DE102006025061A1 - Device for the axial adjustment of at least one lamellar switching element - Google Patents

Abstract

It is a device for axial adjustment of at least one lamellae switching element with a pivot wheel (89) and an adjacent thereto ball ramp disc (91) proposed, wherein the pivot wheel (89) axially fixed and rotatable and the ball ramp disc (91) rotatably and axially displaceably mounted and wherein the pivot wheel (89) cooperates with the ball ramp disc (91) by means of rolling elements (97) which are arranged in depth-varying grooves (95) of the pivot wheel (89) and in corresponding grooves (93) of the ball ramp disc (91), wherein the grooves (93, 95) have a variable slope over their course. It is inventively provided that the grooves (93, 95), starting from an initial position of the rolling elements (97), in the open state of the louver switching element in a first direction of movement (I) of the pivot wheel (89) an initial pitch between 10 ° and 25 ° in a clearance play area (130) of the louver switching element and a pitch of at least 1.4 ° in a working area (132) of the louver switching element.

Description

The The invention relates to a device for axial adjustment at least a lamellar switching element according to the preamble of claim 1 closer defined type.

Such a device for axial adjustment of a lamellar switching element is for example from the EP 0 340 451 A2 known. Therein, a device for axial adjustment is described, which actuates a friction arrangement by means of a selectively operable rotary drive via a pressure ring. For this purpose, an adjustable by an electric motor via a pinion collar is provided which causes an axial displacement of the pressure ring.

Of the Pressure ring is arranged even non-rotatable relative to a housing. At the mutually facing end faces of the pressure ring and the adjusting ring are control curves or control profiles provided which a non-linear rate of change of on the thrust ring effective axial component on the angle of rotation of the adjusting ring and which between the pressure ring and the adjusting ring in abstützender, the pressure ring upon rotation of the adjusting ring shifting active connection stand. It is u. a. proposed the cams as themselves perform in the adjusting ring and the pressure ring grooves, wherein the adjusting ring cooperates with the pressure ring by means of balls, which in the correspondingly arranged grooves of the adjusting ring and the pressure ring are located.

The Control cam has a non-linear rate of change, which in a first phase of operation the friction arrangement a steep increase of the effective axial components to overcome the Play of fins of the friction arrangement a strong spreading rate effected between the collar and the pressure ring. The rise of Axial component drops then progressively down until the desired slope for the work area the blocking effect is achieved and then remains constant until the end of the web. For the rate of change For ball grooves, an initial angle range of 6 ° to 9 ° and a Outlet angle from 1 ° to 1,5 ° as Appropriately proposed, the outlet angle to the end of the Track remains constant.

at such a chosen rate of change is the duration to overcome of the clearance small. Since the slopes of the intended ball grooves very small Accept values is the axial adjustment path for actuating the Slats of the friction arrangement disadvantageously low.

Of the present invention is based on the object, a device for axial adjustment of a lamellar switching element of the beginning Such a way that a fast and secure activity the lamellar switching element is ensured and easy Way to control.

Erfndungsgemäß this is Task with a transmission unit with the features of claim 1 solved.

It is therefore a means for axial adjustment of at least one Slat switching element with a swivel wheel and an adjacent thereto Ball ramp provided, wherein the swivel wheel axially and rotatable and the ball ramp disc rotatably and axially displaceable is mounted, and wherein the swivel wheel with the ball ramp disc cooperates by means of rolling elements, which in depth-varying grooves of the swivel wheel and in it corresponding grooves of the ball ramp disc are arranged, the grooves over her Course have a variable slope. It is provided according to the invention, that the grooves starting from an initial position of the rolling elements at open State of the lamellar switching element in a first direction of movement of the swivel wheel an initial pitch between 10 ° and 25 ° in one Lüftspielbereich of the louver switching element and a pitch of at least 1.3 ° to 1.7 °, in one Working area of the louver switching element have.

through an inventively designed Device for axial adjustment can already by a small Rotation of the swivel wheel the clearance of the lamellar switching element, which may be a multi-plate clutch or a multi-disc brake, overcome be, thereby advantageously very short operating times of the louver switching element can be achieved and an optimal combination from force and time is reached.

