The invention relates to a multi-plate clutch for a motor vehicle with non-rotatable about Belaganbindungsmittel
connected to a first shaft, axially movable friction linings and
with rotationally fixed on a second shaft arranged pressure plates,
wherein at least one of the pressure plates
for clamping the friction linings
and generating a frictional connection between the two shafts axially
A multi-disc dry clutch is from the DE 195 17 968 A1
known. Here Belaganbindungsmittel different friction linings are provided with a radially inwardly facing teeth and arranged axially displaceable in a toothing of a hub connected to the first shaft. Between the friction liners intermediate discs are axially displaceable and rotatably connected to the second shaft. Upon engagement of the clutch, one of the pressure plates moves in the direction of the other pressure plate and clamped arranged on both faces of the pad springs friction linings and the intermediate discs together. The pad springs are moved together with the friction linings in the direction of the other pressure plate. As a result, the frictional connection between the waves is produced.
in the known multi-plate clutch is that the Belaganbindungsmittel
when in the engaged
Incorporate the state of the multi-plate clutch into the toothing of the hub
this leads to
at the subsequent
to ensure that the friction linings first in
remain in their position and at the intermediate discs and fixed
By the DE 34 37 741 A1
is a multi-plate clutch has become known, in which the intermediate disks each have spring elements and push away from each other when disengaged. This prevents that adjacent intermediate discs remain in a state clamping the friction linings. The disadvantage here, however, is that the Belaganbindungsmittel as in the DE 195 17 968 A1
work into the teeth of the hub and therefore can grind in the disengaged state of the coupling to the intermediate discs.
From the US 3,174,602
a friction clutch is known in which spring fingers come out of the region of the friction linings in order to press the friction linings away from the counter friction surfaces. These spring fingers should provide a secure separation of the friction linings from the counter friction surfaces. Due to the fixed clamping of the friction lining carrier on the hub, however, a permanent grinding of the spring fingers during engagement and disengagement is generated. This results in a disturbing drag torque during the coupling process, which does not remain constant due to the wear of the spring fingers.
Invention is based on the problem, a multi-plate clutch
of the type mentioned above so that a grinding of the
State of the coupling is largely avoided.
Problem is solved by the invention
An embodiment according to the characterizing part of claim 1.
This design will be the friction linings when moving apart
the pressure plates
individually biased in their vorgese Henen positions and therefore of
the intermediate discs and the pressure plates separated. A snagging
the friction linings
in the indented
Condition is reliably avoided by the spring means. Therefore, the
Do not grind the state of the multi-disc clutch. Another advantage
this design is that the friction linings thanks
The invention no further springs for a high Einkuppelkomfort
Pad spring could
For example, a welded to a sheet metal part for holding the friction linings coil spring
or have a protruding spring tongue. However, the pad spring has
according to a
advantageous development of the invention, a large axial
Spring travel and can be
at the same time particularly cost-effective
produce when the pad spring is designed meandering.
Incorporation and subsequent
Persistence of the pad springs in the grooves can be according to another advantageous
Development of the invention almost exclude, if the pad springs in their
movable and in the groove penetrating areas slightly narrower
are as the grooves. This allows
the pad springs are supported on the walls of the grooves, if
with the multi-plate clutch according to the invention
transmit very high moments
should be. When later disengaging the
First lift the clutch
the pad springs from the walls of the grooves and then move the
in the axial direction. The pad springs can therefore be at an actuation of the
Multi-disc clutch in the grooves of the hub in the axial direction without friction
move. Therefore leads
even incorporation of the pad springs in the hub when applying
the circumferential force due to the clutch torque due to the engagement
not to a grinding of the friction linings on the intermediate discs
or the pressure plates.
