DE102018120846A1 - Hybrid module with disconnect clutch - Google Patents

Abstract

The invention relates to a hybrid module (1) for a drive train (2) of a motor vehicle, with a disconnect clutch (3), the disconnect clutch (3) furthermore on the input side being a one or two mass flywheel that can be rotatably coupled to a crankshaft (4) of an internal combustion engine Flywheel (5) and on the output side with a rotor (6) of an electric motor (7) can be rotatably coupled or rotatably coupled, and an actuating device (8) which adjusts the separating clutch (3) between its engaged position and its disengaged position, the separating clutch (3) is designed as a normally engaged clutch.

Description

The invention relates to a hybrid module for a (hybrid) drive train of a motor vehicle, such as a car, truck, bus or other commercial vehicle, with a disconnect clutch.

The challenges for designing hybrid modules lie in particular in the fact that, in the case of concepts without a damper, the resulting alternating torques (up to 1600 Nm) have to be transmitted without slip / low slip via the clutch arrangement / separating clutch.

It is therefore the object of the present invention to provide a hybrid module which is intended to ensure that the torque is transmitted as slip-free as possible even in the case of high alternating torques.

According to the invention, this is solved by the subject matter of claim 1. A hybrid module for a drive train of a motor vehicle is hereby provided with a disconnect clutch, the disconnect clutch furthermore having on the input side a flywheel which can be rotatably coupled to a crankshaft of an internal combustion engine and is designed as a single or dual-mass flywheel and can be rotatably coupled or rotatably coupled on the output side to a rotor of an electric motor. The hybrid module also has an actuating device which adjusts the separating clutch between its engaged position and its disengaged position. The separating clutch is also designed as a normally engaged clutch. This enables hybridized drive trains to be operated with a comparatively narrow installation space and high nominal torques (> 700Nm).

Further advantageous designs are claimed with the subclaims and explained in more detail below.

Accordingly, it is also advantageous if the separating clutch is designed as a friction clutch in the form of a single-disk clutch or a multiple-disk clutch, particularly preferably as a friction plate clutch. As a result, the separating clutch is particularly efficient as a friction clutch.

If the actuating device has a concentric clutch release (CSC / "Concentric Slave Cylinder") with an annular piston or several pistons (multi-piston release), which clutch release is preferably received on a bearing plate, the assembly of the hybrid module is further simplified.

In this context, it is alternatively also advantageous if the releaser is supported / received on a housing of the internal combustion engine, on an input shaft or other housing components.

Furthermore, it is advantageous in this context if the actuating device with its clutch release is arranged on an engine side (ie on a side facing the internal combustion engine) of the disconnect clutch or a transmission side / a rotor side (ie on a side facing a transmission / the rotor) of the disconnect clutch is. The clutch release is further preferably designed as a slave cylinder for a hydrostatic device or the like.

Furthermore, it is advantageous if, in addition to the flywheel, there is a clutch cover in the separating clutch, which is connected to the flywheel / fastened to the flywheel. It has proven to be particularly suitable here if the flywheel and the cover are connected to one another by means of a screw connection or by means of a curling.

The separating clutch is further preferably non-rotatably connected on the output side to an intermediate shaft, the intermediate shaft being further rotationally connected to the rotor of the electric motor, which is also part of the hybrid module.

Depending on the intended use, several friction surfaces (two / four) can be provided in the separating clutch, although more than four friction surfaces can also be implemented in principle.

Furthermore, it has proven to be advantageous if a damper is integrated directly on / in the flywheel or a clutch disc of the separating clutch, the damper preferably being arranged radially within a plurality of friction surfaces of the separating clutch.

It is also advantageous if the damper is designed as an arc spring damper (analogous to a dual-mass flywheel) and / or running dry. As an alternative to the position of the damper arranged radially inside the friction surfaces of the separating clutch, it is in principle also possible to position it radially outside the separating clutch, i.e. to be arranged radially outside the friction surfaces.