Become the slope in the clearance area and the slope in the work area as constant slopes, d. H. formed as continuous slopes without radius of curvature, which merge into each other by means of a radius, so is a very simple control cam of the drive mechanism of the louver switching element educated.

deviant However, it can also be provided that the slope of the work area and the clearance area as a continuously variable one Gradient is realized.

In an advantageous embodiment of the invention, the grooves in an area adjacent to the Lüftspielbereich in a second direction of movement of the pivot wheel, which is opposite to the first direction of movement, adjacent have a slope of at least approximately zero. In such an embodiment, the means for axial adjustment for the operation of two slats switching elements may be provided, wherein the first direction of movement is a first and a second slats switching element opening a rotational direction of rotation of the pivot wheel and the second direction of movement opening the first slats switching element and closing the second slats switching element rotational movement direction represents the swivel wheel.

It offers the use of a single motor for control of two ball ramp discs, wherein when closing the one Slat switching element, the other slats switching element not yet further open is when the ball ramp disc of the other, not actuated lamellar switching element formed with an area with a pitch of 0 mm per revolution becomes. In this way, advantageously travel and space saved.

In Advantageous embodiment of the invention are the ball ramp disc and / or on the other hand, the displacement of the slats limiting support disk on its surface facing the slats with one with the slats formed co-operating friction lining. This can be compared to conventional solutions components of the device be saved for axial adjustment, which costs one be saved on the other hand, but also across the direction of actuation of Lamella brake extending space is shortened and thus the package is optimized.

Especially advantageous is the design of the ball ramp disc with a Sintered material, whereby the processing of the ball ramp disc on limited to certain local areas can be. The manufacturing costs for the ball ramp disc fall thereby advantageously low.

Further Advantages and advantageous developments of the invention result from the claims and two described in principle with reference to the drawings Embodiments.

It shows:

1 a partially sectional schematic representation of a Hinterachsgetriebeeinheit a motor vehicle with an operable by an electric motor means for axial adjustment of a lamellar switching element;

2 a fragmentary schematic cross-sectional sketch of a groove of a ball ramp disc of the device for axial adjustment and a groove of a pivot wheel of the means for axial adjustment of 1 wherein a guided on the ball ramp disc ball is shown in an initial position in the open state of the lamellar switching element;

3 one of the 2 corresponding representation of the device for axial adjustment, wherein the ball is shown in a transition state between an end of a clearance and a beginning of a working range of the louver switching element;

4 one of the 2 and 3 corresponding representation of the device for axial adjustment, wherein the ball is shown in a state of the lamellar switching element in the work area;

5 a partially sectional schematic representation of an alternative Hinterachsgetriebeeinheit with two actuated by an electric motor means for axial adjustment; and

6 a fragmentary schematic cross-sectional sketch of the groove of a ball ramp disc and the groove of the pivot wheel of the means for axial adjustment of 5 wherein the ball is shown in a neutral position.

In 1 is a range of a gear unit 1 shown which one of a drive machine or internal combustion engine only schematically shown 10 provided, via a drive shaft 2 transmitted drive torque to a first output shaft 3 and a coaxial with respect thereto and with respect to the drive shaft 2 symmetrically arranged second output shaft 5 distributed.

The gear unit 1 is intended for installation in a motor vehicle and is designed in the embodiment shown as Hinterachsgetriebeeinheit, but it is also conceivable that a substantially analog gear unit is used as Vorderachsgetriebeeinheit. It is also conceivable to use the present transmission unit both as a front axle transmission unit and as a rear axle transmission unit, for example in a four-wheel drive motor vehicle.

