DE666542C - Friction gear change transmission, especially for motor vehicles - Google Patents

Description

The invention is directed to a friction gear change transmission, in particular for motor vehicles, of the genus in which two in circular segment-shaped grooves the same axis lying friction disks adjustably arranged friction rollers provided are. In known devices, the friction rollers are related in one or more their angular position as a function of one another

arranged to standing sentences. So you want change the transmission ratio, each time a whole set of related Friction rollers are adjusted, which requires a certain amount of force.

The invention differs advantageously in that a control device connected to only a single friction roller for the purpose of changing the transmission ratio which is set independently of the other roles, and that a compensating device, z. B. the roller carrier, responds to the various torques transmitted by the individual rollers and the Rolls automatically brings them into positions in which they transmit the same torques.

The invention has the advantage that only a relatively small Force to adjust the one role, which can be referred to as a control role, required is. As a result, even a less powerful person is able to use the transmission to be adjusted while the car is in motion. There is also the possibility of an automatic Adjustment of the gearbox under the supervision of a speed controller provide, which acts so that it automatically adjusts the engine speed within the desired Limits. Once the regulating roller has been adjusted in this way, all the remaining friction rollers become the same in a short time Adjusted way so that all rollers transmit the same torque.

The invention is illustrated by way of example in the drawing; there are:

Fig. Ι longitudinal section through the transmission, seen from the left side of the vehicle,

Fig. 2 is a plan view of Fig. 1 in the direction of arrows 2-2, certain parts broken away,

3 partial diagram of the joint arrangement for the regulating roller,

Fig. 4 view of the transmission from the right, certain parts of the housing broken away,

Fig. 5 cross section along line 5-5 of Fig. 1,

6 a section along line 6-6 of FIG. 5 to illustrate the controller connection,

7 shows a section along line 7-7 to illustrate a device that can be regulated by hand to engage the forward and reverse gear,

8 shows a section along line 8-8 in FIG. 431 9 cross section along line 9-9 | Fig. I, ~

Fig. 10 is a diagram of the individual parts of the Rule role,

11 shows a diagram of the friction disks as well as the intermediate rollers and their storage on the spokes of the roller carrier,

Fig. 12 is a diagram of the movement of the device for automatic compensation of the through the various roles of the torque transmitted by one set of friction rollers (Fig. 11 seen from the right),

13, 13 a and 13 b are schematic representations the movement of a lever that can be pivoted from the outside to tilt the regulating roller and limiting their angle of inclination. The change gear is in a housing arranged. A large partitioned housing space 20 accommodates the friction gear transmission; a smaller one, 22, located in front of it, contains a transmission for coupling the friction wheel transmission with the motor for forward or reverse gear, furthermore an oil pump with drive and an automatic speed controller. The bell-shaped part 23 at the front end of the housing is used for fastening on the usual clutch housing.

The housing H has a rear transverse wall 24, an intermediate wall 25 between the two housing spaces 20 and 22 and a front wall 26 in which bearings for the main shafts sit. Furthermore, the housing is provided with a removable cover; heat-distributing ribs and ventilation openings can also be provided.

The main drive shaft 30 (Fig. 1), e.g. the main clutch shaft common in motor vehicles, the front end of which carries the usual friction clutch, not shown, is at its rear end in a ball bearing 31 of the intermediate wall 26 mounted; the shaft 30 takes the front one in a bore End of a shaft 32 arranged in roller bearings 33. The back end of the Shaft 32 runs in ball bearings 34 of the partition 25 and also has a Bore for receiving the front end of a shaft 35 which is in roller bearings therein 36 is stored. The rear end of the shaft 35 is annular through interposed Parts stored in a ball bearing 37 of the rear wall 24. To the intermediaries Parts mainly include an externally flanged nut 38 which attaches to the 6υ shaft screwed and with radial grooves 39 for the setting of a wrench is provided, whereby it can be adjusted. Around the nut 38 there is a universal joint] 'och .40 arranged, which the shaft 35 with a: / z "u the drive wheels leading shaft more common

t | it connects. The yoke 40 has a . tisatz for the inner race of the ball bearing ^ 7 and is at its front end with equipped with an inner flange 41 which engages around the nut 38. With the inner flange the yoke is supported by means of a thrust bearing 43 on the outer flange 42 of the nut 38; the yoke 40 can rotate relative to the shaft 35 to a limited extent. Of the Purpose is explained below. The aligned axes of the shafts 30, 32 and 35 form the main axis of the transmission.

As illustrated in FIGS. I and 5, the intermediate shaft 32 can be from the drive shaft 30 from depending on the choice of the driver through the illustrated, known per se, direct and reversing gear trains of the countershafts 62 and 65 are driven forwards or backwards.

In the space 20 of the housing are three coaxial friction disks in a manner known per se 90, 91, 92 arranged, which are provided with circular segment-shaped annular grooves. The middle friction disk 90 carries such annular grooves on both sides, while the disks 91 and 92 are only provided with annular grooves on the sides facing one another. The transmission of the rotation from the central disc 90 to the two lateral ones Discs 91 and 92 is made in a known manner by friction rollers 94, 95, which come in two sets three roles each are provided. The two outer disks 91 and 92 are with the driven shaft 35 firmly connected, while the middle disk 90 by a still to descriptive device is coupled to the driving shaft.

The rear roller set 94 includes, among its rollers, the regulating roller 94 ^M ; according to FIGS. 1, 2 and 9 it lies in the upper part of the unit, ie its axis of rotation lies in an almost perpendicular radial plane. The regulated roles of the front set are labeled 95.

