DE2013519A1 - Centrifugal clutch - Google Patents

Description

PATENT LAWYERS

D R .-. L NG. H. FINCKE ⁸ ^ "^ ,, / O Π 1 ^ R 1

DIPL-ING.H. BOHR tU IJJ N

DIPL.-INS. S. STAESER

Long distance call. 224941 Telegrams: Claims Munich Poitscheckkonto Munich 27044

- Bank details ι Bayerische V * reln $ bank Munich, account 620404

8332 - Case 662/678 Description

Folder [NO.

Please indicate in the answer

to the patent application of the company SOCIETE ANONYME FRANCAISE DU FERODO

Paris, France

regarding "centrifugal clutch"

Priorities: 3/20/1969 and 8/11/1969 - FRANCE

The invention relates to centrifugal clutches of the type comprising in series connection between a driving one Shaft and a driven shaft on the one hand a centrifugal device that depends on the speed of the driving shaft and which has a number of flyweights which are shown in an annular space firmly connected to the driving shaft, are radially movable, and between a cover with a flywheel is firmly connected, which is attached to a flange of the driving Shaft is attached, and act a pressure plate, which is axially movable and rotatably connected to the cover, and on the other hand a coupling device between the pressure plate and the driven shaft acts and has a friction disc 'which is axially movable and connected to the driven shaft is rotatably connected, which disc friction lining «between

"" 009140/1481

the flywheel and the pressure plate carries which coupling device is combined with lifting springs that load the pressure plate in an axial direction away from the flywheel.

Such clutches are usually used as separating clutches, the sole effects of centrifugal forces and are exposed to elastic return organs, i.e. lifting springs.

With the previously burned designs of this type the centrifugal weights of the centrifugal device move freely both radially, which is responsible for the operation of the centrifugal device is required, as well as in the circumferential direction, which means a double disadvantage: on the one hand, these Flyweights at standstill have the tendency to regroup and can create an undesirable imbalance when starting up and on the other hand, because of the relative mobility of the flyweights with respect to each other, the mode of operation the centrifugal device is particularly noisy and the balancing may be poor.

In addition, these known couplings are the aforementioned Kind of at least certain of the flyweights of the centrifugal device parallelepipedic elements between slide along the parallel surfaces of their receiving space. the

009840 / U8S

Friction corresponding to such movements is considerable both because of the size of the respective contact surfaces as well as because of the often high inclination of the weight, to get jammed in their recording room.

The main effect of the existence of this friction is that it leads to a considerable inequality of the torque values leads, which through the centrifugal clutch at a given speed of the driving shaft, depending on whether this speed increases or decreases is transmitted.

This disparity, commonly referred to as "hysteresis" becomes annoying when it gets too big because it can under certain conditions difficulties in switching the gearbox associated with the clutch because of the corresponding discontinuity in transmitted torque cause.

In addition, most of the previously known centrifugal clutches the lifting springs are independent elements that, when assembled, are placed individually between the flywheel and the pressure plate must be used.

Such an individual installation of these lifting springs at night complete assembly of the coupling cumbersome and time consuming.

Ö09840 / U88

The object of the invention is to create a centrifugal clutch in which the aforementioned disadvantages are reduced to a minimum or completely eliminated.

The centrifugal clutch according to the invention, that of the preceding Briefly stated type, differs according to a first feature of the invention in that the lid is designed so that it has a conical contact surface of the pressure plate in the direction of the cover increasing diameter forms an annular space which are used to accommodate at least one annular row of balls can, which form the flyweights and in contact on the one hand with the mentioned conical bearing surface of the pressure plate and on the other hand with a conical contact surface of the cover increasing in the direction of the pressure plate Diameter are located, which balls holding means are assigned.

According to a first. Embodiment are two ring-shaped Rows of balls are provided, which rows are radially offset from one another, the holding means with the outermost Row of balls interact and consist only of the balls of the innermost row, and the balls of the outermost row Row are in contact with two balls in the innermost row.

O098A0 / U8B

These holding means act a relative circumferential displacement of the balls against each other, which contributes to the "centrifugal clutch according to the invention a relatively to give noiseless operation.

