DE102006009704A1 - Ancillary transmission for auxiliary components of vehicles has single-stage planetary wheel set with coaxial rotationally secured belt rim connected to planetary wheel support and a switchable clutch - Google Patents

Abstract

The ancillary transmission has a single-stage planetary wheel set with sunwheel (6), planetary wheel support for several planetary wheels (10), and a hollow wheel (7). The sun wheel is connectable coaxially and rotationally secured to a shaft on the output or drive side and a belt rim (1) is connected coaxially and rotationally secured to the planetary wheel support. A clutch can be shifted in between the planetary wheel support and sunwheel to act as drive. A brake can be shifted in between the hollow wheel and a stationary frame part. Independent claim describes drive assembly for ancillary transmission where the sunwheel is connected rotationally secured coaxially to the drive shaft of the auxiliary component which is to be driven or to the output shaft of an output element.

Description

The The invention relates to a switchable attachment gear for ancillaries in vehicles according to claim 1.

ancillaries in vehicles such as three-phase generators, power steering pumps, air conditioning compressors and the like generally have a drive-side pulley on that over a belt with the crankshaft wheel of the vehicle engine in one fixed ratio geared connected is. In spite of this fixed gear ratio an accessory over the entire speed range of the vehicle engine away with appropriate efficiency to operate and at the same time a minimum performance of the accessory also to ensure at engine idling, It is known between the pulley and the drive shaft the ancillary unit to put a switchable planetary gear coaxial, when a speed limit falls below a translation offers fast.

The However, known such transmissions have, among other things their size, production costs, noise and mountability disadvantages.

task The invention is a switchable attachment planetary gear for belt-driven Specify ancillaries in vehicles, in a first switching state a direct drive and in a second switching state, a translation in the same direction offers fast. It should be quiet run, steamed switch, as small as possible build as well as cost-effective in series production and simply in series production.

The The object is achieved by the subject matter specified in claim 1. Accordingly, an attachment gear for ancillaries provided in vehicles, comprising firstly a single-stage planetary gear set, a sun gear, a planetary carrier carrying a plurality of planet wheels and contains a ring gear, and its sun gear with a driven or drive side shaft coaxial and rotationally connected or connected, secondly one Belt ring connected to the planet carrier coaxial and rotationally fixed third, a clutch that is shiftable and driveable between the planet carrier and the sun gear or between them rigidly with each connected parts, fourthly a fixed frame part, and fifth a brake, which is switchable and drove between the ring gear and the frame part or drove between them with each rigid connected parts is arranged.

Of the Drive or take-off of the attachment according to the invention takes place via the Belt wreath. He is suitable, at least, along its circumference a friction or positive Drive belt to be entwined and lead this. For this can the belt ring in the axial or circumferential direction in a known Be straight-toothed, so that in particular conventional endless tooth, Wedge or V-ribbed belts can be used.

Of the Single-stage planetary gear set is preferably made of straight or helical teeth spur gears compiled with uniform tooth width, with the sun gear and the peripheral planetary gears externally toothed are and the ring gear is internally toothed. The sun gear, the planet carrier and the ring gear are arranged coaxially with each other. The planet wheels are stationary with the sun gear and the ring gear constantly in meshing and can on planet carrier rotatably mounted. The ring gear is preferably radial slidably mounted on the planet carrier and / or on this one or both sides sliding axially secured.

Of the Belt ring and the planet carrier are coaxial with each other and permanently connected rotatably. They are also coaxial with and preferably coaxially rotatable on the output or drive side shaft storable or stored. Preferably, the belt ring of the planet rigidly worn, allowing for both a common pivot bearing, z. B. with a rolling bearing can be sufficient.

Of the appropriate Ab- or drive of the attachment gear via the Sun. It is with the, from the point of view of the auxiliary gear output- or drive-side shaft coaxial and permanently rotatably connected or connected, preferably by means of a profile shaft or press connection. The output or drive side shaft can also be part of the attachment gear be and preferably with its one shaft end in the auxiliary gear end up.

The Fixed frame part does not rotate in gearbox operation and supports the Difference between the input and the output torque of the attachment at a suitable resting part in the vehicle. Ideally, that can Actuator by means of the frame part at the same time at the installation, in particular be mounted directly on the accessory or be.