It is clear that when the friction no disc 90, for example clockwise, the friction discs 91 and 92 and therefore the Shaft 35 in the opposite direction of rotation, d. H. counterclockwise, rotated, and vice versa.

In the exemplary embodiment shown, the motor can be the middle one by virtue of the countershaft Drive friction disc 90 both forward and backward so that the friction disc can be addressed as the driving disc of the friction gear. Look for the vehicle faster than the engine to run like that

act the friction disks 91, 92 driving, while the friction disk 90 is now the driven Disc is what transfers the power from the vehicle wheels to the engine. In order to pass on the force between the driving shaft 32 of the transmission and the driven shaft 35, the shaft 32 is inevitable connected to the middle Reibscheibego by a coupling member, attached to the rear end of the shaft 32, moved past the disc 91 with play and attached to the middle friction disc 90 so that it receives the rotational force from the Wave 32 transfers to this. The coupling comprises a cylinder 100 with openings ι ο i, 102 and is at the front on a wheel disc attached, the hub 104 sits on the shaft 32, on the other hand, on the circumference of the rear middle friction disc 90. As Fig. 1 shows, sits on the hub 104, a gear 66, the engages with internal projections in grooves in the hub and in grooves in shaft 32. One Nut 108 pulls wheel 66 and the inner race of bearing 34 backward against it a shoulder on the flange 103.

The middle friction disk 90 is arranged concentrically to the shaft 35 on a muffle 10, which surrounds the shaft with a lot of play and is attached to the housing H with the aid of arms.

The front friction disk 91 is non-rotatably fixed on the shaft 35, namely by a flange 120 fastened on the shaft into which the disk with radial ribs (at 121) engages and against which it is pressed by a loading device to be described will.

The friction disk 92 is also non-rotatably connected to the shaft 35, but to axially displaceable a small amount. Behind the friction disc 92 are on the shaft 35 grooves 130 are provided in which with corresponding Springs a wheel disc 131 engages longitudinally displaceably; against their hub 132 presses the front attachment surface of the nut 38 screwed onto the shaft 35. Between the friction disc 92 and the wheel disc 131 are connected by interlocking radial grooves 133, 134.

The wheel disc 131 takes in on the circumference a shoulder 140 an annular spring 141 which decreases in thickness from the outside to the inside. With its front edge presses the spring 141 against the friction disk 92, namely with one adjustable by the nut 38 Tension. So between the rollers 94, 94 ^, 95 and the friction disks 90, 91, 92 create and maintain the required pressure. When overloaded, the Washer 92 is able to give a little axially.

Except for the spring 141 for normal pressing the friction rollers and disks Fig. ι shows another additional device that adjusts the pressure between the friction disks to the torque transmitted in each case. This is done by roles 154, which between mutually inclined surfaces on the back of the friction disc 92 and corresponding. inclined surfaces are arranged on the front side of an annular disk 150.

These devices are not part of the invention.

The shaft 35 is surrounded by an axially displaceable tube 161 which at each end carries a group of arms 160, 162 arranged like a star beam for receiving the friction rollers 94, 94 ^M , 95. The arms 160, 162 are also movable transversely to the shaft axis, and the arrangement can be such that the tube is capable of transverse movement. Furthermore, a limited relative movement of the arms 160, 162 and the tube 161 is provided, but only transversely. In the circumferential direction and axially, the arms and the tube are immovable with respect to one another. However, the arms can also be connected to the pipe in a completely immovable manner; then the tube itself is also arranged to be transversely displaceable.

In the exemplary embodiment shown, each of the three rollers 94 ^M , 94 of the rear group is held by a spoke arm 160 of the tube 161 which is arranged in a floating manner. The tube passes through the bearing sleeve 110 on which the middle friction disk 90 is rotatably mounted. Each roller 95 of the front group is mounted on one of the three spoke arms 162; these form one piece with a hub 163 which is keyed onto the tube 161 and ^{tightened by a nut 163 s} against a shoulder of the tube. The center lines of arms 160 and 162 lie in pairs in the same radial planes.

So that the pipe 161 and the Arms 160, 162 existing floating structure does not rotate, it supports itself with two resilient arms 164 (Fig. 9) on the housing, which are made in one piece with the tube 161 can exist. The arms 164 lie in the same transverse plane as the radial spoke arms 160 and are slightly curved to avoid rollers 94; they take part spherical ends 165 in bearings on both sides of the housing. The spherical ends 165 of the two arms 164 sit in upper and lower bearing sockets 166, which are by means of Ball bearings 168 on blocks 167 of the housing support. These balls 168 are guided through a ball cage 169. Since the each other opposite surfaces of the ball sockets 166 and the bearing blocks 167 par-

are allelic planes, the balls 168 roll with a lateral displacement of the bearing cups 166 relative to bearing blocks 167 on these levels. Therefore, lateral displacement of the bearing cups 166 is relative to the bearing blocks 167 possible under load with little resistance. The midpoints of balls 168 shift as the balls roll by half the amount of ίο lateral displacement of the ball sockets 166. The ball cage 169 that holds the balls 168 must shift by the same amount as the centers of the balls. Around The ball cage prevents the balls from slipping when the bearing is relieved 169 duroh pin 170 inevitably guided, those with spherical collars in the bores of the ball sockets 166, the ball cages 169 and the bearing blocks 167 fit; therefore, the pegs 170 can move laterally of the ball sockets 166 incline with respect to those three parts without jamming. Since the circle of contact between the middle spherical collar and the cage 169 halfway between the circles of contact between the other two collars and the ball socket 166 or block 167, the ball cage 169 is inevitably guided correctly.