Preferably the balls of the innermost row are strict held in their position with respect to each other when the Clutch does not turn, be it because the balls hit each other, be it that they are held in place by seats in their annular space, for example in the cover or provided in a cage firmly connected to this Projections or the like .. In addition, the ring space in which the two rows of balls are arranged, radially, according to a preferred embodiment, a development that, itself when the clutch device is engaged and the friction linings show the maximum permissible wear, smaller than that of the diameter of the balls in the innermost row and the diameter of the balls in the outermost row total is formed. Therefore, each ball is in the outermost row, which is laterally crossed by two balls at rest innermost row is held, prevented during operation from moving past one or the other of the latter, making their possibilities a relative

Circumferential shift can be reduced even more. In addition, and when it comes to balls, theirs

009840/1485

Contact with the surfaces guiding them is punctiform and which can roll on these, are the flyweights the centrifugal clutch only the cause of a very low internal friction, so that the hysteresis of the invention FÜshkraftkupplung is advantageously returned to acceptable values.

For this purpose and according to an additional feature of the "invention, the plane of the balls of the innermost row is preferred axially offset with respect to the plane of the balls of the outermost row in the direction of the cover of the coupling, which cover the one of the transverse surfaces of the annulus for which forms the balls.

As a result of this arrangement, these balls lose any contact with the other surface of their annulus during operation, what on the one hand enables this other surface to be made economical with the aid of an element of relatively low mechanical strength to shape.

In a second embodiment of the invention, the lifting springs are arranged on the cover and can through Train act on the pressure plate, each lifting spring consists of a wire section in the form of two adjacent coil springs, which have free ends and which are shaped by a central double arm

009840/1486

of a U are united, which ends at one of the two Organs are attached, which form the lid and the pressure plate, while the central double arm on the other of the organs is attached and the central double arms of the Lifting springs form the holding elements for the balls and divide these balls into several groups.

The pressure plate and the cover therefore together form an assembly unit which itself has the associated lifting springs and for this reason can be attached directly to the flywheel very easily and very quickly.

According to a further feature of the invention, the lifting springs form Holding organs that divide the balls into several groups.

According to a particular feature of the invention, if it is lifting springs, which, as mentioned, form two adjacent helical springs, which are replaced by a double central arm in the form of a "U" are united, this central U-shaped arm holding means for at least some of the springs.

The subdivision ensured in this way is sufficient to avoid the disadvantages of general stirring of the balls with which the couplings of this type are equipped around the axis of the agitator unit

009840 / U8 B

are that wear is created on the balls and the surfaces on which they run. At the same time is this circumferential subdivision is rather limited to enable a sufficient number of balls to be used. Ultimately, this subdivision maintains the desired regular geometric division for the balls, whereby unwanted jamming and thus delays in uncoupling can be avoided.

Further objects, features and advantages of the invention emerge from the following description which is more detailed by way of example in connection with the accompanying drawings, namely show:

Fig. 1 is a partial view in elevation of one according to the invention Centrifugal clutch with parts broken away;

FIG. 2 shows a view of the centrifugal clutch in axial section along the broken line II-II in FIG. 1;

Fig. 3 is a partial view of the coupling in section along the curved line III-III in Fig. Ij

U shows a half view of the centrifugal clutch according to the invention in axial section in the engaged position;

009840 / U86

Fig. 5 is a graph which.in schematic Way one of the advantages of the centrifugal clutch according to the invention shows;

Fig. 6 is a partial view in elevation with broken away Parts of a modified embodiment;

Fig. 7 is a view of this modification in axial section according to the broken line VII-VII in Fig. 6;

8 shows a schematic view on an enlarged scale a lifting spring with which the modified embodiment is equipped;

Fig. 9 is a plan view of this spring.

In the embodiment shown in FIGS. 1 to 4, the centrifugal clutch according to the invention has a Flywheel 10, which is fastened to a flange 12 by screws 11 a driving shaft 13 is attached. On this flywheel ^ irst ^ on ^ e ^ r ^ sdsj ^^ shaft 13 opposite Side an annular cover, which is attached for this Purpose has a first set of lying in the same plane fields 15 on its outer circumference, which against the Flywheel 10 and the insertion of screws 16 allow the attachment of the lid to the swing "

001840 / UIi \ ..

ensure wheel.