The output shafts 3 respectively. 5 which are rotatably mounted about a common longitudinal axis X, are connected at their free ends in each case with a vehicle wheel, not shown, wherein in the installed state of the Hinterachsgetriebeeinheit 1 a vehicle wheel with respect to the first output shaft 3 on a transmission left side viewed in the vehicle front direction 7 and a vehicle wheel with respect to the second output shaft 5 on a right side of the transmission 9 located. The rear axle unit 1 be includes a gearbox 11 , which with a substantially the drive shaft 2 surrounding front gear housing part 12 with one of the left transmission side 7 associated side gear housing part 13 from which the first output shaft 3 protrudes laterally, and with a not shown on the right side of the transmission 9 associated lateral gear housing part from which the second output shaft 5 protrudes laterally, is formed.

The rear axle unit 1 distributes that from the drive shaft 2 transmitted drive torque on the two output shafts 3 and 5 and can also have an uneven torque distribution on the two output shafts 3 and 5 effect and thus actively improve the driving characteristics. In this case, the drive torque from the drive shaft 2 in a differential unit 15 initiated, which with a differential 17 and a differential basket 19 trained and with a device 14 for influencing the drive torque on the output shafts 3 and 5 connected is. For operative connection between the drive shaft 2 and the differential cage 19 is a fixed to the drive shaft 2 connected drive pinion 21 with a fixed to the differential basket 19 connected crown wheel 23 engaged, with the differential cage 19 is rotatably mounted about the longitudinal axis X and in the transmission housing 11 supported.

The differential 17 is in a known construction with two with the respective output shaft 3 respectively. 5 connected output side bevel gears 25 and 27 and two with the two bevel gears 25 and 27 meshing drive side bevel gears 29 and 31 educated. The two drive-side bevel gears 29 and 31 are rotatable on a bolt 33 arranged in the differential cage 19 is fixed with respect to a rotation about the longitudinal axis X.

The 1 shows two embodiments of the drive side bevel gears 29 and 31 and the cooperating output side bevel gears 25 and 27 which are engaged with each other, wherein the expert can select an alternative according to the particular application.

Is from the internal combustion engine 10 a drive torque via the drive shaft 2 transmitted, so this is about the drive pinion 21 on the ring gear 23 and the attached differential basket 19 transfer. By means of the with the differential cage 19 connected bolt 33 of the differential 17 the drive torque is applied to the drive-side bevel gears 29 and 31 of the differential 17 which transmits the drive torque in turn to the output side bevel gears 25 and 27 of the differential 17 direct and thus the output shafts 3 and 5 drive. There is no differential speed between the two output shafts 3 and 5 before, the drive-side bevel gears rotate 29 and 31 with the bolt 33 exclusively about the longitudinal axis X. If an output shaft in the installed state, for example, rotate faster than the other due to the turning at different speeds when cornering vehicle wheels than the other, then turn the drive-side bevel wheels 29 and 31 to compensate for the speed difference around the bolt 33 , where the bolt 33 Furthermore, the drive torque via its rotation about the longitudinal axis X on the two output shafts 3 . 5 forwards.

In addition to balancing a different speed of the two output shafts 3 and 5 can with the Hinterachsgetriebeeinheit 1 a different torque distribution on the two output shafts 3 and 5 be achieved. This is the device 14 for influencing the drive torque on the output shafts 3 respectively. 5 formed with two symmetrically arranged to the transmission center axis Y identically constructed torque vectoring units, wherein of the two torque vectoring units in 1 only the left side of the transmission 7 associated torque vectoring unit 35 which is described below. The torque vectoring units are in the transmission housing 11 arranged and are in the present case in each case an associated, switchable electric motor 37 infinitely adjusted and actuated.

As with the illustrated torque vectoring unit 35 can be seen, this one has a translation level 39 trained planetary gear set without ring gear and one of the electric motor 37 actuated brake device 51 on, with the translation stage 39 with two sun wheels 61 and 63 is formed, of which a first sun gear 61 stuck with the differential basket 19 and of which a second sun wheel 63 fixed to the output shaft 3 connected is. The sun wheels 61 and 63 act with three present rotating on a planet carrier 65 planet together, two of which are planets 69 and 71 are visible, and which a continuous toothing 73 exhibit.