This mounting of the arms 164 allows a limited movement of the floating Partly 160, 161, 162 parallel to a die Major axis and the centers of the plane containing spherical arm ends 165, however, prevents rotation around the main axis. Adjusting screws 171 are used for Limitation of movement.

The inside diameter of the tube 161 is much larger than the diameter of the shaft 35, the outer diameter smaller than the inside diameter of the bearing sleeve 110 (Fig. 1), whereby the lateral movement of the Rohrs and his arms is made possible.

However, the arms 164 are also designed to be resilient in themselves, and can therefore Tube 161 and its arms 160, 162 also in move perpendicular planes. The one consisting of the tube 161 and its arms 160, 162 The floating unit is therefore capable of limited movement in every direction, that is to say it is actually floating. Damping devices (Fig. 1 and 9) try to keep them in the central position. For this serve for the longitudinal direction cylinder 181 and piston 182, between which springs 180 come into effect (Fig. 1). The cylinders 181 lie against the friction disks 91, 92 while the pistons 182 are supported against the ends of the tube 161 via rings! In the vertical direction, the flexible arms 164 have a centering effect, while for the Side direction again special damping devices are provided.

In the plane of the arms 160, the tube 161 is pierced transversely; one of the two generated Bores 184 is illustrated in the section of FIG. 9. The outside end of everyone Bore is closed by a screw 185, which has a clock spring Piston pushes against shaft 35; so the rear end of the tube 161 becomes attached to the shaft 35 centered on the side.

Likewise, the front end of the tube 161 is uniform with respect to the shaft 35 by three centered around the shaft distributed spring arrangements, one of which in section in Fig. 1 is shown. A radial shoulder 190 on the hub 163 of the arms 162 takes in a radial bore 191 a hollow piston 192 on, which penetrates an opening of the tube 161 with a stepped extension 193 and is supported on the shaft 35. The extension 193 is perforated and with play through the tube 161 passed through, so that the interior of the hollow piston 192 connection with the annular space between the tube 161 and the shaft 35. Outside is hole 191 through a Completed screw 194, which with a cylindrical part 195 the hollow piston 192 leads. A compression spring 196 between the screw 194 and an outer flange of the Piston resiliently urges the piston against shaft 35, and so does the assembly in conjunction with the other similar arrangements on the front and rear End of the tube 161 the centering.

The friction rollers 94, 94 ^, 95 are with their Central planes parallel to the main axis, their axes of rotation are radial däi; u; therefore roll over they are located on the same circles on the friction disks 91, 92 so that these are opposite and rotate at the same speed as the friction disc 90. However, the rollers can incline so that their median planes are at an angle to the main axis, thereby causing it is possible that the friction disks 91, 92 assume other speeds than the disk 90.

The regulating roller 94 ^{M used} for control is mounted on one of the arms 160 and, together with the two further rollers 94 on the two other arms 160, forms the rear group of friction rollers. The three rollers 95 on the three arms 162 form the front group. The bearings for the three rollers 95 are the same; the bearings of the two rollers 94 differ from this only in the inclination of their spacers 205, described below. The arms 160, 162 end in a head 200 which is rounded on the outside and flattened on both sides (FIGS. 1, 2, 10 and 11). In the head sits at right angles to the die

The radial plane containing the main axis has a hollow pin 201, which is secured by a stud screw 207 is attached. A cylindrical roller carrier 202 is articulated on the pin which the roller is rotatably mounted. The roller carrier 202 is longitudinally slotted at 203; the slot surfaces are parallel and have Ouernuten 204, in which ribs 206 of the Engage angled spacer 205.

By virtue of this design, any roller 94 or 95 can be moved while it is on its support 202 revolves to incline the pin 201 as it is for changing the gear ratio is required.

The tube 161, each arm 160, 162, the Head 200 and spacer 205 can be parallel to the main axis and relative to move the rollers. Then each roller 94, 95 inclines together with its carrier 202 in one Direction obtained by moving its axis of rotation away from the main axis and the plane containing the roll centers results. The relocation of the roller axis of rotation unbalanced forces on the circumference of the roller arise from the radial plane mentioned, which move the roller in a helical line on the friction disks. This will caused the translation change. The roles are considered to be in their normal rotating planes revolving when their axes of rotation lie in radial planes, which are the main axis and contain the roll centers, with of course the median planes of the rolls are perpendicular to said radial planes, regardless of whether they are parallel to the main axis or not. They are only parallel to the main axis at Gear ratio 1: 1.

The control roller 94 ^ is mounted on the head 200 of its arm 160 similar to the other roles. ^{The roller carrier 202 M} articulated on the pin 201, however, has partially cylindrical recesses 210 (FIG. 10) in the surfaces of its slot, into which correspondingly designed blocks 211 engage. These are cut out of a cylinder with a segment-shaped cross-section, namely along planes that are at an angle to the axis. The ends of the pin 201 extend into openings 212 of the part-cylindrical block 211 and therefore restrict the movement of the block to a tilting movement about the pin 201 in a radial plane which includes the main axis of the transmission.

