Dual clutch for a power-shift shifting device having an axis of rotation

Abstract

The utility model relates to a double clutch for a power shifting type gear shifting device with a rotation axis and a reversing transmission, the double clutch comprises a first sub-clutch (1a) and a second sub-clutch (1b) for the reversing transmission of a motor vehicle, and the double clutch comprises an actuating device (100) coaxial with the rotation axis (A). The first actuating lever (20) is supported against the actuating device (100) and the second actuating lever (30) is supported against the actuating device (100), the first sub-clutch (1a) is actuated by the actuating device (100) by pushing for engagement purposes and the second sub-clutch (1b) is actuated by the actuating device (100) by pulling for engagement purposes.

Description

Technical Field

[0001] The present invention relates to a dual clutch for a reversing transmission for use in a motor vehicle. Preferably, the motor vehicle is an agricultural machine, in particular a tractor. The dual clutch according to the present invention is used as a powershift transmission. Background Art

[0002] Corresponding reversing transmissions are commonly used on tractors and agricultural implements that frequently change between forward and reverse travel. A reversing transmission is a manual transmission that can reverse at least one direction of rotation. This type of transmission is required when the drive system needs to provide two equivalent directions of rotation, but the driven machine cannot reverse.

[0003] The dual clutch coupled with a reversing transmission enables almost completely automatic changes of direction between forward and reverse driving without interrupting traction (a so-called powershift) or operating the clutch pedal. Torque is transmitted via one of the two sub-clutches that connect the two sub-transmissions to the drive.

[0004] The dual clutches of a dual-clutch transmission typically use two wet-running multi-plate clutches or single-plate dry clutches. Single-plate dry clutches in dual-clutch transmissions are only used as standard in compact engines with torques up to around 650 Nm, as dissipating the large amounts of waste heat is difficult at higher power levels.

[0005] Wet-running clutches allow for higher torque and vehicle mass for the same size. Waste heat generated during shifting and starting is dissipated via a cooling oil flow. The transmission itself typically serves as an oil sump. Therefore, the oil is used both to cool the clutch and lubricate the gearset. A wet dual clutch always exhibits a certain drag torque during disengagement, resulting in higher idle losses and reduced efficiency. Furthermore, the operation of the oil pump reduces overall efficiency. Furthermore, a wet dual clutch requires additional components for operation and control.

[0006] Wet double clutches for reversing transmissions are known in the prior art and are intended in particular for use in agricultural machinery, such as tractors.

[0007] Wet dual clutches must always be equipped with a cooling circuit to supply lubricating oil to dissipate the heat absorbed by the oil. The corresponding slave / master arrangement, consisting of an actuating lever and actuating bearings, as well as an additional cooling circuit, sometimes requires a considerable number of components. Furthermore, this arrangement requires a considerable amount of installation space and requires a high level of effort to assemble the arrangement.

[0008] Therefore, the purpose of the present invention is to at least partially overcome the problems known in the prior art. Utility Model Content

[0009] The dual clutch for a power shift type shifting device with a rotation axis created by the utility model comprises a first sub-clutch and a second sub-clutch, wherein the first sub-clutch comprises a first pressure plate, a flywheel and a first clutch disc located between the first pressure plate and the flywheel in the direction of the rotation axis, the first pressure plate and the first clutch disc are installed to be able to shift along the rotation axis, and the second sub-clutch comprises a second pressure plate, a housing protrusion fixedly connected to the housing and a second clutch disc located between the second pressure plate and the housing protrusion in the direction of the rotation axis, wherein the second pressure plate and the second clutch disc are installed to be able to shift along the rotation axis,

[0010] The dual clutch also includes an actuation system having a first actuating lever for actuating the first sub-clutch and a second actuating lever for actuating the second sub-clutch, the first sub-clutch and the second sub-clutch being disengaged in an unactuated state, the actuation of the first actuating lever occurring by pushing, and the actuation of the second actuating lever occurring by pulling.

[0011] As a precaution, it should be noted that the numerical designations used herein ("first," "second," etc.) are primarily (only) used to distinguish between several similar objects, dimensions, or processes, and in particular, it is to be specified that these objects, dimensions, or processes do not necessarily have dependencies and / or sequences with respect to each other. If dependencies and / or sequences are necessary, they will be explicitly stated herein or will be followed in a manner that is obvious to a person skilled in the art when studying the specifically described embodiments.