The clutch or the brake can repeatedly produce a temporary driving connection between the planet and the sun or between the ring gear and the stationary frame part during gear operation and under load by switching and then solve again. That way, when closing the clutch of the planet carrier and the sun gear synchronized to their synchronization and decelerated when closing the brake, the ring gear on the fixed frame part to its stop. The brake can therefore also be understood as a clutch that drifts off the fixed frame part. It goes without saying that the clutch or the brake can also be arranged like a drive between other, in each case rigidly connected to the aforementioned elements components. So it is synonymous to arrange the clutch instead of driving between the planet carrier and the sun gear, for example, also driving between the belt ring and the output or drive side shaft. It may in particular be structurally expedient to connect a first drive side of the clutch directly to the output or drive-side shaft and the other second drive side of the clutch to the planet carrier rotatably. The drive connection between the aforementioned of elements of the auxiliary transmission is preferably generated within the clutch or the brake, that with these elements rotatably or rotationally limited connected form-fitting or Reibschlussteile the clutch or the brake are axially displaced to each other, so that between them Force and / or positive connection can be generated. The switching on and off of the clutch or the brake is thus preferably carried out by a controlled axial displacement of one of the form-locking or Reibschlussteile.

The Clutch and the brake can be of different effects and design. Is preferred However, to make the clutch and the brake as identical as possible. The clutch or the brake can in particular friction force acting accomplished be. Thus, a friction clutch or a friction brake, the switchable is, have at least two mutually rotatable friction body, their friction surfaces one another, a loadable with an axial force friction combination form. A first friction body is here according to the planet carrier or the ring gear and a second friction body of the unit shaft or the fixed frame member rotatably or rotationally limited assigned, one of these friction bodies axially controlled against the other of these friction body is displaced. The friction body can at the friction surface be coated with a suitable friction lining or already made consist of a suitable material. A friction combination may be out an inner and an outer friction body, being for a compact design, preferably the inner friction of the Aggregate shaft or the fixed frame part and the outer friction body the planet or the ring gear rotatably associated with or limited rotation. It can also be space-saving, the respective inner friction body axially controlled to perform slidably. Because the friction body while Shifting against each other slip, the adhesion appears only gradually, so that opening and closing muted can be done.

Finally, can It's an advantage, a gearbox provide, at least the planetary gear, the clutch and contains the brake, wherein the output or drive side shaft and the belt ring are accessible to the drive or output.

The auxiliary gearing can assume at least two switching states by combined switching of the clutch and the brake:
In a first switching state, the clutch is closed and the brake is opened. Accordingly, the planet carrier and the sun gear are rotationally connected to each other. and the planet gears do not roll. The ring gear is unbraked relative to the fixed frame member and rotates concurrently with the planet carrier and the sun gear. This switching state represents the direct drive through of the attachment gear, ie the belt ring and the output or drive-side shaft are the same and it is therefore a translation in the same direction i = 1 given
In a second switching state, opposite to the first switching state, the clutch is opened and the brake is closed. Consequently, the ring gear is rotationally connected to the fixed frame part and therefore braked halting. The planet carrier and the sun gear rotate in opposite directions and the planet gears roll accordingly. In this case, the auxiliary gear translates the input speed in the same direction either quickly, for example i = 3, if the belt rim is driven and driven off via the sun on a driven shaft, or slow, for example, i = 1/3, if driven via a drive shaft shaft, the sun and is driven off over the belt wreath. The transmission ratio is dependent on the radii or tooth ratio of the planetary gear set and can be selected appropriately.

Furthermore can in a third switching state, both the clutch and the brake is open be. If enough high load torque on the abortive element of the attachment gears can a Type idle be achieved, in which ideally alone the ring gear absorbs the rotational power.

Further Is it possible, For example, to test or Assembly purposes, in a fourth switching state, both the clutch as well as the brake close. In this case, the sun gear and the output or drive side Wave, the planet carrier and the belt ring and the ring gear together to fixed Frame part blocked.

The Switching principle of the clutch or the brake can be closing or opening. At closing Switching principle is in the switched-on state a connection to torque transmission produced. At opening Switching principle, however, in the on state, the connection to torque transmission interrupted. The off state can, preferably automatically by means Preload, in particular by means of mechanical spring preload be achieved. Accordingly, are for the front-wheel drive four types of switching possible: In a first switching mode is the clutch of closing and the brake of opening switching principle. If both are switched on, the first switching state is direct Through drive and if both are off, the second switching state given. In a second mode of operation, the clutch is of opening and the brake of closing switching principle. If both are switched on, the second switching state and if Both are off, the first switching state is with direct Driven by. In a third shift, both the clutch and as well as the brake of closing switching principle. are both switched on is the fourth switching state and if both are turned off, the third switching state is given. Finally is in a fourth shift, both the clutch and the brake from opening Switching principle. If both are switched on, the third switching state is and if both are off, the fourth switching state is given. The first and second switching modes are preferred because when the clutch and brake off the auxiliary gear one of the preferred first or second switching states can automatically assume. Besides that is it's just possible waiving the third and fourth switching state, the clutch and the brake coupled on and off or between the to change first and second switching state.