Play is provided between the slot surfaces of the roller carrier 202 ^M and the outer surfaces of the head 200. During assembly, the outer partially cylindrical surfaces of the block are brought into a common cylinder jacket surface and form a joint surface around which the carrier 2O2 ^M and the control roller can be pivoted, i.e. in a plane transverse to the main axis or around a line connecting the contact points between the roller and the friction disks . The axis of rotation of the roller emerges from the plane containing the main axis and the roller center point, so that it can reach a position with a different transmission ratio. Since the flat surfaces of the block 211, with which it rests on the parallel surfaces of the head 200, are inclined to the block axis, a longitudinal displacement of the floating tube 161 causes the axis of rotation of the regulating roller 94 * 'to be switched off in a similar manner to the axes of rotation of the other rollers 94 , 95 can be adjusted.

Changes the control role 94 ^ 'under the influence of the driver or an automatic controller The regulated roles 94, 95 acquire their decisive position for the translation automatically a position corresponding to the new translation, each with its corresponding Part of the burden takes over.

To adjust the regulating roller, a flat shoulder 215 (FIG. 10) is provided on the outside of the roller carrier 202 ^, which is parallel to the central plane of the roller 94 ^M and to its normal axis of inclination tt (FIG. 9). A bore 216 receives a pin 217, at the ends of which a bracket 218 is articulated by means of bores 218 ^ (FIGS. 1, 2, 9 and 10). An axial bore 219 of the roller carrier 202 ^Μ is used to receive a stop 220, the upward between two extensions

221 of the upper arm of the bracket 218 protrudes. It also sits in a threaded hole

222 of the roller carrier a screw 223, by means of which the projection 215 is attached to a bridge 224; two resilient arms 225 of the bridge extend along the extension 215 and are bent towards one another behind it. After the bracket 218, the extension 215 protrudes beyond the carrier 202 ^ and is, as shown at 226 (FIG. 3), curved about a center point α which does not coincide with the pivot axis b of the bracket 218.

On the lower leg of the bracket 218 has a friction surface 227 is provided, which abuts the lower surface of the roller 94 ^M. Another friction pad 228, which is formed separately from the bracket, lies between the upper bracket leg and the upper surface of the roller 94 ^ (Fig. 9). The friction pad 228 is bifurcated at 229 at its end remote from the center of the roller in order to accommodate a pin 230 which extends downward from the upper leg of the bracket. The inner end of the pad 228 mates at 231 with the curved end 226 of the lug

606542

215 ^{on and} d is also provided with two stop pins 232 at the top; these are not high enough to capture the spring arms 225 during the angular movement of the bracket 218. As shown in Figures 9 and 10, the upper arm of the bracket 218 is cranked upward at 233; the. Kr-öpfstii'ck is curved around the center point b (Fig. 3) and has sufficient distance from the curved end 226 of the extension 215 to receive a hardened ball 234. (Fig. 2), which on the friction pad 228 between the Ends of the resilient arms 225 and -the stops 232 lies. The pressure of the upper bracket arm on the ball 234 can be regulated by a nut 23S screwed onto the pin 217.

The middle piece of the bracket 218 carries a plate 236 which receives a ball 237 in a central opening for transmitting the pressure exerted by an operating lever. The plate 236 lies in the extension of the central plane of roll 94 ^M. If, viewed from the left in FIGS. 1 and 2, the friction disk 90 rotates in the clockwise direction - vehicle drive forwards - then the roller 94 ^M (FIG. 2) will rotate counterclockwise. The friction between the cushions 227, 228 and the roller causes the bracket 218 to be entrained in the direction of rotation of the roller as far as the stop 220.If the friction disc 90 runs counterclockwise (reverse travel), the roller 94 ^M rotates clockwise ( 2) and pivots the bracket 218 in the opposite direction to the first process up to the stop 220. The bracket 218 is therefore positioned at an angle to the line tt in one sense or the other, depending on the direction of travel.

Is the bracket 218 z. B-. in the limit position for forward travel, the ball 234 lies to the left of the line tt (FIG. 2). The pressure of the resilient upper bracket arm is chosen to be relatively low, and the ball transfers this slight pressure to the cushion 228. The right prong of the cushion rests on the stop 230, while the right pin 232 presses on the ball 234, as a result of which the ball in turn tensions the left spring 225 lightly.

In reverse, all of these forces and displacements are reversed. Left spring 225 urges ball 234 to the right into tighter contact with the two eccentrically disposed curved surfaces between which it sits; the cushion 288 cooperates until its left prong contacts the pin 230, and the ball is pressed onto the cushion 228 with greater force by these processes. As a result of the tighter contact between the cushion and the roller, the roller takes the bracket 218 with it over the axis tt until it reaches its limit position with respect to the friction disk 92. This is determined by the pin 220. The right spring 225 is tensioned by the ball, while the left pin 232 exerts pressure from the left. The friction pressure of the cushion 228 against the roller 94 ** is again lower in this position than on the other side,

When driving forward, the bracket 218 is in the position shown in Figure 2; the ball 237 on the plate 236 lies in that roller circle quarter which is on the Friction disk 90 rushes.