[0012] Preferably, the dual clutch is designed as a dry dual clutch.

[0013] The wet dual clutch always has a certain resistance torque when disengaging, which leads to higher idling losses.

[0014] This does not occur with a dry dual clutch. Therefore, a dry dual clutch offers higher efficiency than a wet dual clutch. Furthermore, a dry dual clutch is less complex than a wet dual clutch and requires fewer components, particularly because an oil cooling circuit is not required. Consequently, a dry dual clutch also requires less installation space. This reduced complexity also reduces assembly effort. Since the dual clutch according to the present invention is preferably used in agricultural machinery, such as tractors, the reduced number of components in the dual clutch also makes maintenance easier, allowing it to be performed on-site, rather than in a workshop.

[0015] The double clutch is formed by two component clutches, a first component clutch being formed by at least an element marked “first” and a second component clutch being formed by at least an element marked “second”.

[0016] A flywheel is a disc-shaped mass that is rotatably mounted on an axis of rotation without any imbalance. Among other things, a flywheel acts as an energy reservoir, storing its rotational motion or rotation with minimal frictional losses, in the form of rotational energy and kinetic energy from inertia, for use when needed. Preferably, the flywheel is connected to the crankshaft of an internal combustion engine.

[0017] Preferably, the housing and flywheel are connected to each other in a rotationally fixed manner, so that the flywheel performs both the functions of a flywheel and a front housing cover. Furthermore, the mass of the flywheel is increased by the components connected to it in a rotationally fixed manner, which increases its moment of inertia to the desired extent. Furthermore, in order to reduce the weight of the entire device, it is also preferred to reduce the mass of the actual flywheel, which is compensated by the mass of the housing.

[0018] The first sub-clutch and the second sub-clutch are arranged one after another along the rotation axis, and the first pressure plate and the second pressure plate arranged between the first clutch disc and the second clutch disc are each disc-shaped and oriented coaxially with the rotation axis. In order to engage or disengage the sub-clutch, the first pressure plate and the second pressure plate can each be actuated by means of a first actuating rod or a second actuating rod. The term "disengagement in the non-actuated state" means that the sub-clutch is disengaged when the associated actuating rod is not actuated, that is, no actuating force is applied, that is, there is no friction connection between the friction pairs of the sub-clutches. Press-actuation means that when actuated, the associated actuating rod presses one of the elements of the sub-clutch towards the other element, that is, applies a force, which is used to displace the components of the sub-clutch so as to produce a friction connection.

[0019] The first and second clutch plates are components that rotate relative to and within the housing, and each has a friction portion formed radially on its outer surface. Preferably, the housing peripherally surrounds at least the first and second clutch plates and the first and second pressure plates, coaxially with the axis of rotation. Due to the friction portion, when the clutch is engaged, the first and second clutch plates contact the friction surface of the flywheel or the friction surface of the housing. Once the friction connection is established, torque is transmitted to the first or second clutch plates via the housing protrusion or the flywheel. The housing protrusion is a region that is directly or indirectly connected to the housing. This region is designed to serve as an abutment for a return spring and securely holds the end of the return spring, located in or on the housing protrusion, relative to the rest of the housing.

[0020] In order to achieve actuation of the first sub-clutch or the second sub-clutch, the first actuating rod is preferably operatively connected to the first pressure plate by means of a first transmission element, and the second actuating rod is operatively connected to the second pressure plate by means of a second transmission element. The task of the first actuating rod and the second actuating rod is to transmit the compressive or tensile forces applied to the first actuating rod or the second actuating rod to the first pressure plate or the second pressure plate. Preferably, the first transmission element and / or the second transmission element is designed as one / more eyebolts. An eyebolt is a bolt which has, for example, a ring at one end of the bolt for accommodating a bearing pin and a thread at the other end of the bolt. In principle, the first transmission element and the second transmission element are not limited to an eyebolt design.