In other words, according to the invention, a clutch is designed in a special way, the clutch being provided as part of a hybrid module.

The invention will now be explained below with reference to figures in connection with various exemplary embodiments.

• 1 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem ersten Ausführungsbeispiel, wobei eine Trennkupplung des Hybridmoduls detaillierter veranschaulicht ist,
• 2 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem zweiten Ausführungsbeispiel,
• 3 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem dritten Ausführungsbeispiel,
• 4 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem vierten Ausführungsbeispiel,
• 5 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem fünften Ausführungsbeispiel,
• 6 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem sechsten Ausführungsbeispiel,
• 7 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem siebten Ausführungsbeispiel,
• 8 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem achten Ausführungsbeispiel, sowie
• 9 eine Längsschnittdarstellung eines erfindungsgemäßen, schematisch dargestellten Hybridmoduls nach einem neunten Ausführungsbeispiel.

Show it:

• 1 2 shows a longitudinal sectional view of a hybrid module according to the invention, shown schematically, according to a first exemplary embodiment, a separating clutch of the hybrid module being illustrated in more detail,
• 2 2 shows a longitudinal sectional illustration of a hybrid module according to the invention, shown schematically, according to a second exemplary embodiment,
• 3 2 shows a longitudinal sectional illustration of a hybrid module according to the invention, shown schematically, according to a third exemplary embodiment,
• 4 2 shows a longitudinal sectional view of a hybrid module according to the invention, shown schematically, according to a fourth exemplary embodiment,
• 5 2 shows a longitudinal sectional illustration of a hybrid module according to the invention, shown schematically, according to a fifth exemplary embodiment,
• 6 2 shows a longitudinal sectional view of a hybrid module according to the invention, shown schematically, according to a sixth exemplary embodiment,
• 7 2 shows a longitudinal sectional illustration of a hybrid module according to the invention, shown schematically, according to a seventh exemplary embodiment,
• 8th a longitudinal sectional view of a hybrid module according to the invention, shown schematically according to an eighth embodiment, and
• 9 a longitudinal sectional view of a hybrid module according to the invention, shown schematically according to a ninth embodiment.

The figures are only schematic in nature and serve only to understand the invention. The same elements are provided with the same reference symbols. The different features of the different exemplary embodiments can also be freely combined with one another.

In 1 is a hybrid module according to the invention 1 shown schematically according to a first embodiment. The hybrid module 1 is already in this version in a partially shown drive train 2 a motor vehicle used. A detailed clutch shown 3 of the hybrid module 1 is between a crankshaft 4 an internal combustion engine and a transmission 13 of the drive train 2 arranged. On one of the gears 13 facing side of the disconnect clutch 3 is an electric motor 7 of the hybrid module 1 arranged. Also the disconnect clutch 3 Actuating actuator shown in more detail 8th is on the gearbox 13 facing side of the disconnect clutch 3 arranged.

The electric motor 7 of the hybrid module 1 is with its rotor designed as an internal rotor 6 with an intermediate shaft 11 non-rotatably connected. The electric motor 7 and therefore also a stator 14 of the electric motor 7 is in a housing of the hybrid module, not shown here 1 integrated / included. The stator 14 is firmly accommodated in this housing. The rotor 6 is about a central axis of rotation 15 which is also an axis of rotation 15 the disconnect clutch 3 as well as the intermediate shaft 11 forms, rotatably arranged. The rotor 6 is in a typical manner with a transmission shaft (transmission input shaft) of the transmission, which is also not shown here for the sake of clarity 13 rotationally coupled or rotationally couplable, with further preference between the rotor 6 and the gear shaft at least one or more clutches, for example in the form of a double clutch, are arranged.

