DE2326947B1 - Infinitely adjustable conical pulley gear - Google Patents

Description

The invention relates to a continuously adjustable conical pulley gear according to the generic term of the main or subsidiary claim.

In known transmissions of this type, the transmission medium can be used as a smooth belt or as Link chain can be designed with friction bodies, but it can also be a smooth chain that connects both pairs of friction disks Ring can be used.

All conical disks can also be used in a known manner be axially displaceable and supported against the aforementioned actuators, which in the mechanical case Are control levers that are usually divided into equal pairs, which are on both sides of the on and Output shaft are arranged. In known hydraulically supported conical pulleys, these are with a cylinder-piston unit in connection or form this with, which is from a pressure medium source related pressure medium is allocated via a control slide, which is used for setting and maintaining the gear ratio on the one hand on an axially displaceable friction disc and on the other hand, for example is hinged to a handle for translation adjustment.

The helical surfaces of the known pressing device can be convex or concave to one another Have running curve branches, depending on the conditions of use intended for the transmission are. The conditions are usually such that with the smallest running radius of the transmission medium on the shaft carrying the pressure device that part of the screw surfaces is effective, which is opposite the radial direction of the shaft has the flattest slope in order to match the correspondingly small arc of contact of the transmission means to generate the highest contact pressure. This means with concave Helical surfaces the effectiveness of the curve base and thus at the same time the smallest axial distance between the axially displaceable friction disc, which also forms the pressure device, and the support ring, while in the case of convex helical surfaces the ratios are exactly the opposite. In general, it is sufficient to use the Form helical surfaces only on the support ring or on the friction disc which also forms the pressure device and on the other part in each case supporting means or other transmission means cooperating with the helical surfaces to be provided. In the following, to simplify the representation, only mutual Helical surfaces with interposed

Rolling elements referred to, but without the invention being limited thereto. Here must be complementary then, in the case of screw surfaces with concave curve branches, ensure that the Always place the rolling elements on opposite parts of the helical surface of the same inclination, i.e. the relative Rotation of opposing screw surfaces of the pressing device just only participate halfway.

If such a known pressing device is provided, it is usually on the drive shaft arranged, with the output-side friction disks, for example, by tongue and groove the output shaft are non-rotatably connected. However, it is also possible and in certain cases desirable one of the mentioned pressing devices on both the drive and the driven side to arrange. The torque transmission then takes place on both shafts via this pressing device instead of.

With such a pressing device, however, considerable Piobleme connect, which so far only by large additional construction costs could be managed, with a large number of sometimes complicated and therefore difficult to manufacture and expensive parts are required, which not only affects the prime cost of the transmission, but also affects its space requirements.

In the case of the known transmission explained above, for example, one which has the helical surfaces Support ring provided as a shaft-fixed collar. This means that the axial distance is opposite to each other Helical surfaces of the federal government on the one hand and the friction disc which also forms the pressure device on the other hand changes over the amount over which this axially displaceable friction disc within the translation range of the transmission is adjustable or must be adjustable. This results in depending on the translation position of the gearbox to carry various parts of the screw surfaces over the rolling elements, which, on the other hand, is the prerequisite for generating transmission-dependent contact pressure, because now one can see the part of the helical surface assigned to each translation position with regard to its slope train so that the optimal contact pressure for this translation position is created.

But now there is a change in the direction of torque, i. H. thus a swap of the drive and driven side of the transmission instead, the pressing devices turn over until the rolling elements are in contact with the get in the circumferential direction opposite branch of the helical surfaces. This allows in particular in gears for the transmission of large powers and in the gear ratios where Shaft collar and adjacent friction disc are in the area of their greatest distance, such impact forces occur, that with frequent changes in the direction of torque, the screw surfaces and the Rolling elements will soon be destroyed or deformed, so that the pressing device no longer does its job ■ can meet the predetermined way or becomes unusable.

Attempts have been made to remedy this inconvenience by using known solutions (e.g. DT-AS 1 184 583) the screw surfaces of either the support ring or the shaft collar or the opposite friction disc has tracked in the axial direction so that the axial play between Helical surfaces and rolling elements were reduced or compensated. For this purpose, however, as already indicated, Complicated mechanical, hydraulic or mechanical-hydraulic tracking devices required, which make the gearbox extremely expensive and increase it in terms of weight and construction volume.

The object of the invention is to make the arrangement in transmissions of the type described above so that that the cover game with the help of extremely simple means across the entire translation range of the transmission is always so small that a serious impairment of the pressing device cannot occur even with frequent changes of the torque direction. The arrangement should in particular also be made in such a way that the size of the gearbox is only slightly influenced and few, additionally required components are easy to manufacture or are available on the market as mass-produced items are.