[0021] Preferably, the first transmission element and the first pressure plate are operatively connected to one another at least indirectly via a shaped element, and the second transmission element and the second pressure plate are operatively connected to one another at least indirectly via a further shaped element, and furthermore, the shaped element and the further shaped element are preferably designed as nuts and / or shoulders on the first transmission element and / or the second transmission element. Particularly preferably, a first spring element is arranged between the shaped element and the first pressure plate, wherein a second spring element is arranged between the further shaped element and the second pressure plate. The first and second spring elements are each preferably formed coaxially with respect to the bolted portion of the first and second transmission elements. The first spring element bears at one end on the first pressure plate and at the other end on the shaped element, while the second spring element bears at one end on the second pressure plate and at the other end on the further shaped element. The first and second spring elements are designed to dampen actuation forces and compensate for sudden actuation during engagement of the sub-clutch. In addition to supporting the first and second spring elements, the shaped elements are also designed to lift the first and second pressure plates off the first and second clutch plates during the disengagement process and to create an air gap between the first and second clutch plates and the flywheel or housing protrusion.

[0022] Preferably, the first actuating lever is actuated by pushing by an actuating device arranged coaxially with the axis of rotation, and the second actuating lever is actuated by pulling by the actuating device. Therefore, the actuating directions, i.e. the directions for bringing the sub-clutches into engagement, are oriented in antiparallel relation to each other. Therefore, only one sub-clutch can be engaged at a time while the other sub-clutch is disengaged, since the engagement of one sub-clutch causes the disengagement of the other sub-clutch. This means that the dual clutch has three position states, i.e. a first state in which the first sub-clutch is engaged and the second sub-clutch is disengaged, a second state in which the first sub-clutch is disengaged and the second sub-clutch is engaged, and a third state in which the two sub-clutches are normally disengaged and the dual clutch does not transmit any torque.

[0023] Preferably, the actuating device includes a first actuating bearing and a second actuating bearing, which are arranged coaxially with the axis of rotation. Thus, the first and second actuating bearings are components of the actuating device. The actuating device is mounted coaxially with the axis of rotation and is movable along the axis of rotation. Furthermore, the actuating device is designed with two bearing seats for the first and second actuating bearings, which are fixedly or partially locked in a rotationally fixed manner in the actuating device.

[0024] Furthermore, a reversing transmission is proposed, which includes a dual clutch as described herein. The reversing transmission is preferably used in motor vehicles, in particular agricultural machinery. The details and advantages disclosed for the dual clutch can be transferred and applied to the reversing transmission, and vice versa. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The present invention and the technical field are explained in more detail below with reference to the accompanying drawings. It should be noted that the present invention is not intended to be limited to the exemplary embodiments shown. In particular, unless otherwise explicitly stated, sub-aspects of the subject matter explained in the drawings may also be extracted and these sub-aspects may be combined with other components and knowledge from this specification and / or the drawings. In particular, it should be noted that the drawings shown and, in particular, the proportions are merely schematic in nature. The same reference numerals indicate the same objects, so that explanations from other drawings may also be used where applicable. In the drawings:

[0026] Figure 1 shows a schematic cross-section of a dual clutch according to the present invention;

[0027] Figure 2 A schematic diagram showing a first sub-clutch of the dual clutch according to the present invention; and

[0028] Figure 3 A schematic diagram of the second sub-clutch of the dual clutch created according to the present invention is shown. DETAILED DESCRIPTION

[0029] Figure 1A schematic cross-section of a dual clutch 1 for a powershift transmission is shown. The dual clutch comprises a first component clutch 1a and a second component clutch 1b. The dual clutch 1 includes a flywheel 5, which is coaxially connected to a third transmission shaft 4, either rotationally fixed or rotatably, about its rotational axis A. The flywheel is also connected to a circumferential housing 10 at its radially outer peripheral end. The third transmission shaft 4 is preferably designed to directly connect a drive (not shown), preferably an engine, to a secondary drive shaft (also not shown). The first transmission shaft 2, designed as a hollow shaft, is rotatable coaxially with the third transmission shaft 4 on its outer peripheral surface and is mounted for axial displacement along the rotational axis A. At its end facing the flywheel 5, the first transmission shaft 2 is rotationally fixedly connected to a first clutch plate 6, which points radially outward. The first transmission shaft 2 is designed to shift into a forward gear via the first clutch plate 6. Furthermore, the second transmission shaft 3 is mounted coaxially with the first and third transmission shafts 2, 4, on its outer peripheral surface so as to be rotatable and axially displaceable along the rotational axis A. The second transmission shaft 3 is shorter than the first transmission shaft 2 in the direction of the flywheel 5. On the other hand, the second transmission shaft 3 is designed to be shifted into reverse gear via a second clutch plate 7.