Between the flywheel 10 and the cover 14 are consecutive arranged: an annular friction disc 17, which is driven on its inner circumference with a Shaft 19 is fixedly connected to the hub 18 arranged in a rotationally fixed manner and friction linings 20 on its outer circumference on both sides carries, also an annular pressure plate 21 and an ■ annular end cage 22 made of thin sheet metal, which with the cover 14 · is firmly connected by riveting its inner circumference around that of the cover and with this an annular space 23A, which is designed so that it can accommodate two rows of balls. In the illustrated embodiment the space 23A contains a first row of balls 24A and a second row of balls 24-B which are rows of balls are offset from one another both radially and axially, but bear against one another.

In the illustrated embodiment, the balls 24A, 24B all have the same diameter, thereby making the insertion the same is simplified.

The intermediate plate 21 has three regularly around the circumference distributed radial lugs 26.

For the passage of these approaches, the cover 14 indicates

009840/1488

its outer circumference bulges, which are through a second set of fields 27 are limited.

A spring 28 is assigned to each of the lugs 26 of the plate 21, which is arranged between this approach and the flywheel · For their guidance and according to the illustrated Embodiment these springs are supported on the ground from pans or depressions 29, 30 which are provided in the flywheel 10 and in the lugs 26 of the plate 21.

Each of the lugs 26 of the plate 21 is also an arm 31 assigned, which connects the plate 21 to the cover 14, for what purpose the latter on its outer circumference has a third set of panels 32, each arm 31 at one end with one of the panels is riveted and at its other end to the corresponding one Approach of the plate 21, which arm 31 extends in a tangential direction, i.e. in one direction, that of the radial direction along which it is attached to the plate 21 is attached, is substantially perpendicular.

In the illustrated embodiment, each is tangent iale arm 31 formed by a tongue made of thin sheet metal.

On the dem. Flywheel 10 facing opposite side the intermediate plate 21 has a protruding conical support

009840/1485

surface 35, the diameter of which in the direction of the cover 14 increases and whose half-angle at the vertex is Al. This support surface 35 forms an annular space 23B with the cover 14, which radially extends the space 23A and in which the balls 24B are arranged.

Between its outer circumference and its inner circumference, the cover 14 has the following ring zones in succession fe on: a peripheral zone which, in addition to the fields 15, 27 and 32, also has fields 36 which are related to the fields 32 on the fields 27 are angularly symmetrical, as well as one first conical surface 37 and a second conical surface 38,

The conical surface 37 has an increasing diameter in the direction of the plate 21 and its half-angle at the apex A2 is smaller than Al of the conical bearing surface 35 of the plate.

The conical surface 38 has a substantially larger half-angle of about 90 ° at the apex and also has one in the direction of the plate 21 increasing diameter.

In the embodiment shown, it is this conical surface 38 which has an axial offset D of the plane PB Centers of the balls 24B with respect to the plane PA of the centers of the balls 24A ensures which plane PB

009840 / U86

the plate 21 is closer than the plane PA.

In the idle state, which is shown in FIGS. 2 and 3, the springs 28 hold the plate 21 at a distance from the flywheel 10 so that the friction disk 17 is not clamped. The balls 24A resting against one another occupy the base of the annular space 23A. The balls 24B, the number of which is the same as that of the balls 24A, are each in contact with two balls 24A, as best shown in FIG. 1, and are therefore isolated from one another. They are also in contact on the one hand with the conical bearing surface 35 of the plate 21 and on the other hand with the conical bearing surface 37 of the cover I ¹ *. These conical bearing surfaces are exposed to the axial force of the springs 28 and, as a result of their design, exert a force on the balls 24B, 24A whose radial component is directed towards the axis of the coupling and tends to bring these balls as close as possible to this axis keep.

As soon as the driving shaft 13 begins to rotate, drives they attach the flywheel 10, the cover 14, the plate 21 and the cage 22, all of which are non-rotatably connected to the flywheel are. The balls 24A, 24B that are in contact either with the lid 14 and the cage or the cap 22 or with the lid 14 and the plate 21 are also taken for rotation. - '

0098407 U8S

In this context it is important to emphasize that despite this joint movement, the balls 24A, 24B do not can perform relative circumferential movement with respect to each other as a result of their original nesting. There therefore they cannot collide, they are from this one No noise source point of view.

Of course, the balls 24A, 24B in their entirety "exert a certain relative circumferential movement with respect to the walls of their annuli 23A, 23B. It is however, it is about a rolling movement that is practically noiseless.