The grooves may be part of the toothing of the hub of the known multi-disc group ment and thus be arranged parallel to the first wave. However, the circumferentially acting on the pad springs forces can be supported very close to the pad springs, without the hub particularly deep grooves needed when the grooves are arranged substantially perpendicular to the first shaft. With this design, the pad springs can be designed particularly soft.
for example, manufactured together with the grooves as a casting or as Blechtiefziehteil
be. The hub has, however, according to a
another advantageous embodiment of the invention a particular
low weight, if the grooves of bends of a support plate
Range of pad springs could
be designed almost arbitrarily. However, the pad springs are according to a
another advantageous embodiment of the invention in tangential
Direction very stiff when in each case from the attachment to the
Wave a radially away leg
a first U-shaped
Bend and bend from one to a second U-shaped bend
Have limbs and guided by the bend to the friction linings leg,
where the friction linings
holding legs at least partially disposed within the groove
is. Support this
the friction linings are under load in the groove. The attachment
the friction linings
on the pad springs can thereby be designed cohesively, since the
Belagfedern by their elastic design a comfortable operation of the
inventive multi-plate clutch
Pad springs are according to a
another advantageous development of the invention reliably
the hub fastened when the pad springs one in the grooves of
an edge of the hub in the central region axially guided leg
Position of the pad springs can be
just set it on the hub before mounting, if the pad springs
around the edge of the hub. Furthermore, the beading contributes to the initiation of
on the friction linings
acting axial forces
in the hub.
the friction linings
the coupling according to the invention
be either away from each other or moved towards each other
on the friction linings
evenly absorbed by the pad springs,
if the lining springs of the friction linings
are arranged mirror-symmetrically to each other. This will be a
the friction linings
ensured. For several juxtaposed, a common friction lining
retaining pad springs can
the pad springs to compensate for angular deviations of the legs
be alternately arranged in mirror image.
coupling according to the invention
is particularly cost-effective,
when the hub on the first shaft together with one of the friction linings axially
slidably angeord net is and if all other friction linings the elastic
have deformable pad springs. As the first wave mostly off
a hardened one
Material exists and the hub in the area of the shaft is very wide
is, the risk of incorporating the hub into the shaft is particularly low
Hub is designed according to a
other advantageous development of the invention constructive particularly
simple, when the hub arranged on the first shaft hub sleeve and
one on the hub shell
arranged drive plate for holding the pad springs has.
can also be several according to the number of friction linings
Carrier discs on the hub shell
Hub has according to one
another advantageous embodiment of the invention, a high stability, if
the drive plate two mirror symmetry arranged to each other
Sheet metal parts have and when the sheet metal parts close to their outer circumference
Spacers are attached. Continue on the hub
For example, simply attach two or four friction linings.
Invention leaves numerous
to. To further clarify their basic principle are several
thereof shown in the drawing and will be described below.
This shows in
1 a first longitudinal section through a coupling according to the invention,
2 greatly enlarges a second longitudinal section through one half of the coupling according to the invention 1 .
3 an exploded perspective view of the coupling according to the invention 1 .
4 a sectional view through the pad spring 2 along the line IV-IV,
5 - 7 in each case longitudinal sections through a hub and friction linings of further embodiments of the coupling according to the invention.
The 1 shows a coupling according to the invention in a longitudinal section. The coupling has a hub to be mounted on a first shaft 1 and an input part to be mounted on a second shaft 2 , To simplify the drawing of the waves is only a common axis of rotation 46 shown. The entrance part 2 is non-rotating with two pressure plates 3 . 4 and rotationally fixed and axially immovable with a washer 5 connected. Between the washer 5 and each of the pressure plates 3 . 4 are rotatable in pairs with the hub 1 connected and against this axially movable friction linings 6 - 9 arranged. For this purpose, the friction linings 6 - 9 on pad springs 10 - 13 arranged. The pressure plates 3 . 4 be from one opposite the entrance section 2 axially displaceable housing part 14 held. One of the pressure plates 4 lies with a lead 15 on a diaphragm spring 16 and can be in the housing part 14 move axially. The other pressure plate 3 can be combined with the housing part 14 move axially. The housing part 14 has a flange 17 for attachment to a housing cover 18 on. The housing cover 18 forms an axial boundary of the clutch and has in its radially inner region a circumferential support bearing 19 for the diaphragm spring 16 , Another support camp 20 is on the lead 15 that of the diaphragm spring 16 close contact pressure plate 4 arranged. Between the diaphragm spring 16 and the housing cover 18 is one at the entrance 2 fixed ejection support plate 21 with several spacer bolts 22 . 23 arranged. The spacer bolts 22 . 23 are mushroom-shaped and penetrate the diaphragm spring 16 in holes 24 , The hat area of the spacer bolts 22 . 23 has an abutment 25 for the diaphragm spring 16 ,
In the marked position, the diaphragm spring is located 16 on the abutment 25 at. Here are the washer 5 and the pressure plates 3 . 4 from the friction linings 6 - 9 separated. In this position, the hub can be 1 and the entrance part 2 slightly twist against each other. Upon movement of the radially inner region of the diaphragm spring 16 to the right, the diaphragm spring moves away 16 from the abutment 25 and gets against the support bearing 19 of the housing cover 18 , Subsequently, the diaphragm spring presses 16 on the support camp 20 the pressure plate 4 and moves it to the left against its next friction pad 9 , As the diaphragm spring 16 on the support bearing 19 of the housing cover 18 is supported, the housing part 14 to the right and thus the diaphragm spring 16 remote pressure plate 3 against her next friction lining 6 emotional. Here is the washer 5 from the friction linings 7 . 8th clamped. In this position is a frictional connection between the hub 1 and the entrance part 2 produced.