[0030] At the end of the second transmission shaft 3 facing the first clutch plate 6, the second transmission shaft 3 is connected in a rotationally fixed manner to a second clutch plate 7 facing radially outward, wherein the first clutch plate 6 and the second clutch plate 7 have the same radial extension. A first pressure plate 40 and a second pressure plate 50 are arranged between the first clutch plate 6 and the second clutch plate 7. The first pressure plate 40 and the second pressure plate 50 are each disc-shaped and arranged coaxially with the axis of rotation A. The first pressure plate 40 and the second pressure plate 50 have an outward radial extension and are each provided with an inwardly facing through-opening 42, 52 toward the axis of rotation A, through which the first transmission shaft 2, the second transmission shaft 3, and the third transmission shaft 4 extend.

[0031] The first actuating lever 20 and the second actuating lever 30 are each pivotally mounted on the housing 10 at one end, with each extending radially inward from a pivot bearing 21, 31 on the housing 10 toward the rotation axis A. The radially inwardly facing ends of the first actuating lever 20 and the second actuating lever 30 are pivotally mounted in the direction of the rotation axis A and about the pivot bearings 21, 31. The first actuating lever 20 bears with its side facing away from the flywheel 5 against the side of the first actuating bearing 80 facing toward the flywheel 5. Conversely, the second actuating lever 30 bears with its side facing toward the flywheel 5 against the side of the second actuating bearing 90 facing away from the flywheel 5. The first bearing 80 and the second actuating bearing 90 are components of an actuating device 100. The actuating device 100 is mounted coaxially with the rotation axis A so as to be movable along the rotation axis. Furthermore, the actuating device is designed with two bearing seats for a first actuating bearing 80 and a second actuating bearing 90, wherein the first actuating bearing 80 and the second actuating bearing 90 are fixedly or partially mounted in a rotationally fixed manner in the actuating device 100. The actuating device 100 is designed to engage and disengage the first clutch 1a and the second component clutch 1b and is therefore configured to actuate the dual clutch 1.

[0032] The first actuating bearing 80 and the second actuating bearing 90 are each designed as a rolling bearing, so that they each have an annular shape. The first actuating bearing 80 and the second actuating bearing 90 are mounted coaxially with the rotation axis A. The first actuating bearing 80 and the second actuating bearing 90, each designed as a rolling bearing, are each provided with an inner ring and an outer ring. The outer ring of the first actuating bearing 80 is supported on the first actuating rod 20, and the outer ring of the second actuating bearing 90 is supported on the second actuating rod 30.

[0033] Figure 1 Only one first actuating rod 20 and one second actuating rod 30 are shown in FIG. 1 , but a plurality of first actuating rods 20 and second actuating rods 30 are provided on the circumference of the housing 10 .

[0034] Another pivot bearing 22 is radially arranged on the inner side of the first actuating lever 20, opposite the pivot bearing 21. A first transmission element 23 is mounted at one end on the other pivot bearing 22. The first transmission element 23 extends from the other pivot bearing 22, approximately parallel to the rotation axis A, in the direction of the flywheel 5. The first transmission element 23 is designed as an eyebolt, with the eye forming a receptacle for the other pivot bearing 22. The end of the first transmission element 23 facing away from the eye is designed as a bolt and is provided with an external thread. Furthermore, a radial extension of the bolt, in the form of a shoulder 24, is formed between the threaded portion of the bolt and the eye. A first spring element 70, formed coaxially with the bolt portion of the first transmission element 23, bears against the shoulder 24 at one end, in the direction of the flywheel 5. The other end of the first spring element 70 bears against the first pressure plate 40. On the side of the first pressure plate 40 facing away from the first spring element 70, a shaped element 41, in the form of a nut, is screwed onto the threaded portion of the transmission element 23. The first spring element 70 is designed to dampen the actuation force during engagement of the first component clutch 1a and compensate for sudden actuation. Furthermore, the first spring element 70 limits the corresponding pressing force of the first component clutch 1a. Furthermore, the shaped element 41 is designed to lift the first pressure plate 40 from the first clutch plate 6 during the disengagement process and create an air gap between the first clutch plate 6 and the flywheel 5.