According to the invention, this object is achieved by the characterizing features of claim 1 or the independent claim 2 listed features solved.

The term "exclusively" is to be understood in such a way that it does not mean the arrangement of a pressing device bridging support spring or the use of a similar support device is excluded is, which is provided in particular to the pressure device co-forming, axially displaceable When the gear unit is at a standstill, support the friction disc so that it is not under the pretension of the transmission medium shifts so that the bias of the transmission means or the associated Maintain the axial position of the axially displaceable friction disc even when the gearbox is at a standstill remain.

Although it is already known for conical pulley gears without pressure devices, the travel sum over change the transmission range through the geometry of the control lever (DT-PS 103 744 and 200 858).

It is also known to change the flank inclination of conical pulleys by making them spherical (DT-Gbm 1 719 199). However, these measures always serve to compensate for the length of the traction mechanism.

Advantageous further developments of the invention are listed in the subclaims.

The arrangement according to claims 5 or 6 results depending on the design of the transmission according to the invention in particular whether the different effective axial travel between the input and output side of the transmission is to be generated via the support ring or one of the axially displaceable friction disks, which do not co-train the pressing device.

To the effect of the invention thus illustrated on the basis of a simple embodiment in detail to explain, without thereby limiting the scope of the invention, one can, for example, a conical pulley gear consider in which the actuators are arranged on both sides of the conical pulley pairs Control levers are and assume that the transmission has only one pressing device on the drive shaft. The following effects then result:

The translation-related axial position of three conical pulleys is precisely defined or forced, whereby a conical disk is supported on the output shaft against the control lever, while the other two Conical disks can be fixed to the shaft in the axial direction or also be supported against control levers. In contrast results in the axial position of the fourth, the

Pressure device co-forming conical disk with equilibrium of the acting on it in the axial direction Forces, on the one hand as a spreading force from the transmission medium and on the other hand as an axial force component proceed from the pressing device.

If the gear ratio is changed, the total on the input and output shaft is the axial If the travel ranges are different, this ultimately has an effect on the mutual axial spacing of the helical surfaces the pressing device off, so that the rolling elements at different depending on the gear ratio Make contact with the screw surfaces and according to the design of the screw surfaces Transmission-dependent pressure forces arise. In this case, however, the mentioned difference between the axial travel sums can be on the input and output shaft can easily be selected so that over the entire translation setting range of the transmission, the mutual axial spacing of the helical surfaces changes only relatively little, so that you can get by with small screw surfaces, which have an equally reduced maximum clearance result in the most unfavorable translation position. This scaled-down envelope game can be found in the named simple way are structurally predetermined so that there is a risk of damage to the Pressure device even with heavily loaded gearboxes and / or frequent changes in torque direction cannot occur.

The mentioned difference between the axial travel sums on the input and output side of the transmission can be differentiated Way to achieve. Once in that, for example, when training the actuators as a control lever the effective lever arm of a control lever is changed. According to a fundamentally different possibility in that at least one of the four conical disks has a different flank inclination than the others Has friction disks. After another fundamentally different possibility by, for example, through Adjustment of control levers by means of an adjusting spindle with opposing threads, these threads are different Have slope. These and other options are different in the following Types of infinitely adjustable bevel pulley gears explained in more detail.

In the case of the transmission according to claim 7, the control levers can usually be centered between the input and output shafts be stored, the adjusting spindle from the adjacent gear shaft with half the center distance is arranged between the shafts corresponding center distance.

The measures according to claim 7 result in the enlarged or reduced lever arm for the part supported on the other hand has an equally enlarged or reduced axial travel path, which is structurally so can be set up so that the axial distance is opposite to one another in the manner described Helical surfaces of the pressing device in the desired or according to the laws of the transmission changes as required.