The Clutch or the brake can be self-switching torque, Drehrichtungs- or speed actuated. For example, you can this be designed as a centrifugal clutch or brake. Preferably, the Clutch or brake, however, mechanical, electromagnetic, pneumatic or hydraulically de-energized, the latter three particularly are easy to automate. Preferably, for the clutch and the brake the same kind of exercise selected. In fluidic external circuit is for the clutch and the brake in usual Each way a working piston provided in a pressure chamber by applying a pneumatic or hydraulic actuating pressure guided slidably, in particular axially guided is displaceable. The operating pressure can be generated and controlled by a control hydraulics.

Especially in hydraulic external circuit of the clutch or the brake is it conceivable in this context, the piston at the pressure chambers not Completely seal and allow some leakage, causing the gearbox partially or completely with hydraulic fluid to fill can and this advantageously for cooling and / or lubrication purposes and / or used for the hydrodynamic bearing for the gear parts can be. It may be appropriate, the hydraulic fluid from the gearbox via a Suction returned and / or to regulate the amount contained. With not specially sealed pistons are also higher Relative speeds to the pressure chamber allowed.

Independent of the type of actuation it may be advantageous to move the opening and closing movement Clamping or braking part pretension, in particular by means of mechanical Spring force, so that in each case the bias voltage is to be pressed for switching and the switching off by means of the bias done automatically can. This option also exists for a clutch or brake, which can open automatically without bias, such as Multi-plate clutches. For mechanical bias are particularly suitable Cylinder or cone helical spring or slotted disc springs.

The Clutch and the brake can be timed to each other so that the change between first and second switching state as fluent as possible, d. H. with suitably overlapping opening and closing process without slumping the rotary power transmission takes place and if possible only appropriate slip friction occurs. In this context, it is conceivable by a controlled generating Slip friction in the clutch and / or in the brake, shift shocks when To turn on and off. Further, this is due to the distribution function of the planetary gear set conceivable, between the first, second and / or third switching state any other switching states or gear ratios to accomplish. For the appropriately combined circuit the clutch and the brake can also be beneficial to shift the clutch and the brake asymmetrically, z. B. the Clutch faster or slower to open or close than the brake closes or opens. It is also conceivable that the opening and the closing curve of Clutch or brake asymmetric, z. B. progressively opening and closing degressive or vice versa.

The clutch and the brake can be independently switchable or coupled switchable. The advantage of independent circuits lies in a separate adjustment and / or Nachregelbarkeit the switching pressure and in particular the switching time for the clutch and the brake. A coupling of the scarf tions can be mechanical, electromagnetic, pneumatic or hydraulic and rigid or linear or elastic or even pro- or degressive. The advantage of a positive connection of the clutch and the brake can be, inter alia, the savings of internal components, in particular of switching means, and of an external coupling logic. Thus, with a single switching means both the clutch and the brake can be switched properly. A coupling may in particular be formed mechanically by means of a rigid connection or an elastic spring connection. Particularly advantageous may be a fluidic coupling, since with only one pneumatic or hydraulic household, the clutch and brake can be switched fluidly mediating each with a working piston. A coupling is particularly advantageous in combination with the first or second switching mode.

The Clutch and the brake can with regard to the switching direction arranged mutually different be. If the clutch and the brake as preferred to shift axially are, can first of all, in one or the other opening axial direction, or second, in opposite axial directions, either from each other be directed away or arranged open to each other. at opposite opening Clutch and brake can be combined with the first or second Switching due to the common axial switching direction one Coupling particularly easy to be realized. In addition to each other dressed open Clutch and brake, the space between them in an advantageous Way for Switching paths and actuating means be shared. When stacked open Cone clutch and cone brake, their friction surfaces are at the same cone angle arranged accordingly mirror image.