To switch to lower gear ⁷ 'is 5 94 ^ inclined the axis of rotation of the roller so that the roller describes a is demagnifying spiral on the disc 90 on the disc 92, however, an increasing spiral, comes whereby the roller to a tilted position. This process can be brought about by pressing down the ball 237 (FIG. 9), the roller being pivoted about an axis which passes through the center of the roller and the points of contact of the roller with the friction disks 90, 92; the axis of rotation thus leaves the radial plane containing the roller center point, specifically in such a direction that the extension of the axis of rotation of the roller passes to the left of the main axis (FIG. 9). So that the roller can transmit the rotary movement with a uniform translation, the axis of rotation must again be in the radial plane containing the roller center at the end of the switching movement; therefore, the central plane of the roller must be perpendicular to that radial plane. For the ratio ι: ι this position is parallel to the main axis, inclined to it for every deviating ratio, but in the steady state><«> of course always at right angles to the specified radial plane.

In these circumstances, the forces acting on the role are driven by the driving force and driven friction disks are exerted> <> 5, so balanced that they are the median plane of the role in the respective role plane and its axis of rotation in the specified radial plane. - '

The position of the roller 94 ^M reached automatically depends exclusively on the position of the ball 237 determined from the outside.

Corresponding ratios apply to reverse gear.

The adjusting device for the ball 237 is "5 illustrated in Figs.

A pivot shaft 240 is within at 241 a sleeve 242 seated on the housing. A forked one sits on the outside of the shaft Lever 243, inside a two-sided 12 »cross piece 244 with a slot 245 in the the ball 237 fits. Moving sideways

The ball 2 $ J in the slot is limited by four adjustable stops 246, between the inner ends of which the plate 236 of the bracket 218 can be accommodated.

The pivot shaft 240 is parallel to the tilt axis tt of the roller 94 ^, but slightly offset from it, for the purpose given below. In Fig. 2 this is indicated by arrows at χ . The offset is in the embodiment in a horizontal plane which coincides with the central plane of the roller 94 ^ when this is set to the translation ι: ι.

When moving forward, the bracket 218 is inclined towards the driving friction disk 90, and the ball 237 is located in the quarter of the circle of the roller 94 ^M adjacent to this disk. If the shaft 240 is now pivoted clockwise (FIG. 9 seen from the right and FIG. 2 seen from above), then the ball 237 is pressed down with the plate 236, and the bracket 218, the roller carrier 202 ^ and the roller inclined from the normal plane of rotation in a direction which causes the roller to spiral inward at friction disc 90. Disk 92 climbs outwards, as a result of which the disk 92 receives a lower speed than before, ie a smaller gear is reached. The pressure of the crosspiece 244 on the ball 237 moves the plate 236 to a new position, substantially parallel to the previous one, until the plate comes into contact with one of the stops 246, as shown schematically in Figures 13, 13a and 13b. The extent of the rotation of the pivot shaft 240 is limited by the plate 236, since this and the bracket 218 are secured against direct rotation and the great pressure of the friction disks on the running surface of the roller prevents this from being transverse to its center plane directly through an outer one Adjust the force. It is therefore not possible to change the speed too quickly.

Rotates to switch to higher gear

the pivot shaft 240 is opposite.

When reverse gear, the bracket 218 is in

a position in the circle quarter adjacent to the disk 92 instead of 90, ie the ball 237 now lies to the right of the line tt instead of the left (FIG. 2). The crosspiece 244 now acts on the ball 237 with its right arm. The same movements of the swivel

i) 5 wave 240 showing the small and large Shifting gears when driving forwards also has the same effect when driving backwards.

If the axis of the pivot shaft 249 coincides with the line tt , the on-order works correctly as described. However, sometimes you want the speed change to be different depending on the gear you are in. The offset χ of the axis cc of the pivot shaft 240 with respect to the axis tt is used for this purpose. As a result of the different position of the center lines around which the roller 94 ^ can tilt or around which the pivot shaft 240 is pivoted, the crosspiece 244 assumes different angular positions relative to the plane of rotation of the roller in its various tilted positions and therefore also relative to the plate 236, which lies in this plane of rotation. In Fig. 13 the role position for the translation ι: ι is illustrated; the cross piece 244 lies parallel to the plate 236, the axis of rotation of the pivot arm 240 falls into the plane of rotation of the roll. If the shaft 240 is now pivoted in the clockwise direction about axis c , the plate, the bracket 218 and the roller are given a limited inclination, the extent of which is determined by the distance between the lines ii in FIG. If the roller inclines in the lower gear (FIG. 13a), the crosspiece 244 adjusts itself at an ever increasing angle to the plane of the plate 236, so that a greater angular movement of the plate and therefore also of the roller itself is possible. When the roller moves into smaller aisles, the tilting speed increases. If you go from small gears to 1: 1, the successive impulses produce ever greater widths of the roller deflection until the position for 1: 1 is reached. If you go to higher gears 1: 1, positions according to FIG. 13b occur. The processes correspond to those described for the small corridors.

The distance i, i can be chosen so that the desired results are achieved.

To operate the pivot shaft 240, the forked arm wedged onto it is engaged 243 by means of a pin 247 to the rear end 250 of a flexible link. That other end 257 of the resilient handlebar is through lever linkage with a centrifugal governor, a hand lever and a damping device connected, as described below is.

The flexible handlebar (Fig. 4) has in connection with the end piece 250, which is on the arm 243 engages, a rod 251 which can be nested with a collar 252 in a Sleeve 253 slides under guidance through a sleeve 259. The other end of the tube is adjustable a second rod 254 is screwed in. Compression springs 256, which press against the collar 252, look for the handlebar in a certain position Length. The handlebar end 257 -connects the rod 254 at 258 to the long arm 260 of an angle lever 260, 206;

this is articulated at 261 on arms 262 of a pivot ^{piece 263, the pins 264, 264 s of} which are mounted in the housing.