[0035] The first pressure plate 40 is formed with a friction surface 43 for the friction portion 8 of the first clutch disc 6 on one side thereof facing the first clutch disc 6. In addition, the flywheel 5 also has a friction surface 5a for the friction portion 8 of the first clutch disc 6 on the side thereof facing the first clutch disc 6.

[0036] Another pivot bearing 32 is radially arranged on the inner side of the second actuating lever 30, opposite the pivot bearing 31. A second transmission element 33 is mounted at one end of the other pivot bearing 32. The second transmission element 33 also extends from the other pivot bearing 32, approximately parallel to the rotation axis A, in the direction of the flywheel 5. Similar to the first transmission element 23, the second transmission element 33 is designed as an eyebolt, with the eye forming a receptacle for the other pivot bearing 32. The end of the second transmission element 33 facing away from the eye is designed as a bolt and is provided with an external thread. Another shaped element 51, in the form of a nut, is screwed onto the threaded portion of the transmission element 33 facing the flywheel 5. Furthermore, another shoulder 34 is formed on the bolt portion of the second transmission element 33 on the side of the second pressure plate 50 facing away from the flywheel 5. One end of a second spring element 71 is supported on the other shaped element 51, while the other end of the second spring element 71 is supported on the second pressure plate 50. In the second component clutch 1b, the second spring element 71 is also designed to dampen the actuation force during engagement of the second component clutch 1b and compensate for sudden actuation. Furthermore, the second spring element 71 limits the pressing force of the second component clutch 1b. However, another shaped element 51 on the side of the second pressure plate 50 facing away from the flywheel 5 is designed to lift the second pressure plate 50 from the second clutch disc 6 during the disengagement process and create an air gap.

[0037] The second pressure plate 50 is designed so that the side facing the second clutch disc 7 serves as a friction surface 53 for the friction portion 9 of the second clutch disc 7. What has been said about the first and second actuating levers 20 and 30 also applies to the first and second transmission elements 23 and 33 and the shaped elements 41, 51, that is, although Figure 1 Only two actuating rods 20 , 30 are shown, but a plurality of transmission elements 23 , 33 corresponding to the number of rod elements 20 , 30 are distributed over the circumference of the housing 10 .

[0038] Depending on the designation "first" or "second," the first component clutch 1a is formed at least by the flywheel 5, the first clutch disc 6, the first pressure plate 40, the first transmission element 23, the first actuating lever 20, and the actuating device 100. The second component clutch 1b is correspondingly formed at least by the housing protrusion 11, the second clutch disc 7, the second pressure plate 50, the second transmission element 33, the second actuating lever 30, and the actuating device 100. The actuating device 100 is therefore part of both the first component clutch 1a and the second component clutch 1b.

[0039] Figure 2A schematic diagram of the first sub-clutch 1a of the dual clutch 1 according to the present invention is shown, with the second sub-clutch 1b concealed to clarify the device's mode of operation. As explained in the preceding description, the first sub-clutch 1a is formed by at least the element labeled "first," and the second sub-clutch 1b is formed by at least the element labeled "second."

[0040] To create a friction connection between the first clutch plate 6 and the friction surface 5a of the flywheel 5 or to engage the first clutch component 1a of the dual clutch 1, an actuating force is transmitted by the actuating device 100 in the direction of the flywheel 5 in a first actuating direction B to the first actuating lever 20. A first transmission element 23, in the form of an eyebolt, transmits a force in the form of pressure and a distance corresponding to the lever ratio to the first pressure plate 40. The first pressure plate 40 follows the lever movement and moves in the direction of the friction surface 5a of the flywheel 5. As a result, the first clutch plate 6 is clamped between the friction surface 43 of the first pressure plate 40 and the friction surface 5a of the flywheel 5, and torque is frictionally transmitted from the third transmission shaft 4, which is rotationally fixedly connected to the flywheel 5, to the first transmission shaft 2. If a pressing force is applied by the first actuating lever 20 to the first pressure plate 40 to engage the first component clutch 1a, this pressure is transmitted in a damped manner by the first spring element 70. However, if a tensile force acts on the first pressure plate 40 to disengage the first component clutch 1 a , the tensile force is applied directly and undamped to the first pressure plate 40 .