As soon as they are set in motion about the axis of the clutch, the balls 24A, 2IB are subjected to the effects of centrifugal force exposed, which has the tendency to displace it radially.

The balls 24B then penetrate like a wedge between the conical bearing surface 35 of the plate 21 and the conical bearing surface 37 of the cover I ¹ + and subject these bearing surfaces to the exertion of a force, the axial component of which pushes them apart. Since the cover 14 cannot be displaced, the balls 24B cause an axial displacement of the plate 21 in the direction of the friction disk 17 against the action of the springs 28. Now

009840 / H85

2O135T9

finds, when the speed of the driving shaft 13 is sufficient, a "grinding" of the friction disc successively 17 and then the clamping of the latter takes place, whereby the clutch is engaged.

During their radial centrifugal movement, the balls 2UB never lose contact with the balls 2UA, which on the contrary, since they are not braked directly by the counterforce of the springs 28, press against the balls 2UB * and add their effect to that of the latter. ^; .

In this way, the balls 2UB stay through the balls 2UA "wedged", x * elch the latter for their part and although they no longer abut one another, through which the balls are wedged.

For this reason, the radial centrifugal movement of the balls 2UA, 2UB takes place without a relative circumferential movement the same, i.e. bump-free ..

In addition, the radial distance R of the annular spaces is 2 3A, 23B between the base Fi, which is assumed to be cylindrical, of the annular space 23A and the cylindrical surface F2, 'which dirch the contact points of the balls 2UB with the conical Support surfaces 35, 37 is placed when clamping the

009840/1486

Disc 17 (Fig. H) smaller than twice the diameter of a ball 24A, 24B. This condition will remain even when the maximum permissible wear is achieved, maintained, in which latter case the balls 24B taking. Indicated in Figure by dot-dash lines radial end position in which the surface of the layer F is F2 ¹ 2 and in which the Big R receives the value R ^f.

A ball 24E can therefore in no case at one of the Balls 24A move past surrounding them and remain wedged by them under all circumstances.

When the speed of the driving shaft or drive shaft decreases, the balls 24A, 24B gradually take up their starting position again under the action of the springs 28, again without a relative circumferential movement. As soon as this speed has become sufficiently low that the plate 21 loses contact with the friction disk 17, the clutch is disengaged.

In this connection it is important to mention that due to the displacement D of the plane PA for the centers of the spheres 24A with respect to the plane PB of the centers of the spheres 24B the balls 24A reinsert the cage during centrifugal motion touch during their centripetal return movement. In fact, this offset D has the effect that the

00984Q / UI6 Sao original

contact force occurring between balls 24A and 24B has an axial component directed towards the cover IM · and which presses the balls 24A against it, from the cage 22 but pushes away.

As briefly outlined above, this arrangement has one double advantage: on the one hand, the locking cage does not need to take on any major stresses, so that it is economical ais thin sheet metal can be made, which also allows it to be economically on its inner circumference Lid 14- can be riveted, and on the other hand are the occurring frictional forces are lower.

In this context, reference is made to the graph in Fig. 5, in which the speed N of the driving shaft is plotted on the abscissa and the torque Cl of the driving shaft and the torque C2 transmitted by the clutch on the ordinate. As a result of the internal friction, the curve representing the torque C2 branches into two arms B1, B2, one of which corresponds to the increasing torques and the other to the decreasing torques. This branching is usually referred to as "hysteresis" one and the same torque value, for example the torque value GL2, at which a "grinding" of the friction disk 17 takes place on the plate 21, two possible values Nl, N2 of the speed of the driving '

. -, - Kr, ^ 00984Q7U86 ^ aSiOS ■ "

Wave match. As mentioned, this disparity can be disturbing in certain cases.

Because of its low internal friction, the inventive Centrifugal clutch only has a low hysteresis.

To explain it should be mentioned that in the inventive Centrifugal clutch the distance Ml, 112 of the grinding torque about 100 rpm. concerned, while he was comparable to the earlier Designs usually 300 U / Ilin. reached.

The value of the half-angles explained above at vertices A1, A2 is not indifferent, since it is possible by a suitable choice of these angles to achieve that the axial component of the ^{force exerted by the balls 2 1} IB on the plate 21 is compared with the centrifugal force, which the mentioned force causes, by a factor K larger than 1 f is multi- plied.

