surface (28) of the first friction ring (26) is frictionally engaged with the conical surface (34a) of the second friction ring (34), and the conical surface (128) of the additional first friction ring (126) is frictionally engaged with the conical surface (134a) of the additional second friction ring (134). The device includes a pre-tightening device (62) that acts between the first friction ring group and the second friction ring group and moves each friction ring group to the friction locking position. It also includes an actuator (80) that acts in the opposite direction to the pre-tightening device and moves each friction ring group to the disengaged position.

2. The synchronous clutch according to claim 1, characterized in that: The first friction ring (26) is an inner friction ring (26), and the conical surface (28) of the first friction ring (26) is disposed on the radial outer surface of the first friction ring (26). The second friction ring (34) is an intermediate friction ring (34) having a friction cone (35), on which the conical surface (34a) of the second friction ring (34) is disposed, and In addition, an outer friction ring (30) is provided, which has a conical surface (32) on its radially inner side and is coupled to the first clutch member (16) in a substantially non-rotatable and axially slippery manner. Among them, the friction cone (35) of the intermediate friction ring (34) extends between the cone surface (28) of the inner friction ring (26) and the cone surface (32) of the outer friction ring (30), and In the friction-locked position, the conical surface (32) of the outer friction ring (30) is frictionally locked to the friction cone (35) of the middle friction ring (34); And / or The additional first friction ring (126) is an additional inner friction ring (126), and the conical surface (128) of the additional first friction ring (126) is disposed on the radial outer surface of the additional first friction ring (126). The additional second friction ring (134) is an additional intermediate friction ring (134) having a friction cone (135), the conical surface (134a) of the additional second friction ring (134) being disposed on the friction cone, and In addition, an additional outer friction ring (130) is provided, which has a conical surface (132) on its radially inner side and is coupled to the first clutch member (16) in a substantially non-rotatable and axially slippery manner. The friction cone (135) of the additional intermediate friction ring (134) extends between the cone surface (128) of the additional inner friction ring (126) and the cone surface (132) of the additional outer friction ring (130). In the friction-locked position, the conical surface (132) of the other outer friction ring (130) is frictionally locked to the friction cone (135) of the other intermediate friction ring (134).

3. The synchronous clutch according to claim 1 or 2, characterized in that: A preload device (62) is positioned between the first friction ring group and the second friction ring group and loads them to separate them from each other, wherein the preload device (62) has at least one spring element.

4. The synchronous clutch according to claim 1 or 2, characterized in that: The first and second friction ring groups are constructed to be mirror-symmetrical, and the axis of rotation (A) extends perpendicular to the plane of symmetry of the friction ring groups.

5. The synchronous clutch according to claim 2, characterized in that: The first friction ring (26) and / or the other first friction ring (126) and / or the other outer friction ring (30) and / or the other outer friction ring (130) are coupled to the first clutch member (16) via a sleeve (52) slidably supported on the first clutch member (16).

6. The synchronous clutch according to claim 5, characterized in that: A first axial stop (64) is provided on the sleeve (52) for the outer friction ring (30), which restricts the axial movement of the outer friction ring (30) in a direction pointing distal from the other outer friction ring (130), and / or a second axial stop (164) is provided on the sleeve (52) for the other outer friction ring (130), which restricts the axial movement of the other outer friction ring (130) in a direction pointing distal from the outer friction ring (30).

7. The synchronous clutch according to claim 6, characterized in that: At least in the friction-locked position, the outer friction ring (30) rests against the first axial stop (64), and the other outer friction ring (130) rests against the second axial stop (164).

8. The synchronous clutch according to claim 5, characterized in that: The sleeve (52) has an internal toothed portion (54) that meshes with an external toothed portion (56) provided on the first clutch member (16), wherein the teeth of the internal toothed portion (54) and the teeth of the external toothed portion (56) extend substantially along the axis of rotation, respectively.

9. The synchronous clutch according to claim 1 or 2, characterized in that: The first or second clutch component (16, 18) is a shaft.

10. The synchronous clutch according to claim 1 or 2, characterized in that: The second or first clutch component (18, 16) is the driven wheel or driven cover (22).

11. The synchronous clutch according to claim 2, characterized in that: The first friction ring (26) or the other first friction ring (126) is provided with a first support ring (68), wherein the first friction ring (26) or the other first friction ring (126) rests against an axial stop (66) provided on the first clutch member (16) via the first support ring (68).