The Clutch and the brake can also arranged differently with respect to the planetary gear set be. It is possible, the clutch and the brake on one side or the other to arrange the planetary gear set. This can be done in a simple way with only one switching means the clutch and the brake at the same time be switched. In addition, conceivable is the planetary gear and its To arrange pivot bearing between the clutch and the brake.

Triggering switching event is preferably the underflow or exceedance a speed limit. In the case of external switching, the speed can be used for this purpose be detected at a suitable location with electronic measuring means. To avoid a switching hysteresis, it is conceivable that the measured data on a to average or filter a suitable time interval. For external switching are also other triggering switching events conceivable, which can be classified into three groups. The first group requires an increased, the second a reduced and the third no speed at the Driven side. Examples of such switching events may be the Operating state of the motor starter, the operating state of direct and indirectly connected aggregates or other conditions in or out of the vehicle such. B. be a temperature.

The inventive attachment gear is associated with a number of general benefits: the on or off Downforce over the, with the planet carrier rotatably connected belt ring and the corresponding Ab- or Drive over the sun gear allows a particularly integrated construction with high packing density. In addition, in this way a simple series assembly at the output or drive-side shaft possible; even an afterthought Gear up by replacing an existing pulley is conceivable. Of the for one Conventional pulley already existing space can from the It is optimally used for auxiliary gears. In addition, the rolling gears in the first switching state, d. H. in the direct drive not off, whereby the planetary gear set is spared. Furthermore, in the first Switching state by locking the planet carrier with the sun gear or with the output or drive side shaft effectively an otherwise caused by the backlash of the planetary gears Gearless and the associated gear noise at Load change can be effectively prevented. The third switching state achievable backlash can be of great benefit in several ways be. Last but not least, the use makes it easy to produce Assemblies, such as the planetary gear set, the clutch and the brake, a cost-effective Series production possible. The intentional transmission according to the invention is therefore ideal for over pulleys driven or aborted ancillaries, such as those fitted as standard in passenger and commercial vehicles are installed.

In an advantageous embodiment according to claim 2 also exactly a transmission housing is provided, which is at least partially formed by the belt ring. As a result, the attachment gear can be built even more compact. The gear housing is in this case the only housing of the attachment gear and preferably rotationally symmetrical. It is a rigid, rotatable unit, which can be made in one or more parts and is preferably liquid-tight. By exactly one permanently remaining opening, which is not closed by components of the gear housing, first, the output or drive-side shaft can be guided to the outside, and projects, secondly, either the fixed frame part to the outside or an external fixed connection part to the inside. Through the opening In addition, leading to the actuator of the clutch and the brake lines can be passed, in particular supply, control and control lines. The opening may be closed in addition to the output or drive side shaft preferably by the fixed frame member and / or by a wall on the connecting part and in particular, for. B. be sealed by a sealing ring. Optionally existing temporary openings, in particular mounting holes are closed with components of the gear housing and preferably sealed.

The gearbox is at least partially formed by the belt ring. The belt wreath is therefore firmly integrated component of the rigid and rotatable Unit, with the gearbox always runs with the belt ring. The gearbox and Thus, in particular, the belt ring can preferably be rigid with the planet be connected, wherein the thus formed Rotationsverbund ideally with a single pivot bearing, in particular a rolling bearing is rotatably mounted on the output or drive side shaft. Due to its rotationally symmetrical shape is the belt ring preferably at its periphery a part of the transmission housing. Of the Belt wreath can do this on its circumference next to the one, for a Belt usable effective section also one or more, him axially Having one or both sides widening peripheral portions. However, it is also possible that the belt ring instead of or in addition to this also frontal part of the transmission housing is. The belt wreath can this is comparable to a pulley one or more, closed or have partially open end walls, in particular also serve for attachment to the planet can. The belt ring can on the circumference and / or front side and the be the only part of the transmission housing. In addition, it may be appropriate the planet carrier frontally to integrate as a wall in the transmission housing. The transmission housing thus preferably contains all rotating parts of the attachment gearbox except the belt ring and the output or drive side shaft. In particular, in the transmission housing at least the planetary gear set, the clutch, the brake and partly the be included fixed frame part. The output or drive side shaft can end with her a shaft end in the gearbox.