The 2 shows greatly enlarged a longitudinal section in the area of two pad springs 10 . 11 by the coupling according to the invention 1 , The pad springs 10 . 11 are meandering and elastic and have an axial, in a groove 26 the hub 1 arranged legs 27 . 28 , At the edge of the hub 1 are the pad springs 10 . 11 each with a bead 29 . 30 held. On the axial leg 27 . 28 closes radially up to a first U-shaped bend 31 . 32 guided thigh 33 . 34 at. The pad springs 10 . 11 have another one of the first U-shaped bend 31 . 32 to a second, in the groove 26 arranged U-shaped bend 35 . 36 guided thigh 37 . 38 , Another, the friction linings 6 - 9 wearing thigh 39 . 40 joins the second U-shaped bend 35 . 36 at. This gives the document springs 10 . 11 a high stability in the tangential direction and a high elasticity in the axial direction. This will be the friction linings 6 - 9 in every position of the pressure plates 3 . 4 held in their intended location. Due to its symmetrical design, the clutch has a uniform wear pattern on the friction linings 6 - 9 , Further shows 2 in that the housing part 14 and the entrance part 2 in the radial direction positively interlocking arms 41 . 42 exhibit.
The in the 1 and 2 shown coupling can also be summarized with a flywheel, not shown, or a torsion damper, also not shown to form a structural unit. Of course, the flywheel may be designed as a dual-mass flywheel. The torsion damper can be, for example, on which the pressure plates 3 . 4 retaining housing part 14 or in the hub 1 assemble.
The 3 shows an exploded perspective view of the coupling according to the invention 1 , For clarity, the axis of rotation of the fully assembled clutch is shown in phantom. It can be seen that the input part 2 and the housing part 14 each a variety of arms 41 . 42 exhibit. The poor 41 . 42 of the housing part 14 and the entrance section 2 each penetrate into grooves 43 . 44 the washer 5 one. As a result, the housing part 14 guided axially displaceable and positively in the tangential direction with the input part 2 and the washer 5 connected. Each of the paired friction linings 6 - 9 comes from a variety of pad springs 10 - 13 held. The hub 1 has one of the number of pad springs 10 - 13 corresponding number of grooves 26 , Of course, the coupling can additionally with a torsional vibration damper, not shown between input part 2 and hub 1 be provided or attached to the output side of a dual-mass flywheel to eliminate torsional vibrations from the drive train.