On the hub 269 of the angle lever 260, 266 sits (FIG. 2) except for the arms 260, 266 yet another arm 267; arms 266,

267 engage with forked ends on pegs

268, which protrude from opposite points of a ring 306 which engages in a recess in the regulator sleeve 270. When the speed of the main drive shaft 32 increases, the governor sleeve 270 goes out as a result of the centrifugal forces of the governor balls. down; this pivots the arms 260 and 243 counterclockwise (FIG. 4). As a result, the roller 94 ^ inclines in such a way that its tilting movement to a higher gear is initiated, ie the roller 94 ^M moves on the driving friction disc 90 on an increasing spiral, on the driven 92 on a decreasing spiral. An increase in the engine speed causes higher gears by means of the controller and, conversely, a decrease in smaller gears.

The pin 264 ^{a of} the pivot piece 263 passes through the housing // and carries an arm 292 on the outside, to which the hand control (not shown) is connected. On the swivel piece 263, which can be swiveled by external forces by means of the arm 262, there are two short arms 293 approximately the length of the arms 262 (FIG. 4). The arms 293 engage a link 294, the opposite end of which is attached to the piston 295 of a damping device. The piston has openings 296, in a known manner, which are usually closed by a valve 297. The valve is urged against its seat by a clock spring 298. A bypass passage 301 (FIG. 8) can be regulated by a needle valve 302 in a known manner. Upward movement of the piston (when pivoting the part 263 counterclockwise, FIG. 4) takes place unchecked, since the valve 297 is then open. The downward movement of the piston, on the other hand, is braked. The damping is effective when shifting manually to a higher gear.

An oil container below the gearbox, which is separated from the main space 20 of the housing by a sieve 310, is used for lubrication. The bottom of the oil container consists of a corrugated metal plate 311 (FIGS. 1 and 5) which is screwed to the housing H in an oil-tight manner. An oil pump 315, 316, 317 is arranged in the chamber 22 (FIGS. 1 and 5) below the normal oil level. The pump pressure chamber 318 is closed by a spring-loaded outlet valve 320, which only allows oil to enter the oil container at a certain excess pressure. The drive of the pump shaft 321 is based on the main clutch shaft 30, so that oil circulation takes place as soon as it starts. ·

An oil pipe 330 leads from the pressure chamber 318 at right angles to one another arranged bores 331, 332 of the housing. A radial tube 333 presses in a liquid-tight manner onto a seat 334 which is arranged in the channel 332 so as to be able to slide radially. The other end of the pipe engages in a liquid-tight manner tapered bore of floating tube 161 and thus opens into the annular space between the tube 61 and the shaft 35 (Fig. 1). The seat 334 is loaded by a spring 336.

By virtue of this arrangement, oil can drop Pressure to get into the annulus around shaft 3 5 going through the top at each end described damping devices is completed with oil for the purpose of Be fed steaming. Arms 160, 162 are drilled radially at 337 (Figures 1 and 9). From these radial bores, the oil passes through lateral channels 338 (FIG. 10) into the hollow pins 201, from these between the heads 200 and the spacers 205 as well between these and the parallel inner surfaces of the slots of the roller supports 202; these surfaces can be equipped with oil grooves. For the rule role, the way goes of the oil accordingly. The running surface of the front friction plate 91 is oil jetted Lubricated and cooled from jet pipes 340, which are connected to one or more of the lateral damping cylinders 190 stand. Similar jet pipes can also be provided for the friction disks 90 and 92 be; for this purpose, the spring arms 164 are provided with channels 341, which are in connection stand with the annulus around the shaft 35 and deliver the oil from jet outlets 342

A pipe 350 (Fig. 5) with an adjoining channel 351 is used to lubricate the regulator, which leads diagonally upwards to the bearing 273 of the governor shaft.

Parts that are not necessarily lubricated by the oil pressure system are retained sufficient lubrication by the oil mist generated in the company; for corresponding openings, through which the oil splashing around. the storage areas can penetrate, must be taken care of, as this z. B. illustrated in FIG is; you can see here oil holes 352 in the sleeve 25 3 of the flexible handlebar and a Oil hole 353 in bearing 242 of pivot shaft 240.

In operation, the gear shift lever 81 (Fig. 2 and 5) is first operated so that he puts the gearbox in neutral

brings, d. H. the slidable coupling part 52 is from the main shaft 30 and the slidable Gear 63 of the countershaft disengaged, and gear 63 is out of engagement with reverse gear. The engine is started but does not transmit any movement to the friction gears. Only the oil pump starts to work and allows oil to flow to the parts of the friction gear and the regulator.

The controller is inactive, however, since it is in connection with the shaft 32 that is still present stands. The friction rollers 94, 94 * ', 95 are located in the position for low gear in which they were previously brought by the regulator.

To start up, the main clutch is now released in a known manner and the hand lever 81 is operated so that the claw clutch parts 51, 53 come into engagement with one another, whereby the shaft 32 is coupled to the motor. After the main clutch is engaged, the shaft 32 transmits its rotation to the governor and to the friction disk 90. This drives the rollers 94, 94 ^M and 95, which in turn set the friction disks 91, 92 and, via these, the driven shaft 35 in rotation. The spring 141 results in a sufficient axial pressure between the friction disks and the rollers when the load is lighter. When the load increases, the forked clutch 40 yields in the circumferential direction, as a result of which an additional axial force is transmitted to the friction disk and the friction pressure is increased as required; however, this is not part of the invention.