The disconnect clutch 3 points according to 1 a disc-shaped flywheel 5 on what flywheel 5 is basically implemented as a single-mass flywheel. The disconnect clutch 3 is implemented in this version as a single-disc friction clutch. So the flywheel 5 with a lid 12 / Clutch cover of the disconnect clutch 3 non-rotatably connected. On this lid 12 is a pressure plate 16 relatively displaceable along the axis of rotation 15 arranged. The pressure plate 16 is about several leaf springs combined into leaf spring assemblies 17 on the lid 12 supported. The leaf springs 17 are essentially aligned in the circumferential direction and in the axial direction between the pressure plate 16 and the lid 12 clamped that they have an axial preload depending on the direction of rotation of the flywheel 5 relative to a clutch disc 18 the disconnect clutch 3 produce. The clutch disc 18 the disconnect clutch 3 is non-rotatable with the intermediate shaft 11 connected.

To actuate the disconnect clutch 3 is the pressure plate 16 with a disc spring 19 operatively connected. The disc spring 19 is on the lid 12 pivoted. The disc spring acts on a radially inner area 19 a hydraulic clutch release 9 an actuator 8th adjusting one. The clutch release 9 is a concentric clutch slave cylinder / clutch release 9 implemented. An actuator housing 20 of the releaser 9 is on a bearing plate 10 firmly supported / supported. The end shield 10 is in operation in a typical manner with a housing, preferably the housing of the hybrid module 1 connected.

In this version, the lid 12 and the flywheel 5 over several screws 21 connected with each other.

The disconnect clutch 3 is implemented as a normally engaged / closed clutch. The disc spring 19 is therefore basically in its initial position on the lid 12 supported that the pressure plate 16 against the clutch disc 18 and this in turn against the flywheel 5 , forming a frictional connection between the clutch disc 18 and the flywheel 5 , presses. To disengage the disconnect clutch 3 , ie for moving the clutch 3 from its engaged to its disengaged position, the actuator acts accordingly 8th in an activated state on the disc spring 19 on.

The disconnect clutch 3 is in this version directly over the flywheel 5 on the crankshaft 4 supported and thus stored. The flywheel 5 is on the front side of the crankshaft 4 screwed and over an axial extension 36 the crankshaft 4 in the radial direction relative to the crankshaft 4 supported. It can be seen that the leaf springs 17 in the radial direction at the same height with several between the clutch disc 18 and the flywheel 5 / the pressure plate 16 trained friction surfaces 22 is arranged. Thus there is also talk of arranging the leaf springs 17 within the friction surfaces 22 ,

It should also be noted that the releaser 9 is preferably implemented as a hydrostatic actuator or has a hydrostatic actuator.

In connection with the 2 to 9 then further preferred exemplary embodiments are shown in principle, but the basic structure and the function of the hybrid module 1 correspond to the first embodiment. For the sake of brevity, only the differences from the first exemplary embodiment or between the individual exemplary embodiments are described.

In contrast to the first embodiment according to 1 is in the second embodiment 2 the clutch disc 18 with a damper 23 fitted. The damper 23 is located radially inside the friction surfaces 22 , ie a friction lining 24 the clutch disc 18 , The damper 23 is realized as an arc spring damper and in a carrier part 25 the clutch disc 18 integrated. The carrier part 25 is the component that the friction linings 24 to its radial outside and a hub to a radial inside 26 , the rotatably with the intermediate shaft 11 is further connected.

The further structure of the in 2 separating clutch shown 3 corresponds to the design of the disconnect clutch 3 of the hybrid module 1 the 1 , Accordingly, the disconnect clutch 3 indented again normally. Storage of the disconnect clutch 3 takes place via the flywheel 5 on the crankshaft 4 , Also, the disconnect clutch 3 / the lid 12 with the flywheel 5 screwed. There are also the leaf springs 17 within the friction surface 22 , It is also operated by a CSC 9 (preferably with a hydrostatic actuator); the CSC 9 is still on a separate sign 10 arranged.