The brake device 51 has a multi-disc brake 77 trained lamellar switching element on. The infinitely adjustable multi-disc brake with regard to its transmission capacity 77 points as fins on the planet carrier 65 arranged inner fins 75 on which with in the gearbox 11 fixed outer plates 79 menwirken together by their axial adjustability so that they can be brought into a frictional contact or from a frictional contact. The electric motor 37 actuates the brake device 51 in this case via one of its drive shaft 83 driven, gearbox fixed mounted idler 85 , which with the on drive shaft 83 of the electric motor 37 engaged and a facility 87 for axial adjustment of the multi-disc brake 77 actuated. The device 87 for axial adjustment of the multi-disc brake 77 is with a swivel wheel 89 , which with the intermediate wheel 85 engaged and like the idler 85 on the side facing away from the transmission center axis Y side of the multi-disc brake 77 is arranged, and one between the pivot wheel 89 and the multi-disc brake 77 arranged ball ramp disk 91 built up.

In an open state of the multi-disc brake 77 the translation stage is running 39 without torque transfer around the longitudinal axis X order. Is about the electric motor 37 a friction joint in the multi-disc brake 77 triggered, so from the drive torque on the respective output shaft 3 respectively. 5 generates effective torque vectoring moment. This is done by a support of the planet carrier 65 over the brake device 51 in the transmission housing 11 , It is thus a torque transfer from the drive shaft 2 via the differential basket 19 and from there by means of the planet carrier 65 from the first sun wheel 61 on the respective with the output shaft 3 respectively. 5 connected second sun gear 63 generated, by means of which a different torque distribution to the first output shaft 3 and the second output shaft 5 can be achieved.

For actuating the multi-disc brake 77 have the rotationally fixed and axially displaceable in the transmission housing 11 mounted ball ramp disk 91 and the swivel wheel 89 around the first output shaft 3 the device 87 for axial adjustment over its radius distributes three varying in depth grooves 93 on. In with the grooves 93 the ball ramp disk 91 corresponding, also in their depth varying grooves 95 of the swivel wheel 89 Three are balls 97 trained rolling elements, about which at one by the electric motor 37 controlled rotation of the swivel wheel 89 an axial movement of the ball ramp disc 91 results, so that the housing-fixed outer plates 79 after overcoming a clearance of the multi-disc brake 77 with the inner plates 75 the multi-disc brake 77 make a frictional connection.

Because when using a ball ramp disc 91 with constant pitch circle diameter of the ball track the maximum available twist angle at 360 ° divided by the number of balls 97 can, in a version with three balls 97 the maximum angle of rotation of the ball ramp disc 91 will be realized. Furthermore, by using only three balls 97 the carrying percentage per ball maximum, the load in relation to the number of balls due to manufacturing tolerances can not be increased by more balls. A maximum angle of rotation of the swivel wheel 89 Thus, due to the present three points 97 trained facility 87 for axial adjustment to a value of about 120 °. But there is also the possibility to use more balls.

The grooves 93 the ball ramp disk 91 , Which in the present case represents a component made of sintered material, as well as the grooves 95 of the swivel wheel 89 are in the 2 shown in a cross section and have, starting from a starting position shown in this figure, in which the ball ramp disc 91 and the swivel wheel 89 have a minimum axial distance from each other, over a circumferential region which an axial, a clearance play area 130 of the lamellar switching element 77 assigned to associated travel S1, a constant large pitch and a subsequent peripheral area, which a travel S2 of a work area 132 associated with a structure of a clutch torque, a constant small pitch on. The ball track sections of the clearance range 130 and the workspace 132 are over a radius 134 connected with each other.