When the motor speed is increased, the controller will exert a counterclockwise force on the pivot shaft 240 (seen from the right in FIG. 9). The regulating roller 94 ^ will therefore incline in such a way that a change to a higher gear is initiated. Since the control roller is thus more heavily loaded than the other rollers in the group, the rear end of the tube 161 is displaced in a direction parallel to the plane of the rotational forces which seek to shift the roller axis, as a result of the pressure of the control roller on its arm in a direction corresponding to a lowering of the gear. The displacement of the axes of rotation of the two other rollers 94 is, as can be seen from FIG. 12, half that of the regulating roller 94 ^M and is directed in such a way that these two rollers 94 seek to move into a higher gear position.

The axial positions of the three roles are thus equal to each other, until they are all on the same Gear are set.

As soon as this has been achieved in the case of the roller group 94 ^M , 94, it is also implemented in the case of the other roller group 95. Because the combined rotational force of the roller group 94 ^M , 94 has become greater than that of the roller set 95, the floating tube 161 moves axially to the right (Fig. 11), namely as a result of the lateral pressure of the roller carriers 202, 202 ^M on the inclined spacers 205 , 211, which, as described, lie between the ends of the arms and the roller supports. The axial movement of the floating tube 161 gives the rollers 95 lateral movement and causes their axes of rotation to be shifted in a direction which causes the rollers 95 to tilt to a position corresponding to the higher gear, while the rollers 94 ^, 94 simultaneously have moved in the sense of reduced gear until an equal load on all roles of the two groups is achieved.

Should for some reason be 'one of the Roles experience a greater load than the other roles, so this is the same in the described way.

The roller 94 ^ ■ experiences a greater load than it actually should, since its axis of rotation is somewhat lower (FIG. 11) when the friction disk 90 rotates in the direction of the arrow, or somewhat to the left in FIG. 12. The centers of the regulating roller 94 ^M and the two other rollers 94 are denoted by n, n? and n ⁴ denotes and, after the shift, assume new positions n ', n ^s and n ^s , respectively; the roles

94 have shifted half as far as the role 94 ^. The movement of the roller 94 ^{M took place} in a direction that caused a reduction in the gear, while the movement of the two rollers 94 (n ² and w- ⁴ ) took place in the sense of increasing the gear. The overall effect is an even distribution of the load on all three rollers 94 ^ and 94.

If there is an inequality in the rotational force between the roller sets 94 ^, 94 on the one hand and the rollers 95 of the front group on the other hand, an equalization takes place between the two sets in the manner described. Assuming that the friction disk 90 rotates in the direction of the arrow (FIG. 11) and the rollers 95 transmit, for example, a greater rotational force than the rollers 94 ^M , 94, then the back pressure of the rollers

95 axially follows the arms 162 and the tube 161 moved to the left due to the axial component of the inclined surfaces of the spacers 205. This movement urges rollers 94 downwards, roller 94 ^ upwards, viewed in FIG. 11. Therefore, the setting of the two sets of roles balances out, see above that finally all six roles assume a position with the same translation.

If the main role 94 ^, as described, is inclined by the pressure exerted by the pivot shaft 240, it starts

Tilting the role in a new position from deviating Ganges, and so long until the roller axis returns to the radial plane which passes through the main axis and the center of the roll goes.

Only then are those attacking the role Forces balanced.

The illustrated resilient damping devices, which are permanently on the pipe

ίο -i6i and the arms i6o, 162 act, have the effort to keep this unit in the central position. A force suddenly attacking which strives to push the floating unit out of its central position, counteract the damping devices, so that a quiet position is guaranteed.

The main role 94 ^ is controlled via a flexible part so that the changeover does not fail too suddenly if the Manual shift to lower gear; that shown in Figs Damping device prevents too rapid movement. The manual through the Arm 292 and the pivot piece 263 exerted control is independent of the automatic Regulator.

Claims (21)