4 shows in a sectional view taken along the line IV-IV through the coupling 2 Representing the in 1 illustrated pad springs 10 - 13 one of the pad springs 10 , The pad spring 10 is here in the 2 shown, from the washer 5 separate position of the friction linings 6 . 7 shown. Dash-dot is in 4 also the pad spring 10 in the against the washer 5 pressed position of the friction linings 6 . 7 shown. Here it can be seen that in the groove 26 arranged U-shaped bend 35 narrower than the axial, in the groove 26 arranged, adjacent to the flanging leg 27 , This allows the friction linings 6 . 7 move smoothly in the axial direction in the unloaded state. Wear of the pad spring 10 and the wall 45 the groove 26 is thus kept very low. If the friction linings 6 . 7 against the in 2 illustrated washer 5 be biased, the hub can be 1 opposite to the likewise in 2 illustrated input part 2 twist it until it is in the groove 26 arranged U-shaped bend 35 the pad spring 10 against a wall 45 the groove 26 arrives. This allows the pad spring 10 a very comfortable operation of the clutch. An incorporation of the pad spring 10 in the wall 45 the groove 26 In addition, when disengaging does not lead to a persistence of the friction linings 6 . 7 in their position, since those in the groove 26 arranged bend 35 initially almost perpendicular to the wall 45 the groove 26 is pulled away.
5 shows a hub 47 with friction linings 48 a further embodiment of the multi-plate clutch according to the invention in longitudinal section. The hub 47 has a hub shell 49 with a drive disc 50 for holding a ring 51 , The hub shell 49 has an internal tooth 52 for mounting on a shaft. To simplify the drawing of the shaft is only its axis of rotation 53 shown in phantom. On the ring 51 are pad springs 54 . 55 for axially resilient mounting of the friction linings 48 attached. The driving disc 50 has two mirror-symmetrically arranged sheet metal parts 56 . 57 on. The sheet metal parts 56 . 57 be close to their outer circumference of spacers 58 held in their intended location. The longitudinal section is in the upper half of the 5 by a pair of opposing pad springs 54 . 55 and in the lower half of the 5 through one of the spacers 58 guided. The ring 51 is profiled and has like those in the 1 - 4 illustrated hub 1 groove 59 for lateral support of the pad springs 54 . 55 , In contrast to the pad springs 10 - 13 the multi-plate clutch from the 1 - 4 have the pad springs here 54 . 55 two beadings each 60 . 61 ,
6 shows a longitudinal section through a hub 62 with friction linings 63 a further embodiment of the multi-plate clutch according to the invention. The hub 62 has a hub shell 64 for attachment to a not shown first shaft of the multi-plate clutch. The hub shell 64 carries a drive disc 65 , on the support plates 66 . 67 are attached. The support plates 66 . 67 have bends 68 . 69 on. The bends 68 . 69 form perpendicular to a rotation axis 70 the shaft extending grooves 71 . 72 for lateral guidance of meandering, the friction linings 63 holding pad springs 73 . 74 , In the drawing, the longitudinal section in the upper half by the pad springs 73 . 74 and in the lower half in front of one of the support plates 66 . 67 guided. The pad springs 73 . 74 are with a thigh 75 . 76 in the groove 71 . 72 on the support plate 66 . 67 welded. Between the attachment to the support plate 66 . 67 and the friction linings 63 have the pad springs 73 . 74 two freely movable legs each 77 . 78 and two bends. The friction linings 63 holding thighs 76 . 78 is from the support plates 66 . 67 especially close to the friction linings 63 supported. The thigh 77 . 78 Show off like that 4 a game in the groove 71 . 72 on, so that the friction linings 63 can move axially and under load at the bends 68 . 69 support.
7 shows a longitudinal section through a hub 79 with friction linings 80 . 81 a further embodiment of the multi-plate clutch according to the invention. This embodiment differs from that of 6 essentially in that a hub sleeve 82 the hub 79 is provided for rotationally fixed and axially displaceable arrangement on a shaft. To simplify the drawing of the shaft is only its axis of rotation 83 indicated by a dot-dash line. On the hub shell 82 is a driver disk 84 attached. The driving disc 84 carries pad springs 85 for holding a pair of friction linings 81 and several support plates 86 , The support plates 86 have like that out 6 bends 87 . 88 for lateral guidance of meandering pad springs 89 of the second pair of friction linings 80 , The bends 87 . 88 form as in the multi-plate clutch 6 with grooves 90 for the pad springs 89 , These pad springs 89 are with the support plates 86 welded. This is the second pair of friction linings 80 through the elastically deformable pad springs 85 opposite the hub 79 held axially movable.