However, there is no jamming of the balls 24B between the conical bearing surfaces 35, 37 and / or too strong a marking To avoid these bearing surfaces by the balls mentioned, this multiplication factor preferably applies 1, 2 or 1.3 limited.

In this case the angle Al is between 70 ° and 80 °

009840/148 5 ^ßm original

preferably about 75 ° and at the same time the angle is Ä2 between 50 ° and 60 °, preferably about 55 °.

Preferably and around too strong a marking of the bearing surfaces 35, 37, the plate 21 is made of special cast iron manufactured whose strength properties are equal to or superior to those of steel. Furthermore, the lid IU is preferred produced by a drawing work, making him through. Work hardening is given considerable hardness.

Finally, it is also interesting to point out that with each engagement or disengagement of the clutch, the tongues 31, which erfindungsger.äß the plate 21 with the. lid 14. Connect for rotation, through elasticity and as a result of it tangential arrangement and its circular symmetry a slight helical relative movement of the plate 21 with respect to cause the cover 14 * As a result of this helical movement is the marking of the balls 24B on the bearing surfaces 35, 37 Advantageously not punctiform, which makes the foils ge ** be mitigated, and the risk of disguising the bullets 24A, 24B during their centrifugal or centripet albev: e ~ ung is lower * ...

The invention is not limited to that described and illustrated Embodiment limited, but includes all modification possibilities, especially with regard to the balls where

the number of annular rows can be greater than two and the diameter of which can be different per row, as well as with regard to the holding means, which the balls of the innermost Row are assigned. In the example shown, the holder is ensured by the fact that in the idle state the balls in the innermost row collide. In other embodiments not shown, this is Support ensured by formations of the cover 14 or the cage ^ 22 or both parts.

In a further embodiment, not shown, the bearing surface 38 of the cover 14 is on the axis of the coupling perpendicular.

The embodiment shown as a variant in FIGS. 6 and 7 has a flywheel 110, which is attached by screws 111 is attached to the flange 112 of a driving shaft 113 (FIG. 7) and that with an annular friction disc 114 cooperates, which is firmly connected on its inner circumference with a hub 115, non-rotatably on a driven shaft 116 is arranged and carries friction linings 117 on its outer circumference on both sides.

An assembly unit 118 is attached to the flywheel 110 on its side opposite the driving shaft 113, which is shown in Fig. 7 with thick lines.

009840 / U85

This assembly unit comprises an annular cover 119, which, on its outer circumference, has a first sentence of has fields 120 located in the same plane, those on the flywheel 110 for inserting screws 121 for System can be brought, which secure the attachment of the cover to the flywheel.

The assembly unit 118 also includes between the annular cover 119 and the friction disc 114 an annular pressure plate 123. The latter is with three radial Approaches 124 provided, which are regularly distributed over the circumference, and points to the passage of these approaches the cover 119 on its outer circumference cutouts 125, which are laterally on both sides by a second set of in the same plane lying fields 127 are limited.

Each of the lugs 124 of the pressure plate 123 is assigned an arm 128 which connects the plate 123 to the cover 119. For this purpose, "each arm 128 is at its one end by a rivet 129 with the corresponding lug 124 of the plate 12 3 connected and riveted at its other end to one of the fields 127 of the cover 119. Everyone Arm 128 is located on the side of plate 123 facing flywheel 110 and extends in a tangential direction, i.e. in a direction which is essentially perpendicular to the radial direction,

^; ". ■ ■; £ S % « Cl

0098AO / H85

on which it is attached to the plate 123,

In the embodiment shown, each tangential arm 128 is in the form of a tongue made of thin sheet metal and a single tangential arm 128 is provided for each radial extension 124 of the plate 123, which extends in the circumferential direction in the same way as the other arms of the coupling .

The plate 12 3 is also axially on the cover 119 by a Set of three lift-off springs 130 attached, which are angled regularly are distributed over the inner circumference of the cover 119.

Such a lifting spring is shown separately in FIG. 8 in FIG Fig. 9 shown. It is formed by a piece of wire which is shaped in a suitable V / eise and wound so that two coaxial coil springs 131Λ, 131B are obtained, h which have free ends 132A, 132B and are connected by a central double arm 13 3 which is bent in a U-shape.