As well as the 3 and 4 it can be seen which the ball 97 in other stages with a rotation of the swivel wheel 89 in a first direction of movement I, which one of the multi-disc brake 77 represents closing rotational movement, takes in the clearance area 130 the slope is a value between 10 ° and 25 °. This can advantageously already by a very small rotation of the swivel wheel 89 the clearance of the multi-disc brake 77 be overcome. The workspace 132 on the other hand has a relatively low pitch of 1.4 ° to 1.7 °, which causes the axial adjustment of the multi-disc brake 77 can be made very accurately and on the electric motor 37 only a small moment to build up a clutch torque is applied. In addition, the clearance of the multi-disc brake 77 at a given maximum speed of the electric motor 37 be traversed quickly and in the work area 132 a high positioning accuracy can be achieved with a high number of revolutions of the electric motor. A high number of revolutions of the electric motor 37 This results in a good position control, which is expediently formed with a sensor, not shown.

The slope in different areas 130 . 132 can be selected depending on the required resolution such that an optimal path resolution at the electric motor 37 is achieved and that the nonlinearity of friction linings of the slats 75 . 79 the multi-disc brake 77 is compensated, wherein the slope is flatter with stiffer friction lining.

In a particularly space-saving manner are here the ball ramp disc 91 and an opposite support disk of the louver switching element 77 provided with a friction lining, whereby these elements as end plates of the lamellar switching element 77 serve.

In 5 is a largely the Hinterachsgetriebeeinheit the 1 corresponding rear axle transmission unit 1 shown, which in contrast to the Hinterachsgetriebeeinheit the 1 only a single electric motor 37 ' for controlling both the torque vectoring unit 35 ' the left side of the vehicle in the direction of the vehicle front 7 as well as the torque vectoring unit 36 in the vehicle front right gear side 9 associated device 87 ' for axial adjustment.

The electric motor 37 ' stands with a connecting shaft 105 in engagement, which in turn by means of an intermediate wheel 85 ' . 86 each with an output shaft 3 respectively. 5 associated swivel wheel 89 ' respectively. 90 the device 87 ' cooperates for axial adjustment.

The 6 shows an example of the formation of the grooves 93 ' the ball ramp disk 91 ' and the swivel wheel 89 ' at the first output shaft 3 , where the ball ramp disk 92 and the swivel wheel 90 on the second output shaft 5 are formed substantially identical. Compared to the execution of the 2 to 4 have the grooves 93 ' . 95 ' starting from an initial position of the balls 97 with the multi-disc brake open 77 ' an area without slope, which is related to the balls 97 in a clearance area 130 ' located opposite area.

The electric motor 37 ' operated upon rotation of its drive shaft 83 ' in one direction, for example, the left side of the transmission 7 assigned multi-disc brake 77 ' in the first direction of movement I and with a rotation of its drive shaft 83 ' in the other direction the right side of the transmission 9 assigned multi-disc brake 77B by rotation of the swivel wheel 90 in an opposite direction of movement II.

By such a design of the grooves 93 ' . 95 ' the ball ramp disk 91 ' and the swivel wheel 89 ' is at a closing of the respective other transmission side 7 respectively. 9 associated multi-disc brake 77 ' respectively. 77B the ball ramp disc 91 ' and the swivel wheel 89 ' only twisted against each other, without resulting in a travel on the multi-disc brake 77 ' respectively. 77B results. As a result, space can be saved in an advantageous manner.