If, for example, the pressing device is arranged on the drive shaft of the transmission, this pressing device also has concave curved surfaces, and should ultimately have the greatest contact pressure with the smallest Run radius of the transmission means are generated on the drive shaft, so this can either be done thereby achieve that the support ring of the pressing device against the control lever with a reduced lever arm is supported or that the axially displaceable conical disk, which co-forms the pressing device Conical disk diametrically opposite one another, against the control lever assigned to it with an enlarged Lever arm is supported. Exactly the opposite is true in this case when the helical surfaces have convex curve branches. Again, the situation is reversed, if for certain cases of need the transmission means are detected by the drive-side conical pulleys with the greatest contact pressure should, if it has the largest running radius there. The rotary joint according to claim 8 is not intended to do so serve to support the conical pulley forming the pressure device when the gear unit is running in the axial direction, since this is done by the pressing device itself. The said rotary joint has but the task of the transmission-related axial distance within the pressing device when the gearbox is at a standstill to be maintained, since this is done by the pressing device itself when the gearbox is at a standstill cannot happen. Without the additional rotary connection with the adjacent control lever for the The conical pulley also forming the pressure device would affect this with the gearbox at a standstill Tensioning device have the same effect as if the transmission means too little bias would have. The tensioning device would readjust the pivot bearings of the control levers and at the same time the opposing screw surfaces of the pressing device to their smallest distance bring, whereby the pressing device would be set incorrectly when the gearbox is running again.

It is precisely to prevent this from happening that the rotary connection for the conical disk forming the pressing device is necessary provided, which holds the conical pulley in the current axial position when the gearbox is at a standstill.

Is the gearbox described intended for applications in which one can also rely on the translation position dependent pressure forces, so very precisely those assigned to the respective translation position Contact pressure only needed over part of the translation range, namely where the highest loads occur, the training according to claim 9 can be advantageous. That way it gets over a part of the translation range of the enlarged or reduced lever arm effective, and the pressing device is adjusted in this translation range when the gear ratio is changed, while in the remaining part of the translation range, the lever arm of the control lever part that has not been enlarged or reduced is effective and the setting of the pressure device is not changed. This allows reduce the maximum play in the pressure device even further.

In the case of the transmission according to claim 10, the arrangement can again be made in this way for the normal case be that the control levers are pivoted centrally between the shafts and that the adjusting spindle with a center distance corresponding to half the center distance between the whites next to the adjacent one Shaft is located.

In the above-mentioned case, the axial Change in distance within the parts forming the pressing device over the translation area thereby instead of the separate control lever acting on the support ring on the adjusting spindle opposite one another the other control levers changed travel per revolution of the adjusting spindle! Has. The after the previous

409528/283

existing for the adjustment of the support ring taken Measure can of course just as well be taken for one of the axially displaceable conical pulleys, which do not form the pressing device. As for the size of the deviating pitch of the thread for concerns the separate control lever on the adjusting spindle, this can be above or below the other The thread pitch of the adjusting spindle depends on whether the screw surfaces are concave or convex Curve branches are used and at which transmission position of the transmission the maximum contact pressure is desired.

In the embodiment according to claim 12 of the solution, preference is given, in which the pressing device is arranged between the control lever and this loading ^χ 5 adjacent friction disc. With this possible solution, too, the effective lever arm of the control lever can easily be designed in such a way that the difference between the axial travel sum on the input and output sides of the transmission, which is aimed at by the invention, is obtained, whereby it is also easy to take into account whether the pressing device has screw surfaces with concave or convex surfaces Has curve branches and at which translation position of the transmission by the pressing device the maximum pressing force is to be generated.

The measures according to claim 14 also allow the different Axial travel sums on the input and output side of the gearbox over the transmission range range, depending on what training the screw surfaces of the pressing device have and when the maximum contact pressure should occur.

In addition to or instead of the different thread pitches on the adjusting spindle, the Offset of the swivel bearings, starting from the center between the two gear shafts, may be unequal however, it is not to be preferred, since this changes the running plane of the transmission medium, which one usually tries to avoid whenever possible.

In the embodiment according to claim 10, it is advantageous when the pressing device between one of the cylinder-piston units and an associated one Conical disk is arranged.

Exemplary embodiments of the invention emerge from the following description with reference to the drawing. In the drawing shows

F i g. 1 a conical pulley gear with the support of the four axially displaceable conical pulleys against Control lever,

F i g. 2 the transmission according to FIG. 1 with a tensioning device for the control levers,

F i g. 3 a transmission similar to that according to FIG. 1 and 2 with only partially translation-dependent generation the contact pressure,

F i g. 4 a transmission similar to that according to FIG. 1 and 2 with different thread pitches of the adjusting spindle,

F i g, 5 a gear with two equidistant adjustable, diametrically opposed conical disks,

F i g. 6 a transmission similar to that according to FIG. 1 and 2 with pivoting off-center between the shafts Control levers,

F i g. 7 a transmission with two radially opposite fixed disks and two radially opposite one another opposing, axially displaceable conical disks and

F i g. 8 a transmission with hydraulic conical disk support.