The helical coils 131A, 131B of a small spring are made by './indings wound in the opposite sense formed and the respective ends 132A, 132B have end pieces 134A, 134B, which are directed towards each other, outside the Rolls 131A, 131B, which end with mutually parallel end sections 135A, 135B.

009840 / U86

SAD ORfGlNAi

As for the center arm 133, it is at 136 in the mowing of its end angled.

The lifting springs 130 are arranged in the assembly unit 118 in the following manner.

The cover 119 is opposite the pressure plate 12 3 a recessed annulus IUQ, which by a cylindrical Outer wall 141, an essentially inclined wall 142 and bounded by a cylindrical inner wall 143 whose free edge is perpendicular to the axis of the coupling is bent back as shown at 144.

The circumference of this edge 144 is provided in pairs Cutouts 146 provided in such a way that iJasen 147 received that extend in the circumferential direction.

Opposite a pair of cutouts 146 has the cylindrical inner wall 143 of cover 119 has an opening 15.

This opening is used to guide the Kittelarnves 133 through a lift-off spring 130, whose helical V.'ickel 13IA, 131B stay outside the ring area 140 * while the Ends 132A, 132B of this spring in the associated cutouts 146 engage and rest against the inner surface of the

0 * _{9840/1488 ßAD}

Noses 147 limited by these cutouts are supported.

Also lies the angled end 136 of the central arm a lifting spring 130 against the corresponding radial projection 124 of the pressure plate 12 3, in 'which system he is held by a tab 155 which is attached to the mentioned approach by the same lliet 129 by the already the associated tangential arm 12 8 is attached, ^ on the other side of the attachment, based on this arm, is attached.

Opposite the annular space 140, which is formed by the cover 119, the plate 123 has a protruding one conical bearing surface 156, the diameter of which in Direction to the cylindrical outer wall 141 of the lid towards the center.

Liese conical bearing surface 156, which is locally at the point of each lifting spring 130 for the passage and the support des. '! ittelarrr.s 13 3 of the same is interrupted, closes at least partially the recessed ring space 140 formed by the cover 119 in order to create a annular row of balls 160 to hold.

Inventor.il.i is this row of balls divided into three groups the 'littelarr.e 133 of the lifting springs 130 separated and inside

00984Q / U86

BATH ORIGINAL

half of these groups are the end balls in contact with the central arms 133 of the lifting springs 130, which the , Limit group.

It should also be mentioned that, in the rest state, each ball 160 is on the one hand in contact with the pressure plate 12 3 is located at one point of the conical bearing surface 156 - of the same and on the other hand in contact with the cover 119 at two points of the same, one of which is on the sloping wall 142 of the lid and the other on the inner wall 143.

For this reason, and because of its special design, the cover 119 by itself largely acts as a holder of the balls 160 without it being necessary to attach any end cap to it for this purpose, which confession is characterized · that the lid 119 has two walls 142, 143 which are inclined to one another at an acute angle.

In the illustrated embodiment, the balls have 160 all have the same diameter, which is what the insertion of the same as well as the manufacture of the cover 119 and / or the plate 123 simplified. The balls could of course have different diameters, in which case the walls 142, 143 of the Cover 119 for this purpose 'has a special training

0 098A0 / U85

- e.g.-

would practice.

In the idle state shown, the lifting springs 130 keep the pressure plate 123 at a distance from the flywheel 110, so that the friction disk 114 is not clamped. The balls 160 occupy that part of the ring brown 140, which is furthest inward radially.

As soon as the drive shaft 113 begins to rotate, it takes the flywheel 110, the cover 119 and the plate 12 3 rait, all of which are non-rotatably connected to the flywheel. The balls 160 that are attached to the lid 119 and the plate 12 3 are in contact, are also driven to rotate, but they are as a result the separation of the balls by the lifting springs 130 prevents any common to these two organs Perform circumferential agitation, which causes wear.

As soon as they are set in motion around the axis of the coupling the balls 160 are subjected to the effects of centrifugal force tending to displace them radially. They therefore penetrate like a wedge between the conical bearing surface 156 of the pressure plate 123 and the conical Support surface 142 of the cover 119, so that this Surfaces are subjected to a force that is axial

009840 / U85

Outward component has. Since the cover 119 with reference to the flywheel 110 is axially stationary, the balls 160 cause an axial displacement of the plate 123 in the Direction to the friction disc 114 against the effect of the Lift-off springs 130. Then and when the speed of the driving shaft 113 is sufficient, it occurs in succession grinding the friction disc 114 and then clamping the latter, engaging the clutch will.