Claims ·. . i. Friction gear change transmission, in particular for motor vehicles, with friction rollers adjustably arranged in circular segment-shaped annular grooves of two friction disks lying on the same axis, which are arranged in one or more sets which are dependent on one another with regard to their angular position, characterized in that a control device (240, 243, 244, 250 ) is connected to the purpose of changing the transmission ratio only with a single friction roller (94 ^M ), which is set independently of the other rollers (94, 95), and that a compensating device, such as the roller carrier (160), on the various of. the individual roles transmitted torques responds and automatically brings the roles into such positions in which they transmit the same torques. 2. friction gear change transmission according to claim i, characterized in that the Roller carrier (160), which is usually coaxial with the axis of the friction disks (90, 92) is arranged, is adjustable transversely to this axis by forces resulting from the unbalance of the torques transmitted by the various rollers (94, 94 ^M). 3. friction gear change transmission according to claim 2, characterized in that the Roller carrier (160) in its usual equiaxed position held by spring-loaded bolts' (192) which is located in bores (184, 191) move. 4. friction gear change transmission according to one of the preceding claims, characterized characterized in that rotational movement of the roller carrier is prevented by transversely directed elastic arms (164) which are supported in the housing (H) of the transmission by laterally displaceable bearings (167). 5. Friction gear change transmission according to one of the preceding claims, characterized in that the roller carrier consists of an inner hub or sleeve and uniformly distributed arms (160) which extend radially outward from the sleeve and on which tiltable bearing journals (202, 202 ^M ) are attached, which rotatably support the rollers (94, 94 ^M ). = _. - 6. friction gear change transmission according to one of claims 1 to 4 with two at a distance Friction disks fastened to each other on a shaft and an equiaxed middle friction disk, which independently is rotatable by them, characterized in that the roller carrier to the Ends of a friction disc shaft (35) surrounding with play and opposite it longitudinally displaceable tube (161) and the tiltable bearing pin at its ends (202, 202 ^) for example by means of inclined blocks (205) carry so that one at one end of the tube (161) transmitted exceptional torque of a roller set (94 or 95) causes a longitudinal movement of the pipe, which causes a displacement of the roller axes from their usual position and thereby causes the rollers to take positions in which they are the same Transferring torques. 7. friction gear change transmission according to claim 6, characterized in that annular sleeves (181). the friction disk shaft (35) surrounded, in which no annular, under the action of feathers (180) standing sleeves (182) are housed, which are stored with the game Tube (161) in the axial direction in its hold middle position. i »5 8. friction gear change transmission according to any one of the preceding claims, characterized in that the control roller connected to the control device (94 ^M ) is arranged so that it can be inclined by the control device about a line which their points of contact with the friction disks and that they also for the purpose of speed change tilted around the intersection of the central plane of the roller with a plane perpendicular to the friction disk shaft (35) can be, while the remaining rollers (94, 95) can be tilted, but not are pivotably mounted. 9. friction gear change transmission according to one of the preceding claims, characterized in that the control device ^{consists of a control lever (218) which acts on the bearing (202 ^) of the regulating roller (94 M} ) and which is provided with a pressure-transmitting projection (237) which extends radially outward from the circumference of the roller, and in that a control shaft (240) is provided for adjusting the control lever and has a fork (244), the arms of which embrace the projection (237) of the control lever (218) on both sides. 10. friction gear change transmission according to claim 9, characterized in that the Projection (237) is located on a tab (236) that protrudes between the fork arms (244) and limits the dimension, around which the shaft (240) is rotated relative to the control lever (218) and thus the regulating roller (94 *) by the control device is inclined. 11. friction gear change transmission according to claim 9 or 10, characterized in that the axis of the control shaft (240) is substantially parallel, but slightly offset to the axis about which the control roller (94 ^M ) is tiltable. 12. Friction wheels with change transmission according to one of the preceding claims 4 <> a reversing gear for the friction disc or discs, characterized in that the control device for the regulating roller (94 ^) is self-regulating, for example in that the control lever is pivotable through a limited angle in the plane of rotation of the roller, whereby the the pressure receiving projection (237) is brought to one side or the other of the axis of the control shaft (240), so that in this way the direction of inclination of the roller is reversed when the direction of rotation of the friction disks changes. 13. Friction gear change transmission according to claim 12, characterized in that a friction member (228) carried by the control lever (218) presses against the control roller (94 ^M ) and pivots the control lever in the respective direction of rotation of the roller within the limits determined by it. 14. Friction gear change transmission according to one of the preceding claims, characterized in that a controller (280, 281) influences the rotational speed of one of the friction disks (90, 91, 92) and that an externally adjustable arm (292) by an elastic member (250) is connected to the control device (240, 243) of the regulating roller (94 ^M ). 15. Reibriäderwechselgietriebe according to claim 14, characterized in that a damping device (295) a excessive swiveling of the regulating roller (94M) is prevented. 16. Friction gear change transmission according to one of the preceding claims, in where two sets of friction disks are held together by a tube that surrounds the shaft on which the friction disks are placed are attached, characterized in that the tube (161) is so designed and arranged is that a cavity is created between it and the drive shaft (35) into which oil is introduced under pressure can, so that to lubricate the friction tracks (90, 91, 92) and the roller bearings (202) serving oil also to dampen the vibrations of the pipe (161) opposite the shaft (35) is used. 17. Friction wheel change transmission according to the Claims 7 and 16, wherein the tube is movable in the longitudinal direction of the shaft is, characterized in that the spring loaded sleeves (182) serve as closures for the ends of the tube to prevent the oil from leaking. 18. friction gear change transmission according to claim 16 or 17, wherein the friction rollers are arranged on radial arms which extend from the tube, characterized in that the arms (160, 162) have longitudinal bores (337) which with the oil space between the Tube (161) and - the driven shaft (35) on the one hand and with the bearings (202, 202 ^M ) of the rollers (94, 94 ^, 95) on the other hand. 19. friction gear change transmission according to one of claims 16 to 18, characterized marked that the tube (161) with no Nozzles (340) or openings (342) are provided, which with the oil space between the pipe (161) and the shaft (35) in Connect and are arranged so that they jets of oil on the work surfaces the friction disks (90, 91, 92). 20. Reibräderwechselgetriefoe after the Claims 3 and 19, in which the tube is movable transversely with respect to the shaft is, characterized in that the nozzles (340) sit on the sleeves (190), the spring-loaded bolt (192) for holding of the tube in its middle position, and over the sleeves with the oil space between the pipe (161) and the shaft (35) in connection stand. 21. friction gear change transmission according to one of claims 16 to 20, characterized characterized in that the oil space between the pipe (r6i) and the driven Shaft (35) with a device for supplying pressurized oil through a radially projecting one Tube (333) is connected, which is mounted so that it perform both an axial and a transverse movement can. For this purpose 2 sheets of drawings - BERLIN. GKDn [KtKT JN DER HKICHSDRtJCKEHEI