In the following description of the embodiments according to the invention are for simplification and abbreviation of the representation are given recurring parts with the same reference numbers and, if possible, only explained once. The conical disks are referred to below as friction disks.

In a transmission housing 1, the drive shaft 2 and the output shaft 3 are continuously adjustable Conical pulley gear arranged rotatably for example via roller bearings, not shown. On the waves 2 and 3 sit friction disks 4 to 7, between which a traction means 8 rotates.

The friction disks 6 and 7 on the output side are mutually axially displaceable, but by means of a feather key 9 relative to the shaft 3 non-rotatable. In contrast, the friction disks 4 and 5 are basically characterized relative to the shaft 2 rotatable and axially displaceable, but mutually non-rotatable that the friction disc 4 includes the shaft 2 with a sleeve 10 on which the friction disk 5 is displaceable, but by means of a key 11 is held non-rotatable.

The axial position of the friction disks 5 to 7 is determined by control levers 12 and 13. These are around the middle Pins 14 and 15 arranged between shafts 2 and 3 are pivotable and are formed by brackets 16 and 17 are, which in turn sit on a threaded spindle 18 with opposing threads, which are also rotatable is stored in the housing 1. The adjustability of the brackets 16 and 17 by means of the threaded spindle 18 is used in addition, tolerances resulting from wear and tear and inaccuracies over time due to readjustment the pivot bearing for the control levers 12 and 13 to compensate.

The pivoting of the control levers 12 and 13 to change the gear ratio is carried out by a Adjusting spindle 19, which is rotatably mounted parallel to the shaft 2 in the gear housing 1 and, for example, by means of a handwheel 20 can be rotated, the adjusting spindle 19 having opposing threads 21 and 22, by means of which brackets 23 and 24 are adjustable, which control levers 12 and 13 via pins 25 and 26 keep.

The friction disks 5 to 7 are against the control levers 12 and 13 via pivot bearings 27 to 29 and sleeves 30 to 32 supported, to which the control levers are pivotably articulated via pins 33 to 35.

The rotary transmission between the friction disk 4 and thus also the friction disk 5 on the one hand and the shaft 2, on the other hand, takes place via a device for generating torque- and transmission-dependent pressure forces between the friction disks and the traction means 8. To form this pressing device is the Friction disk 4 expanded by a hub 36, and there is a support ring 37 on the axially opposite one another Shaft 2 is axially displaceable, but is non-rotatable by a feather key 38. The axial support of the Support ring 37 takes place via a pivot bearing 39 and a sleeve 40, which in turn via pivot pin 41 on Control lever 13 is hinged. The opposite end faces of the hub 36 and the support ring 37 have mutually assigned screw surfaces 42 and 43, between which for torque transmission Rolling bodies 44 are used.

While the friction disks 5 to 7 against their control levers 12,13 are firmly supported in the axial direction, takes place

the support of the friction disk 4 takes place indirectly via the pressing device against the control lever 13 by by introducing a torque into the shaft 2 between screw surfaces 42 and 43 and the Rolling bodies 44 forces arise, one in the circumferential direction and one in the axial direction of the shaft 2 Have component, the force component going in the axial direction, the friction disc 4 in the axial direction holds, while the force component going in the circumferential direction for driving the friction disk 4 " and thus also the friction disk 5 ensures. As a result, the friction disk 4 is positioned in the axial direction at the respective Translation position where a balance between that generated by the pressing device axial force component on the one hand and the spreading force exerted by the traction means 8 on the other hand prevails. According to this axial setting of the friction disk 4, the axial distance between the Helical surfaces 42 and 43 and thus, depending on the gear ratio, determine the point at which the rolling elements are located 44 are in contact with the screw surfaces 42 and 43. Due to the different inclination of the helical surfaces 42 and 43 can thus be used for each transmission position of the transmission Apply axial forces to the friction disk 4 through the pressure device.

Were now the lever arms with which the control levers 12 and 13, based on their pivot pins 14 and 15 on the friction disks 5 to 7 or the support ring 37, would be the same, so the axial distance would be the same Do not change between the helical surfaces 42 and 43 over the entire transmission range of the transmission. However, as shown in FIG. 1 can be seen from the position of the pin 34 shown, the control lever engages 12 on the friction disc 7 with a lever arm that is longer than the same lever arms with which the Attack control levers 12 and 13 on friction disks 4 to 6.