When the speed of the driving shaft 113 decreases and as a result of the action of the lifting springs 130, which tend to pull the pressure plate 123 in the direction Returning to the lid · —1-19 ", the balls win 160 progressively back to their starting position. As soon as the mentioned speed is sufficiently low so that the Plate 12 3 the contact with the grinding wheel 114 ver «. the clutch is disengaged.

The support of a lift spring 130 in the circumferential direction is ensured at the location of the central arm 133 by the edges of the opening 150 of the cover 119, through the he extends, and on the other hand siurc.h the flanks of the radial hat, which in the conical contact surface of the 'pressure' plate 123 provided for the passage of the arm mentioned is.

0098AO / Uli

In this context it should be emphasized again that the lifting springs 130 are built into the assembly unit 118 and therefore this very quickly and very easily can be attached to a flywheel 110.

Finally, it is important to emphasize that the invention Training for particularly economical designs, especially in comparison to the previously known Execution forms leads.

The invention is of course not limited to the described and illustrated embodiments, but rather can experience various changes within its framework.

Patent claims:

0098A0 / U85

⁸ ^ ORIGINAL

Claims (3)

Patent claims: 1.) Centrifugal clutch of the type comprising in series connection between a driving wave and a driven shaft on the one hand a centrifugal force f direction, which is dependent on the speed driving shaft is fastened, and a pressure plate act, which is axially movable and rotationally fixed to the cover is connected, and secondly a coupling device which ä between the pressure plate and the driven shaft \ <tlvkt and having a friction disc which is axially movable and with the driven shaft is rotatably connected and which also carries friction linings between the flywheel and the pressure plate, lifting springs loading the pressure plate in an axial direction which leads away from the flywheel, characterized in that the cover (14, 119) is designed so that it especially with a conical bearing surface (35, 156) of the pressure plate 009840 / U85 (21, 123) increasing in the direction of the lid Diameter forms an annular space (23A, 23B, IUO), the can accommodate at least one annular row of balls which form the mentioned flyweights, wherein the balls are in contact on the one hand with the conical bearing surface (35, 155) of the pressure plate and on the other hand with a conical inflation surface (37, 38, 142, 143) of the Lid of increasing diameter in the direction of the pressure plate are in contact and the balls holding means assigned. 2. Centrifugal clutch according to claim 1, characterized in that d 3.Ά two annular rows of balls (24A, 24B) are provided radially offset from one another and the refrigerants interact with the outermost row of balls and are formed by the innermost row of balls. 3. Centrifugal clutch according to claim 2, characterized in that the holding means of the outermost row of balls alone consist of the balls (24A) of the innermost row, the balls (24B) of the outermost row each in contact with are two balls on the innermost row. 009840/1485 bad original 4. Centrifugal clutch according to claim 2, characterized in that the balls of the innermost row with reference be held exactly in their position on each other if the coupling does not turn, either because the balls are in contact with each other or because that they are held in place by the formation of their room are, for example, through training in the cover (IM) or in an Xäf.i ;; (22). 5, centrifugal clutch according to claim 2, characterized in that that-the ringraun, in which "the two rows of balls (2UA, 2UB) are arranged, has a radial extension, even when the clutch device is engaged and the friction linings (20) have the maximum permissible Abnut taper, smaller than the surrn caused by the diameter of the balls in the innermost row and the diameter of the balls in the outermost row is formed. 6. Centrifugal clutch according to claim 2, characterized in that because "the plane (PA) of the centers of the balls (2UA) the innermost row in the direction of the lid (14) r.it is axially offset with respect to the plane (PB) of the centers of the balls (243) of the outermost row, (D). 0098A0 / U85 ORIGINAL 7. Centrifugal clutch according to claim 6, characterized in that the cover (14) is in contact with the balls (24A) of the innermost row a second bearing surface perpendicular to the axis or conical from in the direction of the flywheel having increasing diameter. Γ. Centrifugal clutch according to Claim 2, characterized in that dsÄ only the balls (2UD) of the outermost row in contact on the one hand with the conical bearing surface (35) of the intermediate plate (21) and on the other hand with the first conical bearing surface (37) of the cover (14) and that the conical support surfaces (35) of the Z '.' Ischenplatte (21) one half; angle (Al) on vertex between 70 ° and PC and preferably of about 75, and the conical bearing surface (37) of the lid Half angle (A2) at the vertex between 50 ° and 60 ° and preferably of about 55. 