[0041] Figure 3 A schematic diagram of the second component clutch 1b of the dual clutch 1 according to the present invention is shown, with the first component clutch 1a now hidden to clarify the device's mode of operation. To create a friction connection between the second clutch plate 7 and the friction surface 13 of the housing projection 11, or to engage the second component clutch 1b of the dual clutch 1, a tensile force, i.e., a force in a second actuation direction C opposite to the direction of the flywheel 5, acts on the actuation device 100. Consequently, the second actuation direction C is oriented opposite to the actuation direction B during the engagement process of the first component clutch 1a.

[0042] In the second sub-clutch 1b, force and distance are also transmitted by the second transmission element 33 to the second pressure plate 50 according to the lever ratio. Contrary to the first sub-clutch 1a, the second pressure plate 50 is pulled in the direction of the second actuating lever 30. Consequently, the second pressure plate 50 follows the lever movement of the second actuating lever 30 and moves away from the flywheel 5. Consequently, the second clutch plate 7 is pulled a certain distance against the interior of the housing 10, or specifically against the housing protrusion 11. Due to the transmitted actuating force, the second clutch plate 7 is clamped between the friction surface 53 of the second pressure plate 50 and the friction surface 13 of the housing protrusion 11. This creates a friction effect between the second clutch plate 7 and the housing protrusion 11, causing the second sub-clutch 1b to engage and enabling torque to be transmitted from the housing 10 connected to the flywheel 5 to the second transmission shaft 3. If a tensile force is applied to the second pressure plate 50 by the second actuating lever 30 to engage the second sub-clutch 1b, this force is transmitted in a damped manner by the second spring element 71. However, if the second component clutch 1 b is to be disengaged, a compressive force acts on the second pressure plate 50 , and this pressing force is applied directly and undamped to the second pressure plate.

[0043] Therefore, the first actuation direction B and the second actuation direction C are oriented in opposite directions parallel to each other in order to switch the sub-clutches 1a, 1b to the engaged state or the disengaged state. Therefore, only one sub-clutch 1a, 1b can be engaged at a time while the other sub-clutch 1a, 1b is disengaged, because due to the connection of the first actuation bearing 80 to the second actuation bearing 90, the engagement of one sub-clutch 1a, 1b will result in the disengagement of the other sub-clutch 1a, 1b. Figure 2 and Figure 3 As can be seen, or as can be seen from Figure 1 As can be seen from the combination of , the result is that the dual clutch 1 has three position states. Specifically, there is a first state in which the first sub-clutch 1a is engaged and the second sub-clutch 1b is disengaged; a second state in which the first sub-clutch 1a is disengaged and the second sub-clutch is engaged; and a third state in which the two sub-clutches 1a and 1b are normally disengaged and the dual clutch 1 does not transmit any torque.

[0044] Thus, by means of the actuating device 100, the two actuating levers 20, 30, and thus the two component clutches 1a, 1b, can be actuated by moving the actuating device 100 in a first actuating direction B, thereby actuating the first component clutch 1a, i.e., engaging the first component clutch 1a, while the second component clutch 1b is simultaneously disengaged, or actuating the second component clutch 1b in a second actuating direction C, while the first component clutch 1a is simultaneously disengaged. Because both component clutches 1a, 1b are designed to be normally disengaged, the actuating device 100 ensures that at most one component clutch 1a, 1b is engaged at any given time, and never both component clutches 1a, 1b are engaged simultaneously. The actuating device 100 is moved in the direction of the rotational axis A, i.e., in the first actuating direction B or the second actuating direction C, via corresponding actuators (not shown) to initiate the corresponding engagement and disengagement processes. The actuators can preferably be hydraulic actuators.