12. The synchronous clutch according to claim 11, characterized in that: The first support ring (68) passes at least partially through the outer friction ring (30) or the other outer friction ring (130) in the axial direction.

13. The synchronous clutch according to claim 11, characterized in that: The first friction ring (26) and / or the other first friction ring (126) and / or the outer friction ring (30) and / or the other outer friction ring (130) are coupled to the first clutch member (16) via a sleeve (52) slidably supported on the first clutch member (16) and in the friction-locked position, the first support ring (68) and / or the axial stop (66) provided on the first clutch member (16) are spaced apart from the sleeve (52) along the axis of rotation.

14. The synchronous clutch according to claim 11, characterized in that: The first friction ring (26) and / or the other first friction ring (126) and / or the outer friction ring (30) and / or the other outer friction ring (130) are coupled to the first clutch member (16) via a sleeve (52) slidably supported on the first clutch member (16) and in the disengaged position, the first support ring (68) and / or the axial stop (66) disposed on the first clutch member (16) abut against the sleeve (52) along the axis of rotation (A), wherein the axial stop (66) abuts against the sleeve (52) via the first support ring (68).

15. The synchronous clutch according to claim 5, characterized in that: The additional first friction ring (126) or the first friction ring (26) is provided with a second support ring (168), wherein the additional first friction ring (126) or the first friction ring (26) is coupled to an actuator (80) acting in the axial direction via the second support ring (168).

16. The synchronous clutch according to claim 2, characterized in that: The additional first friction ring (126) or the first friction ring (26) is provided with a second support ring (168), wherein the additional first friction ring (126) or the first friction ring (26) is coupled to an actuator (80) acting in the axial direction via the second support ring (168) and the second support ring (168) passes at least partially through the additional outer friction ring (130) or the outer friction ring (30) in the axial direction.

17. The synchronous clutch according to claim 15, characterized in that: The actuator (80) includes an annular piston (82) to which fluid can be loaded via an annular pressure chamber (90).

18. The synchronous clutch according to claim 15, characterized in that: The first friction ring (26) and / or the other first friction ring (126) and / or the outer friction ring (30) and / or the other outer friction ring (130) are coupled to the first clutch member (16) via a sleeve (52) slidably supported on the first clutch member (16) and in the friction-locked position, the second support ring (168) is spaced apart from the sleeve (52) along the axis of rotation (A).

19. The synchronous clutch according to claim 15, characterized in that: In the disconnected position, the second support ring (168) rests against the sleeve (52) along the axis of rotation (A).

20. The synchronous clutch according to claim 2, characterized in that: The first friction ring (26) and / or the outer friction ring (30) and / or the second friction ring (34) and / or the additional first friction ring (126) and / or the additional outer friction ring (130) and / or the additional second friction ring (134) are a plurality of shaped sheet metal parts or a single shaped sheet metal part.

21. The synchronous clutch according to claim 2, characterized in that: The first friction ring (26) and / or the outer friction ring (30) and / or the second friction ring (34) and / or the additional first friction ring (126) and / or the additional outer friction ring (130) and / or the additional second friction ring (134) have L-shaped cross sections extending in the radial plane and have tapered side legs (62) and radial side legs (42) extending radially outward or radially inward from the tapered side legs.

22. The synchronous clutch according to claim 21, characterized in that: The radial side legs (46, 146) of the second friction ring (34) and / or the other second friction ring (134) have external teeth (58) on the radially outer side, and the external teeth (58) engage with internal teeth (60) provided on the second clutch member (18).

23. The synchronous clutch according to claim 21, characterized in that: The radial side legs (62) of the first friction ring (26) and / or the other first friction ring (126) have internal teeth (48) on the radially inner side, and the internal teeth (48) engage with external teeth (50) provided on the first clutch member (16) or provided on the sleeve (52) coupled to the first clutch member.

24. The synchronous clutch according to claim 21, characterized in that: The radial side legs (143) of the outer friction ring (30) and / or the other outer friction ring (130) have internal teeth (48) on the radially inner side, and the internal teeth (48) engage with external teeth (50) provided on the first clutch member (16) or provided on the sleeve (52) coupled to the first clutch member (16).

25. The synchronous clutch according to claim 1 or 2, characterized in that: The pre-tightening device (62) is positioned between the first friction ring (26) and the other first friction ring (126).

26. The synchronous clutch according to claim 3, characterized in that: The pretensioning device (62) has a disc spring assembly.

27. The synchronous clutch according to claim 9, characterized in that: The shaft is the compressor shaft.

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