9. Centrifugal clutch according to claim 1, characterized in that there? the ring receiving the balls (24A, 24B) together through the cover (14), one fixed to this connected closing cage (22) and the pressure plate (21) is re-formed. 0098A0 / U85 bad original 10. Centrifugal clutch according to claim 1, characterized in that that the cover (14) made of deep-drawn sheet metal and the intermediate plate (21) made of cast iron of high mechanical strength is. 11. Centrifugal clutch according to claims 1 and 9, characterized characterized in that the cover (14) and the end cage (22) both have the shape of a ring and the end cage on its inner circumference around the inner circumference of the lid. ■ 12. Centrifugal clutch according to claim 1, characterized in that that the intermediate plate (21) with the cover (14). d-ur; ch arms (31) are allied, which are symmetrical in a circle are distributed and each superimposed by a tongue or several Tongues are formed, each of these arms preferably to a radial direction through its Attachment to the pressure plate (21) runs, essentially is perpendicular. 13. Centrifugal clutch according to claim 2, characterized in that that the balls (24A, 24B) of the two rows of balls have the same diameter. 0098A0 / U85 14. Centrifugal clutch according to claim 1, characterized in that the lifting springs (130) are arranged on the cover (119) and can act by pulling on the pressure plate (123) and that each lifting spring consists of a. Wire section, which in Forrr. are curled by two adjacent helical '.vickeln (131A, 131B), which
have free ends (132A, 132B) and which are united by a U-shaped central double arm (133) which ends bear against one of the two organs formed by the cover (119) and the pressure plate (12 3), while the central double arm (133) abuts against the other of the organs mentioned. 15. Centrifugal clutch according to claim 14, characterized in that that the ends (132A, 132B) of the lifting springs (130) fc gezen the cover (119) and its central double arm (133) against the pressure plate (123). 16. Centrifugal clutch according to claim 14, characterized in that the ends of the lifting springs (130) in holding cutouts (146) engage, which are provided in the cover (119). 009840/1485 bathroom 17. Centrifugal clutch according to claim IM-, characterized in that that the helical VJickel (131A, 131B) of a lifting spring are coaxial and their './indungen are wound in the opposite sense. 18. Centrifugal clutch according to claim IU, characterized in that that the middle double arm (13 3) of a lifting spring is thereby held on the pressure plate (12 3) v? ird that he is between this and one at this attached tab (15 5) extends. 19. Centrifugal clutch according to claim 18, characterized in that that the tab (155) on the pressure plate by means of an Iliets (129) is attached, which is used for attachment an arm (128) is used to connect the pressure plate (12 3) to the cover (119). 20. Centrifugal clutch according to claim 19, characterized in that that the mentioned tab. C155) and the twisted one Arm (128) are on opposite sides of the pressure plate (12 3). 21. Centrifugal clutch according to claim 14, characterized 0098407 U8S shows that the central double arm (133) of a lifting spring passes through one provided in the cover (119) Opening (150) extends. 22, centrifugal clutch according to claim IM-, characterized in, that the central double arms (133) of the lifting springs form the holding means for the balls (160) and these divide into several groups. 23, centrifugal clutch according to claim 1, characterized in that that the lifting springs (130) form the holding means assigned to the balls (160) and divide them off. 24, centrifugal clutch according to claim 23, characterized in that that the lifting springs (130) are arranged on the cover (119) and by pulling on the pressure plate (123) can act and that each lifting spring consists of a wire section, which is in the form of two helical each other adjacent coils (131A, 131B) which have free ends (132A, 132B) and together are united by a central U-shaped arm (133), and that the central U-shaped arm is at least more specific Abhebefedern forms the holding members mentioned. 0098A0 / U85 25g centrifugal clutch according to claims 22 and 23 ₉ characterized in that each ball (160) in the rest state is in contact with the cover (119) on two walls (142, 143) of the same, which walls are inclined to each other and an acute angle between to lock myself in. For SOGIETE ANONYME FRANCAISE DU FERODO 0098A0 / U85 Blank page