This always results in a change in the gear ratio on the output shaft 3, effective axial travel than on the drive shaft 2, which has the consequence that the friction disk 4 via the traction means 8 compared to the support ring 37 is pushed into changed axial distances when the gear ratio changes. The arrangement is made so that the axial distance between the friction disc 4 and Support ring 37 is smallest when the traction means 8 between the friction disks 4 and 5 has the smallest running circle assumes, while the axial distance between the friction disc 4 and support ring 37 is greatest when the Traction means 8 between the friction disks 4 and 5 is located on the largest running circle.

As can be seen, the difference in length with which the control lever 12 on the friction disk can now be determined 7 attacks, determine in a simple manner how large the axial change in distance between the friction disc 4 and Support ring 37 is over the transmission range of the transmission. The aim is to be as low as possible axial change in distance so that the screw surfaces 42 and 43 are correspondingly small or in the circumferential direction can be short, which leads to a small amount of play between screw surfaces 42 and 43 as well as the rolling elements 44 leads when the gear unit suddenly interchanges input and output takes place.

The in Fig. The transmission shown in FIG. 2 corresponds essentially to the transmission according to FIG. 1, why so far reference is made to the description there.

The difference is that the brackets 16 and 17 on the threaded spindle 18 with automatically working tensioning devices 45 and 46 are provided, which are known per se and, for example, in the DT-PS 1214 503 are described in detail. These tensioning devices ensure that through wear and tear For example, the play that occurs in the axial direction of the traction means 8 is automatically compensated when the transmission is at a standstill.

The axial distance would now be applied to these tensioning devices 45 and 46 when the gearbox was at a standstill between the friction disk 4 and the support ring 37 in the same way as if, for example, between the Friction disks 4 and 5 and the traction means 8 would be game. As a result, the tensioning devices became Readjust the control levers until the axial distance between the friction disk 4 and the support ring 37 assumes a minimum, d. H. the rolling elements 44 would be printed in the base of the helical surfaces 42 and 43. As a result, however, when the gearbox is running again, the rolling elements 44 would not come into contact there the screw surfaces 42 and 43 arrive, which corresponds to the existing translation setting.

In order to counteract this, the control lever 13 is extended in the direction of the friction disk 4 Extended lever arm part 47, on which a roller 48 is rotatably mounted via a pin 49, with In relation to the pin 15, the lever arms behave towards the pin 41 on the one hand and to the pin 49 on the other hand in such a way that that the roller 48 in each translation position of the transmission according to the associated axial distance between friction disk 4 and support ring 37 directly, d. H. practically free of play, next to the friction disc 4 stands.

This measure ensures that the friction disk 4 in the axial direction when the transmission is at a standstill it is noted that the axial distance between the friction disc 4 and support ring 37 of the respective Translation position corresponds, so that the tensioning devices 45 and 46 also do not can take effect.

The F i g. 3, 3a and 3b show a modification of the transmission according to FIG. 1, in which only about a part the translation area translation-dependent contact pressure are generated, while the remaining Part of the transmission range, the contact forces are only proportional to the torque. To the representation To keep it clear, only the essential reference numbers from FIG. 1 repeated.

As shown in FIG. 3, the friction disk 7 is against the control lever 12 depending on its pivot position supported either via a pressure roller 50 or via a pressure roller 51. The pressure roller 51 is seated here so that there is the already explained, larger lever arm relative to the pin 14, while the pressure roller 50 is arranged so that the lever arm opposite the pin 14 is equal to the lever arms, with which the control levers 12 and 13 attack the friction disks 4 to 6.

Like F i g. 3a shows, this leads to the fact that the pressure roller 50 is effective from about a transmission position 1: 1 up to fast output speeds, so that in the Pressure device no axial change in distance occurs, while according to FIG. 3b from the middle mentioned Gear ratio adjustment up to low output speeds the pressure roller 51 the friction disk 7 supported and by the pressing device not only torque, but also gear-dependent

Pressure forces are exerted on the friction disk 4.

This measure, which of course is not limited to the translation areas mentioned is, you have it in hand, the pressing device only in the one for the respective application of the transmission to make the critical translation area effective, which in particular allows for a further reduction in size of the screw surfaces of the pressing device and the possible turning play in it leaves.

According to FIG. 4 is a further modification of the on the basis of FIG. 1 described transmission given, in general, referring again to the description of FIG. 1 is referred to in order to avoid repetition, and only the reference numerals are repeated for the essential parts.

The difference is that the support ring 37 is supported by a separate control lever 52. This is also mounted on the pivot pin 15 of the control lever 13 and by the adjusting spindle 19 via ao the thread 21 held. On the other hand, however, is the control lever 13, against which only the friction disk 6 now is supported, displaceable on the adjusting spindle 19 by means of a thread 53, the pitch of which is different from that of the Thread 21 and 22 deviates. Finally, the as takes effect Control lever 12 in this case on the friction disc 7 with the same lever arm on the pin 54, the he has opposite the friction disk 5.