[0045] Reference Signs List

[0046] 1 dual clutch

[0047] 1a First sub-clutch

[0048] 1b Second sub-clutch

[0049] 2 First drive shaft

[0050] 3 Second drive shaft

[0051] 4 Third drive shaft

[0052] 5 Flywheel

[0053] 5a Friction surface

[0054] 6 First clutch plate

[0055] 7 Second clutch plate

[0056] 8 Friction part of the first clutch disc

[0057] 9 Friction part of the second clutch disc

[0058] 10 Housing

[0059] 11 Housing protrusion

[0060] 13 Friction Surface

[0061] 20 First actuator rod

[0062] 21 Pivot bearing

[0063] 22 Another pivot bearing

[0064] 23 First transmission element

[0065] 24 Shoulders

[0066] 30 Second actuating lever

[0067] 31 Pivot bearing

[0068] 32 Another pivot bearing

[0069] 33 Second transmission element

[0070] 34 Shoulders

[0071] 40 First Pressure Plate

[0072] 41 forming elements

[0073] 42 through opening

[0074] 43 Friction Surface

[0075] 50 Second Pressure Plate

[0076] 51 forming elements

[0077] 52 through opening

[0078] 53 friction surface

[0079] 70 first spring element

[0080] 71 Second spring element

[0081] 80 First Actuator Bearing

[0082] 90 Second actuating bearing

[0083] 100 Actuator

[0084] A. Rotation axis

[0085] B. First moving direction

[0086] C Second actuation direction.

Claims

1. A dual clutch (1) for a powershift transmission having an axis of rotation (A), characterized in that The dual clutch comprises a first sub-clutch (1a) and a second sub-clutch (1b), The first sub-clutch (1a) comprises, in the direction of the rotation axis (A), a first pressure plate (40), a flywheel (5), and a first clutch disc (6) located between the first pressure plate and the flywheel, wherein the first pressure plate (40) and the first clutch disc (6) are mounted so as to be displaceable along the rotation axis (A). wherein the second sub-clutch (1b) comprises a second pressure plate (50) in the direction of the rotation axis (A), a housing protrusion (11) fixedly connected to the housing (10), and a second clutch disc (7) located between the second pressure plate and the housing protrusion, wherein the second pressure plate (50) and the second clutch disc (7) are mounted in a displaceable manner along the rotation axis (A), and the dual clutch further comprises an actuating system having a first actuating rod (20) for actuating the first sub-clutch (1a) and a second actuating rod (30) for actuating the second sub-clutch (1b), wherein the first sub-clutch (1a) and the second sub-clutch (1b) are disengaged in an unactuated state, wherein the actuation of the first actuating rod (20) occurs by pushing, and wherein the actuation of the second actuating rod (30) occurs by pulling.

2. The dual clutch (1) according to claim 1, characterized in that The actuation of the first actuating rod (20) is achieved by pushing by an actuating device (100) arranged coaxially with the rotation axis (A), wherein the actuation of the second actuating rod (30) is achieved by pulling by the actuating device (100).

3. The dual clutch (1) according to claim 2, characterized in that The actuating device (100) comprises a first actuating bearing (80) and a second actuating bearing (90), wherein the first actuating bearing (80) and the second actuating bearing (90) are arranged coaxially with the rotation axis (A).

4. The dual clutch (1) according to claim 1, characterized in that The housing (10) peripherally surrounds at least the first clutch disc (6) and the second clutch disc (7) and the first pressure plate (40) and the second pressure plate (50) coaxially with the rotation axis (A).

5. The dual clutch (1) according to claim 1 or 2, characterized in that The first actuating lever (20) is operatively connected to the first pressure plate (40) by means of a first transmission element (23), wherein the second actuating lever (30) is operatively connected to the second pressure plate (50) by means of a second transmission element (33).

6. The dual clutch (1) according to claim 5, characterized in that The first transmission element (23) and / or the second transmission element (33) are designed as eyebolts.

7. The dual clutch (1) according to claim 5, characterized in that: The first transmission element (23) and the first pressure plate (40) are operatively connected to each other at least indirectly via a shaped element (41), and the second transmission element (33) and the second pressure plate (50) are operatively connected to each other at least indirectly via a further shaped element (51).

8. The dual clutch (1) according to claim 7, characterized in that The shaped element (41) and the further shaped element (51) are designed as nuts and / or shoulders on the first transmission element (23) and / or the second transmission element (33).

9. The dual clutch (1) according to claim 7, characterized in that A first spring element (70) is arranged between the shaped element (41) and the first pressure plate (40), wherein a second spring element (71) is arranged between the further shaped element (51) and the second pressure plate (50).

10. A reversing transmission, characterized in that: The reversing transmission comprises a dual clutch (1) according to any one of claims 1-9.

Images