In covered a further advantageous embodiment according to claim 3 the one, for a belt usable effective portion of the belt rim at least an element from the group planetary gear set, clutch and brake axially complete and / or at least two elements from this group axially partially. The or the covered elements are here radially within the active portion of the belt ring arranged. Preferably, the active portion has such an inner radius that all elements of the group lie radially inside of it can. This arrangement ensures an axially very compact design. It is also possible to do that Effective section of the belt ring suitably for a convenient tilting moment axially over to arrange the, preferably common pivot bearing for the belt ring and the planet carrier.

In a further advantageous embodiment of the attachment gear according to a The first variant of claim 4, the clutch is a switchable Multi-plate clutch and the brake a multi-disc brake. The multi-plate clutch and the multi-disc brake can each over a multi-outer slats bearing Outer plate carrier and have an inner disk carrier carrying a plurality of inner disks. The Outside- and the inner disks of the multi-plate clutch or the multi-disc brake form a disk pack, which is used to transmit torque controlled by an axial force is loadable. Preferably, this is the outer disk carrier of Multi-plate clutch to the planet carrier, the inner disc carrier of Multi-plate clutch to the sun gear, the outer disc carrier of the Multi-disc brake the ring gear and the inner disc carrier of Multi-disc brake assigned to the fixed frame part rotationally fixed. The advantage of the lamellar construction over other constructions lies in the big one Friction surface at same or smaller outer diameter. Furthermore short switching times are achievable.

In a further advantageous variant of claim 4, the clutch is a switchable cone clutch and the brake is a cone brake. The cone clutch or the cone brake can be made single-acting here. The conical coupling or the cone brake in single-acting mode can have two friction bodies, one of which has an internal conical and the other an outer conical friction surface, which form a friction pair to each other, and one of which is axially loadable controlled against the other. In particular, in this case one of the friction body is a, an inner conical friction surface exhibiting outer ring and the other friction body, a corresponding outer conical friction surface exhibiting inner ring. Preferably, the outer ring of the clutch planetary gear, the inner ring of the clutch of the unit shaft, the outer ring of the brake to the ring gear and the inner ring of the brake to be assigned to the fixed frame member rotationally fixed. For the distribution of the friction torque, to improve the heat dissipation and to reduce switching shocks, it may also be advantageous in the cone clutch or the cone brake in single action, between the innenkoni rule friction surface of the outer ring and the outer conical friction surface of the inner ring loose a conical additional friction ring preferably in the form of a truncated cone shell between. In order to prevent the auxiliary friction ring stuck when opening on the inside and / or outside conical friction surface, the additional friction ring, z. B. be self-solvent by ovalization, or it may be suitable solvents, eg. B. can not be provided surface-parallel inner and outer conical friction surfaces.

The Cone coupling or the cone brake can also be designed double-acting. Such a cone clutch can have three friction bodies on the two inner conical and two outer conical friction surfaces so distribute that together they are two, adding in their effect Form friction pairings. One of the three friction bodies has two conical friction surfaces. He is one of the drive sides of the conical clutch rotation and axially displaceable assigned. This friction body is the other two friction bodies interposed, over only one conical friction surface each dispose and the two of the other drive side of the cone clutch rotatably assigned and one of them is controlled against the other two is axially displaceable. The one interposed friction body can from the other friction bodies on both sides concurrently frictionally effective, d. H. doubly effective, by the one controlled axially displaceable friction against the intermediate, axially displaceable friction body and with this on the other friction body suppressed.

For example can the cone clutch or the cone brake in double action so be executed that firstly an intermediate ring in the form of a double cone with two, preferably arranged in mirror image to each other inside conical friction surfaces rotatably and axially displaceable with the planet carrier or the ring gear is connected and secondly, two inner rings provided are each over a corresponding outer conical friction surface feature, and both the aggregate shaft and the fixed frame part are assigned rotationally fixed, and one of which against the intermediate ring and controlled with this against the other inner ring axially displaceable is.

For example can the cone clutch or the brake in double action also so be executed that firstly an intermediate ring in the form of a truncated cone with one inside and one outside conical friction surface, preferably parallel to each other surface are rotatably and axially displaceable with the planet or the ring gear is connected and secondly, an outer ring with a innenkonischen friction surface and an inner ring provided with an outer conical friction surface is, between which, preferably spaced parallel to the surface friction surfaces the intermediate ring is arranged, and both the aggregate shaft or the fixed frame member are assigned rotationally fixed, and of one against the intermediate ring and with this against the other Inner ring controlled axially displaceable. To prevent that the intermediate ring when opening on the inside and / or outside conical friction surface stuck, the intermediate ring, z. B. be self-dissolving by ovalization, or it can suitable solvents, z. B. not surface parallel internal and external conical friction surfaces or suitable axial pressure or pulling devices may be provided.