This is because of the different pitch of the threads 21 and 22 on the one hand and of the thread 53 on the other hand, care is taken that the on the basis of FIG. 1 explained in detail Axialwegdifferenz between The input and output of the gearbox is created over the transmission range.

F i g. 5 shows a transmission of the type generally described above, but in which the change in the Gear ratio setting by an adjusting spindle 55 mounted between shafts 2 and 3 on the gear housing 1 he follows. On this two arms 57 and 58 are axially and equidistantly adjustable by means of a thread 56, the are rigid and connected in the radial direction to a sleeve 59 which is in engagement with the thread 56. Against the arms 57 and 58, the friction disks 5 and 6 are supported in the manner described above, wherein whose effective length or whose lever arm is the same. On the other hand, the friction disk 7 is on the shaft 3 due to the fact that it is axially immovable in that it is in contact with a shaft collar 95. The friction disc 4 is again part of a pressing device of the type described.

If you wanted to generate only torque-proportional contact pressure with this gearbox, it would it is sufficient to keep the support ring 37 axially immovable on the shaft 2. For the generation also proportional to the ratio However, according to the invention, this pressure is now against a control lever 60 a pivot bearing 61 is supported, on the one hand via a pin 62 on the sleeve 59 and on the other hand via a Bearing 63 is pivotably mounted on the transmission housing 1. The control lever 60 is on pin 41 with the Support ring 37 in connection.

In this design, the control lever 60 and its lever arms are between the bearing 63 and the pin 41 on the one hand and pin 62 and pin 41 on the other hand ensure that it extends beyond the translation range of the transmission results in the axial change in distance between the friction disc 4 and the support ring 37, which is dependent on the ratio Generation of the pressing forces on the friction disk 4 in the manner described above is necessary.

In the case of the transmission according to FIG. 6, for which, moreover, refer to the explanations for most of the details Begug can be taken to the transmission according to FIG. 1, the control levers 12 and 13 not pivoted centrally between shafts 2 and 3. Rather, their pivot bearings 64 are located and 65 offset off-center in the opposite direction on the gear housing 1. In this case, the axial change in distance to generate gear-dependent contact pressure between friction disc 4 and Support ring 37 can thereby be achieved in the required manner over the transmission range of the transmission, that when the pivot bearing 64 and 65 is offset from the center between the shafts 2 and 3, the thread 66 and 67 for the control levers 12 and 13 on the adjusting spindle 19 have different inclines.

F i g. 7 shows another gear structure. In this case there are two friction disks lying radially opposite one another 68 and 69 supported axially immovable on the shafts 2 and 3 by being in contact with each a shaft collar 70 and 71 are located. On the other hand, the rest are radially opposite one another Friction discs 4 and 6 axially displaceable on the shafts 2 and 3, the friction disc 4 being part of a again Pressing device of the type described is.

The axially displaceable friction disks 4 and 6 are supported by a control lever 72, which is between the shafts 2 and 3 is pivotably mounted eccentrically via a bracket 73 on the gear housing 1 and is adjustable by an adjusting spindle 74, which is based on the bracket 73 on the other side of the shaft 2 rotatable in the Gear housing 1 is located.

This is where the axial distance change necessary for the respective translation position takes place between The friction disk 4 and the support ring 37 are held by the eccentric articulation of the control lever 72 on the bearing block 73.

F i g. 8 shows a transmission in which the axially displaceable friction disks are supported hydraulically takes place by cylinder-piston units, with im Example shown the pistons 75 and 76 are shaft-proof, while the cylinders 77 and 78 are axially displaceable are. In addition, the diametrically opposed friction disks 5 and 6 are axially immovable arranged on their shafts 2 and 3. Finally, there is again a pressing device of the type described brought into connection with the friction disk 4, the support ring of which is part of the cylinder 77.

The cylinder-piston units are supplied by a pressure medium source 79 and 80, which are also shared Pressure medium source can be, related pressure medium allocated via control spools 81 and 82, with excess amounts of pressurized oil via lines 83 and 84 in the pressure medium tanks 85 and 86, the can also be a common pressure medium tank, can flow back. From the control spools 81 and 82, the pressure medium reaches the pistons 75 and 76 and the cylinders via lines 87 and 88 77 and 78 formed cylinder spaces.