Also in the third embodiment of the 3 is the disconnect clutch 3 realized as a normally engaged clutch. Compared to the 1 is a damper 23 additionally in the flywheel 5 arranged. The flywheel 5 is therefore no longer implemented as a single-mass flywheel, but as a dual-mass flywheel. The damper 23 is like in 2 , realized as a bow spring damper. The damper 23 is on the inside, ie radially inside the friction surfaces 22 arranged. The bearing of the disconnect clutch 3 continues via the flywheel 5 on the crankshaft 4 , Also the clutch 3 / the lid 12 with the flywheel 5 screwed. The leaf springs 17 are still within the friction surface 22 arranged. It is operated by a CSC 9 (preferably with hydrostatic actuator), the CSC 9 on a separate sign 10 is arranged.

A further preferred embodiment is with 4 illustrated. The fourth embodiment of the 4 shows a flywheel designed as a dual mass flywheel 5 , A primary page 27 of the flywheel 5 is directly non-rotatable on the crankshaft 4 appropriate. A secondary page 28 of the flywheel 5 is over several bow springs 29 / Leaf springs relative to the primary side 27 rotatable within a limited range of rotation angles and supported in a resilient manner. The secondary side 28 at the same time forms an outer disk carrier 30 the separating clutch designed as a multi-plate clutch / friction disk clutch 3 out. On the outer disk carrier 30 are several first friction plates protruding inwards in the radial direction 31 arranged. The first friction plates 31 are rotatably and relatively displaceable in the axial direction on the outer disk carrier 30 arranged. Several second friction plates 32 the disconnect clutch 3 are rotatably and relatively displaceable in the axial direction on an inner disk carrier 33 added, the inner disk carrier 33 again rotatably with the intermediate shaft 11 is further connected. The first and second friction plates 31 . 32 are arranged alternately next to each other in the axial direction and at the same height in the radial direction, forming a large number of friction surfaces 22 ,

The disconnect clutch 3 is still with an actuator 8th operable, this actuator 8th again the clutch release shown schematically 9 in the form of a concentric slave cylinder / CSCs. Furthermore, there is a rigid pressure pot instead of the previously used disc spring 34 used the adjusting on the disconnect clutch 3 acts. A bias spring 35 (also implemented as a plate spring) acts on the friction plates 31 . 32 so shifting that they are in an unactuated position by the actuator 8th are frictionally connected to each other. According to this, the disconnect clutch 3 still implemented as a normally engaged clutch. The pressure pot 34 passes through the friction plates 31 . 32 in the axial direction, to one through the biasing spring 35 supported first friction plate 31 to be in contact.

It can also be seen that the secondary side 28 , ie the outer disk carrier 30 , also on the extension 36 the crankshaft 4 directly via a roller bearing 37 is supported.

This is the disconnect clutch 3 the 4 also normally closed with a disc spring in front 35 realized. The disconnect clutch 3 has a plate design (first and second friction plates 31 . 32 ) on the radially inside the dual mass flywheel, ie the arc springs 29 of the flywheel 5 , is arranged. The bearing of the disconnect clutch 3 including flywheel 5 takes place via the flywheel 5 even with a bearing on the primary side and on the secondary side on the crankshaft 4 , The actuation continues to be carried out by a CSC 9 (preferably with hydrostatic actuator), with the CSC on a separate bearing plate 10 is arranged. Disengaging the disconnect clutch 3 is preferably done with a pressure pot 34 by the outer plate pack, ie by the first friction plates 31 , protrudes through and up to the disc spring 35 on an opposite side of the actuation, acts on it accordingly.

Combined with 5 is a fifth embodiment of the hybrid module according to the invention 1 shown. In contrast to the embodiment of the 1 is in turn a flywheel designed as a single-mass flywheel 5 no longer has a screw connection to the lid 12 connected, but via a roller. The lid 12 is therefore on the flywheel 5 on a radially outside of the friction surfaces 22 arranged area attached via a roller.

The disconnect clutch 3 is again indented normally. The bearing of the disconnect clutch 3 takes place via the flywheel 5 on the crankshaft 4 , The leaf springs 17 are still within the friction surface 22 arranged. It is operated by the CSC 9 (preferably with hydrostatic actuator), the CSC 9 on a separate sign 10 is arranged.