1

Hinterachsgetriebeeinheit

2

drive shaft

3

first output shaft

5

second output shaft

7

left transmission side

9

right transmission side

10

Internal combustion engine

11

gearbox

12

front Gear housing part

13

lateral Gear housing part

14

contraption for influencing the drive torque on the output shafts

15

differential unit

17

differential

19

differential cage

21

pinion

23

crown

25

driven side bevel gear

27

driven side bevel gear

29

driving side bevel gear

31

driving side bevel gear

33

bolt

35

Torque vectoring unit

35 '

Torque vectoring unit

36

Torque vectoring unit

37

Electric Motor

37 '

Electric Motor

39

translation stage

51

braking device

61

first sun

63

second sun

65

planet carrier

69

planet

71

planet

73

gearing planet

75

inner disk

77

multi-disc brake the torque vectoring unit

77 '

multi-disc brake the torque vectoring unit

77B

multi-disc brake the torque vectoring unit

79

outer disk

83

drive shaft Electric Motor

83 '

drive shaft Electric Motor

85

idler

85 '

idler

86

idler

87

Facility for axial adjustment

87 '

Facility for axial adjustment

88

Facility for axial adjustment

89

caster

89 '

left caster

90

right caster

91

Ball ramp disk

91 '

Ball ramp disk

92

Ball ramp disk

93

groove the ball ramp disk

93 '

groove the ball ramp disk

95

groove of the swivel wheel

95 '

groove of the swivel wheel

97

roll

105

connecting shaft

130

Lüftspielbereich

132

Workspace

134

radius

136

Area without incline

I

first movement direction

II

second movement direction

S1

Travel Range

S2

Travel Range

X

longitudinal axis

Y

Transmission center axis

Claims (5)

Device for axial adjustment of at least one lamellar switching element ( 77 . 77 ' . 77B ) with a swivel wheel ( 89 . 89 ' . 90 ) and an adjacent ball ramp disc ( 91 . 91 ' . 92 ), wherein the swivel wheel ( 89 . 89 ' . 90 ) axially fixed and rotatable and the ball ramp disc ( 91 . 91 ' . 92 ) is mounted rotationally fixed and axially displaceable, and wherein the swivel wheel ( 89 . 89 ' . 90 ) with the ball ramp disc ( 91 . 91 ' . 92 ) by means of rolling elements ( 97 ), which in depth-varying grooves ( 95 . 95 ' ) of the swivel wheel ( 89 . 89 ' . 90 ) and in corresponding grooves ( 93 . 93 ' ) of the ball ramp disc ( 91 . 91 ' . 92 ) are arranged, wherein the grooves ( 93 . 93 ' . 95 . 95 ' ) have a variable pitch over their course, characterized in that the grooves ( 93 . 93 ' . 95 . 95 ' ) starting from an initial position of the rolling elements ( 97 ) in the open state of the lamellar switching element ( 77 . 77 ' . 77B ) in a first direction of movement (I) of the swivel wheel ( 89 . 89 ' . 90 ) an initial pitch between 10 ° and 25 ° in a clearance range ( 130 ) of the lamellar switching element ( 77 . 77 ' . 77B ) and a slope of at least 1.4 ° in a work area ( 132 ) of the lamellar switching element ( 77 . 77 ' . 77B ) exhibit. Axial adjustment device according to claim 1, characterized in that the slope in the working area ( 132 ) is at least approximately 1.7 °. Device for axial adjustment according to one of claims 1 or 2, characterized in that the slope in the clearance play area ( 130 ) and the slope in the work area ( 132 ) represent constant slopes, which by means of a radius ( 134 ) merge. Axial adjustment device according to one of claims 1 to 3, characterized in that the grooves ( 93 . 93 ' . 95 . 95 ' ) in one of the clearance area ( 130 ) in a second direction of movement (II) of the swivel wheel ( 89 ' . 90 ), which is opposite to the first direction of movement (I), adjacent area ( 136 ) have a slope of at least approximately zero. Device for axial adjustment according to claim 4, characterized in that this for actuating two lamellar switching elements ( 77 . 77 ' . 77B ) is provided, wherein the first direction of movement (I) is a first lamellar switching element ( 77 ' ) closing and a second lamella switching element ( 77B ) opening rotational direction of the pivot wheel ( 89 ' . 90 ) and the second direction of movement (II), a first lamellae switching element ( 77 ' ) and a second lamellae switching element ( 77B ) closing rotational direction of the pivot wheel ( 89 ' . 90 ).