The control slide 81 and 82 are in connection with adjusting levers 89 and 90, which on the one hand on the axially displaceable part of the associated cylinder-piston unit, for example via a groove 91 and 92 and on the other hand, are articulated to one another via a connection 93 in such a way that the gear ratio adjustable via a hand lever 94, but the resulting axial travel on shafts 2 and 3 is different is by, for example, the adjusting lever 89

has different, effective lever arms a and b .

Various combinations of the measures described are possible with one another, for example the on the basis of FIG. 3 described, only partial generation of translation-dependent, axial Contact pressure concerns.

In particular, however, it is possible to use the described different travel ranges of the control levers or cylinder-piston units to be replaced by the fact that the friction disks have a mutually different flank

have inclination. If one takes, for example, the transmission according to FIG. 1 and forms this in such a way that the control lever 12 also acts on the friction disk 7 with the lever arm based on the pin 14, which the Have control levers 12 and 13 opposite the friction disks 4 to 6, the required axial change in distance results between friction disk 4 and support ring 37 even if the disk inclination angle, for example the friction disk 4 is different from the other friction disks.

For this purpose 3 sheets of drawings 409528/283

Claims (18)

Patent claims: 1. Infinitely adjustable conical pulley gear with at least two each on the input and output shaft arranged conical disks and between these revolving transmission means, the Conical pulleys of each pair are rotatably connected to one another and to their shaft and at least a conical disk on each shaft axially displaceable * ° and in the axial direction against a transmission actuator is supported and wherein the rotary connection of at least one pair of friction disks with its shaft for generating torque and Transmission-dependent pressure forces between friction disks and transmission means as a pressure device is formed, which is distributed over the circumference several helical surfaces with variable Incline on the axially displaceable friction disc and / or on a non-rotatable with the shaft associated support ring as well as cooperating transmission means, in particular rolling elements , characterized in that the one containing the pressing device Conical disk (4) is supported in the axial direction exclusively via the pressing device and that when changing the gear ratio on the support ring (37) and thus / or on the control lever axially displaceable conical pulleys (4, 5, 6, 7) effective axial travel on the input and output side of the Transmission is different at least over part of the gear ratio range (changing Travel total). 2. Infinitely adjustable conical pulley gear with at least two each on the input and output shaft arranged conical disks and between these revolving transmission means, the Conical pulleys of each pair are rotatably connected to one another and to their shaft and at least a conical pulley axially displaceable on each shaft and axially against a transmission actuator is supported and wherein the rotary connection of at least one pair of friction disks with its shaft for generating torque and Transmission-dependent pressure forces between friction disks and transmission means as a pressure device is formed, which is distributed over the circumference several helical surfaces with variable Incline on the axially displaceable friction disc and / or on a non-rotatable with the shaft associated support ring as well as cooperating transmission means, in particular rolling elements , characterized in that the conical disk containing the pressing device (4) is supported in the axial direction exclusively via the pressing device and that with constant Travel sum of the axially displaceable conical disks (4, 5, 6, 7) on the input and output shafts (2, 3) at least one conical disk has a flank inclination that differs from the other conical disks. 3. Transmission according to claim 1 or 2, characterized in that opposing concave screw surfaces (42, 43) of the pressing device with the smallest running radius on its shaft (2) are closest to the transmission medium. 4. Transmission according to claim 1 or 2, characterized in that that opposing convex helical surfaces of the pressing device with the smallest running radius of the transmission medium on whose shaft (2) they are furthest. 5. Transmission according to claim 1, 3 or 4, characterized in that the support ring (37) on its Shaft (2) is axially displaceable and supported against the actuator (13,52,60,72,77) adjacent to it. 6. Transmission according to one of claims 1 to 4, characterized in that the support ring on its Shaft is stationary in the axial direction. 7. Transmission according to one of claims 1 and 3 to 6, wherein the actuators via pivot bearings on the conical disks Attacking control levers are the pivot bearings arranged between the input and output shafts for setting the gear ratio can be swiveled in opposite directions and to maintain the translation position in its swivel position, in particular by an adjusting spindle with opposing threads, are held on the the threaded spindle facing away from one of the gear shafts is arranged, characterized in that, that the one of the axially displaceable friction disks (7) or the support ring (37) engaging Control lever (12 or 13) has an enlarged or reduced lever arm. 8. Transmission according to claim 7, wherein the pivot bearing for the control lever on one of the shafts parallel threaded spindle with counter-rotating threads automatically to maintain the preload of the transmission means are adjustable, characterized in that at one of the axially displaceable conical disks (7) engaging control lever part with enlarged or reduced Lever arm of the control lever part supporting the support ring (37) at the same time via a rotary connection (48) acts directly on the conical disk (4) forming the pressing device and that the The lever arm of this rotary connection corresponds to the enlarged or reduced lever arm (Fig. 2). 