The sixth embodiment according to 6 differs in terms of the actuator 8th from the first embodiment. The clutch release 9 is no longer just with an annular one around the axis of rotation 15 revolving piston 38 (as in the 1 to 5 ), but with several individual pistons distributed along a circumference 38 fitted. The clutch release 9 is consequently designed as a multi-piston release. Every piston 38 acts with a connecting bridge 39 on an actuation bearing 40 shifting which actuation bearing 40 again on the disc spring 19 acts to adjust / is supported on this.

The further construction in turn essentially corresponds to the first exemplary embodiment, so that the separating clutch 3 the clutch is still engaged normally 3 over the flywheel 5 on the crankshaft 4 the disconnect clutch 3 with the flywheel 5 is screwed, the leaf springs 17 within the friction surfaces 22 are arranged and actuated by a CSC 9 he follows. Preferably, the CSC 9 additionally a hydrostatic actuator. The clutch release 9 is still on a separate sign 10 arranged.

In 7 is a seventh embodiment of the hybrid module according to the invention 1 clearly visible. This seventh embodiment is relatively similar to the sixth embodiment of FIG 6 educated. The disconnect clutch 3 is therefore still indented / implemented normally. The bearing of the disconnect clutch 3 takes place via the flywheel 5 on the crankshaft 4 , The coupling 3 / the lid 12 is with the flywheel 5 screwed. The leaf springs 17 are within the friction surfaces 22 arranged. It is operated by a CSC 9 (preferably with hydrostatic actuator). The CSC is also 9 still implemented in multi-piston design, ie has several pistons distributed around the circumference 38 on. The clutch release 9 is now on a support camp 41 supported in the form of a ball bearing. The clutch release 9 is with its actuator housing 20 about the support bearing 41 on the central intermediate shaft 11 supported. The end shield 10 can thus be implemented significantly thinner in a typical manner, and is therefore implemented as a drag torque support. The drag torque support 10 is still with the bell bottom, ie preferably a transmission housing of the transmission 13 , further connected.

With 8th is an eighth embodiment of the hybrid module according to the invention 1 illustrated. In this context, compared to the first embodiment 1 to recognize that the actuator 8th with the clutch release 9 no longer on the rotor 6 facing side (rotor side) of the separating clutch 3 but on one of the rotor 6 the crankshaft 4 facing side (motor side) of the clutch 3 is arranged. Accordingly, the disc spring is also 19 on an axial side of the flywheel facing the internal combustion engine 5 arranged and no longer on a the rotor 6 axially facing side of the flywheel 5 , Furthermore, the flywheel 5 essentially realized in a pot shape and by means of an extension element 42 on the crankshaft 4 appropriate. The extension element 42 is realized essentially in the form of a sleeve / tube and has at least one, preferably a plurality of through holes distributed in the circumferential direction 43 on. Through every through hole 43 protrudes a screw 44 through and is on a flywheel 5 axially opposite side of the extension element 42 in the crankshaft 4 screwed.

The flywheel 5 is designed in a pot-like manner such that it extends from its radially inner region with which it is attached to the extension element 42 is applied, in the radial direction outward axially to the crankshaft 4 again extends. In a radially inside the flywheel 5 thus formed space 45 is at least partially the clutch release 9 added. A the actuator housing 20 receiving housing area, which is preferably directly an area of a housing of the internal combustion engine, is shown schematically in dashed lines.

Due to the arrangement of the actuator 8th as well as the disc spring 19 in comparison to 1 on another axial side of the flywheel 5 is also the pressure plate 16 acting in a different axial direction to the clutch disc 18 arranged. A counter plate 46 the disconnect clutch 3 is with the flywheel 5 screwed; the flywheel 5 forms the diaphragm spring 19 receiving lid 12 immediately. Between the counter plate 46 and the flywheel 5 are the pressure plate 16 as well as the clutch disc 18 arranged. The carrier part 25 the clutch disc 18 is also essentially pot-shaped and on its radial inside with the intermediate shaft 11 non-rotatably coupled. The leaf springs 17 are still radially outside the friction surfaces 22 arranged.