9. Transmission according to claim 7 or 8, characterized in that with partial generation of translation-dependent Contact pressure of the control lever part forming the enlarged or reduced lever arm (12) two acting on the associated friction disc (7) regardless of its pivot position Has rotary connections (50, 51) with this, of which one (51) the enlarged or reduced Has lever arm (Fig. 3 to 3b). 10. Transmission according to one of claims 1 and 3 to 5, wherein the actuators via pivot bearings to the Control levers that attack conical disks are arranged between the input and output shafts Swivel bearing for setting the gear ratio swiveling in opposite directions and for maintaining it the translation position in its swivel position by an adjusting spindle with opposing threads are held, which are arranged on the side facing away from the threaded spindle of one of the gear shafts is, characterized in that the support ring (37) has a separate control lever (52) and an intermediate pivot bearing is supported that this control lever around the adjacent Pivot bearing (15) is rotatable and that the adjusting spindle (19) for the actuation of this control lever has a thread pitch that differs from that for actuating the other control levers (12, 13) (Fig. 4). 11. Transmission according to claim 10, wherein the Swivel bearing for the control lever on a threaded spindle parallel to the shafts with counter-rotating The threads can be adjusted automatically to maintain the pretension of the transmission medium are, characterized in that the conical disk (4) forming the pressing device has a Pivot bearing with the control lever (13) for the friction disc (6) of the other located radially opposite it Transmission shaft (3) is connected, this control lever on both friction disks with the same * ° Lever arm attacks based on its pivot bearing (15). 12. Transmission according to one of claims 1 and 3 to 5, wherein two diametrically opposite one another Conical disks over themselves radially to an adjusting spindle arranged centrally between the shafts extending arms and pivot bearings are supported, which can be adjusted equidistantly by the adjusting spindle are, characterized in that a third, axially displaceable conical disk (4) against one on the one hand on the gear housing (1), on the other hand on the adjusting spindle (56) pivotable control lever (60) supported is that the pivot bearing on the adjusting spindle with the arms (57, 58) is adjustable that the Pressure device between one of the axially displaceable friction disks (4) and the associated one Arm or control lever (60) is arranged and that the fourth friction disc (7) on its shaft (3) is supported axially immovable (Fig. 5). 13. Transmission according to claim 12, characterized in that the pressing device between The control lever (60) and the third conical disk (4) are seated and that the control lever engages the support ring (37). 14. Transmission according to one of claims 1 and 3 to 5, wherein the actuators via pivot bearings to the Control levers that attack conical disks are arranged between the input and output shafts Swivel bearing for setting the gear ratio swiveling in opposite directions and for maintaining it the translation position in its pivot position, in particular by an adjusting spindle with counter-rotating Threads are held on the side facing away from the threaded spindle of one of the gear shafts is arranged, characterized in that the pivot bearing (64, 65), based on the Center between the shafts (2, 3), which are arranged offset in opposite directions in the radial direction and that the thread pitches of the adjusting spindle (19) are unequal (FIG. 6). 15. Transmission according to one of claims 1 and 3 to 5, characterized in that two radially each other opposite conical disks (68, 69) are axially immovably supported that one of the the other two conical disks (4, 6) and the support ring (37) against a common control lever (72) are supported and that the control lever between the shafts (2, 3) is mounted eccentrically pivotable (73) is (Fig. 7). 16. A transmission according to any one of claims 1 and 3 to 6, wherein two mutually diametrically gegenüberlie- ^e constricting axially displaceable conical discs are each supported a hydraulic cylinder-piston assembly via °, to which the purchased from a pressure medium source pressure medium is assigned a control slide , which is articulated to setting and maintaining the transmission position of the gearbox on an adjusting lever which is articulated on the one hand to the axially displaceable part of the cylinder-piston unit and on the other hand to a lever for setting the transmission ratio for the transmission, characterized in that each cylinder-piston Unit (75, 77; 76, 78) is assigned a control slide (81, 82) and that their adjusting levers (89, 90) are articulated to one another (93) in such a way that the cylinder-piston units have different axial adjustment paths when the gear ratio is changed carry out. 17. Transmission according to claim 16, characterized in that that the pressing device between a cylinder-piston unit (75, 77) and the associated conical disk (4) is arranged. 18. Transmission according to claim 8 or 11, characterized characterized in that the rotary connection (47,48,49) is adjustable in the axial direction.