Accordingly, the clutch is also in the eighth embodiment 3 indented normally. The bearing of the disconnect clutch 3 now takes place via an extension element 42 on the crankshaft 4 (ie in the axial direction as well as in the radial direction under contact with the crankshaft 4 ). A counter plate 46 is with the flywheel 5 screwed. leaf springs 17 are now outside the friction surfaces 22 preferably arranged. It is operated by a CSC 9 (preferably with hydrostatic actuator).

The CSC 9 is now placed on the back of the engine. There is also a towing anchor 47 between the release bearing (operating bearing 40 ) in the CSC 9 and the disc spring 19 intended.

In 9 is finally a ninth embodiment of the hybrid module according to the invention 1 realized. This ninth embodiment is similar to the eighth embodiment. In contrast to the eighth embodiment, the separating clutch is 3 but now realized as a normally engaged / closed multi-plate clutch, namely a two-plate clutch. In addition to the counter plate 46 and the flywheel 5 is therefore an intermediate plate 48 available. The axially between the counter plate 46 and the flywheel 5 arranged intermediate plate 48 is radially outside via leaf springs 17 to the corresponding counter plates 46 and the flywheel 5 tethered. The clutch disc 18 is realized as a double clutch disc and has two axially displaceable on the support part 25 arranged covering slats. The lining plates (second friction plates 32 ) have a toothing on the inside 49 with a hub of the carrier part 25 connected. As in the eighth exemplary embodiment, the storage takes place via the extension element 42 on the crankshaft 4 , The counter plate 46 is still with the flywheel 5 screwed. The leaf springs 17 are outside the friction surfaces 22 arranged. It is operated by the CSC 9 (preferably with hydrostatic actuator), the CSC 9 is arranged on the back of the engine. A towing anchor 47 is also between the release bearing 40 in the CSC 9 and the disc spring 19 available.

LIST OF REFERENCE NUMBERS

1

hybrid module

2

powertrain

3

separating clutch

4

crankshaft

5

flywheel

6

rotor

7

electric motor

8th

actuator

9

clutch release

10

end shield

11

intermediate shaft

12

cover

13

transmission

14

stator

15

axis of rotation

16

pressure plate

17

leaf spring

18

clutch disc

19

Belleville spring

20

actuator housing

21

screw

22

friction surface

23

damper

24

friction lining

25

support part

26

hub

27

primary

28

secondary side

29

bow spring

30

External disk carrier

31

first friction plate

32

second friction plate

33

Inner disk carrier

34

pressure cooker

35

biasing spring

36

extension

37

roller bearing

38

piston

39

connecting web

40

operation seat

41

support bearing

42

extension element

43

Through Hole

44

screw

45

gap

46

counterplate

47

drag anchor

48

intermediate plate

49

gearing

Claims (4)

Hybrid module (1) for a drive train (2) of a motor vehicle, with a separating clutch (3), the separating clutch (3) also having a flywheel (5) that can be rotatably coupled to a crankshaft (4) of an internal combustion engine on the input side and is designed as a one- or two-mass flywheel. has and on the output side with a rotor (6) of an electric motor (7) is rotationally coupled or can be rotationally coupled, and an actuating device (8) which adjusts the separating clutch (3) between its engaged position and its disengaged position, the separating clutch (3) being a normally engaged one Coupling is formed. Hybrid module (1) after Claim 1 , characterized in that the separating clutch (3) is designed as a single-disc clutch or a multi-disc clutch. Hybrid module (1) after Claim 1 or 2 , characterized in that the actuating device (8) has a concentric clutch release (9), which clutch release (9) is received on a bearing plate (10). Hybrid module (1) according to one of the Claims 1 to 3 , characterized in that the separating clutch (3) is rotatably connected on the output side to an intermediate shaft (11), the intermediate shaft (11) being further rotationally connected to the rotor (6).

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