cone clutch or cone brakes generally have the advantage of low axial shifting forces transmit high torques to be able to. The conical friction surfaces can also radially close to the gearbox arranged and also large volume be what the heat dissipation and distribution benefits. About that In addition, there is the advantage, in particular compared with multi-plate clutches, axially shorter to build. It is therefore conceivable, the clutch or the brake as a multiple Double-acting cone clutch or as a conical clutch to perform with a lamella pact of conical outer and inner lamellae use. Such a coupling combines the advantages of a multi-plate clutch with disc-shaped friction bodies and a cone clutch with a conical friction body.

In a further advantageous embodiment according to claim 5, the clutch and / or the brake designed positively acting, in each case also provided a synchronization device which is connected upstream of the positively acting clutch or brake. The positive connection in the clutch or in the brake can be achieved by interlocking two suitable form-fitting parts, such as, in particular, in recesses axially engaging claws. In order to keep the axial length small, however, an inner and an outer toothing is preferably provided, which are positively connected to one another by axial telescoping. The synchronization device is used in each case for speed matching of the form-fitting parts and for this purpose contains at least two synchronizing elements, which are each suitably connected to one of the form-fitting parts. By rubbing the synchronizing elements against each other, the mold parts are accelerated or delayed accordingly, so that they run in time before their positive connection. With production of the positive connection, no friction torque acts between the synchronizing elements and the synchronization device is load-free. The synchronizing elements can be designed, for example, as inner and outer plates of a multi-plate clutch or preferably as inner and outer cone of a cone clutch. Main advantage ei ner such a clutch or brake is that a shift, in particular the closing despite form fit during operation under load and with low switching force is possible. The switching also takes place as in an exclusively traction effect also damped. It is also advantageous that after closing no slip is possible, as it may otherwise be the case with strong input or output side torque fluctuations. This advantage is particularly important in a direct arrangement of the attachment gear on the crankshaft, since there is no damping by a belt.

The The above synchronization devices may according to claim 5 preferably as lock synchronization devices be executed and therefore each additional have at least one blocking element, which is a compound of the form-fitting parts prevented as long as they run parallel. As soon as synchronization is achieved is, falls the blocking effect of the blocking element away and the positive connection can be made. Preferably, this is at least a blocking element rigidly connected to one of the synchronizing elements or with this one piece executed. The advantage of such a lock synchronization device is in the improved switchability and less wear.

For example Such a lock synchronization device together with the clutch or the brake be executed as follows: A switch body with a shift toothing and a gear body with a gear teeth are rotatably connected by the switch body controlled so axially displaced is that the gear teeth and the gear teeth are in meshing engagement can. The switch body leads rotatably and axially elastic at least one pressure piece with. A first synchronous element bears rigid a locking toothing, is axially guided by the switching body elastic over the Pressure piece displaceable and opposite the Pressure piece by a certain angle by friction on a second synchronizing element, which is rigidly connected to the gear wheel, limited rotatable. The Pressure piece can during displacement of the switch body, the first synchronizing element press against the second synchronizing element. As long as the two Synchronous elements rotate at different speeds, arises a friction torque, which is the first synchronous element with respect to the Pressure piece up twisted to a limit stop in a locked position, at the ratchet teeth in front of the shift teeth and a further shifting of the switching body is prevented. Only when synchronization is achieved does it intervene the synchronizing elements no more frictional torque and the first synchronizer element can be opposite the pressure piece turned back by the gear teeth in an exemption which are switching body and gear body by a form fit Tooth engagement can be connected.

Preferably here as a switching body a switching ring with a radially outer gearing and as a gangway a gear ring provided with a radially inner gear teeth. The individual pressure pieces can on regular basis be arranged the switching collar or be designed as a ring pressure piece. The synchronous elements are as inner synchronizer ring with external conical friction surface and as an outer synchronizer ring with internal conical friction surface executed. The special feature of this lock synchronization compared to, in particular from the vehicle transmission construction known embodiments is that instead of a radially externally operable, internally toothed sliding sleeve and an axially fixed and externally toothed Synchronizer, only an axially displaceable ring gear is provided, the in particularly compact design of radially inwardly operable.

There the above-described synchronization devices or Lock synchronization devices each contain their own couplings, can this in a generalization as the main clutch or main brake according to the invention be considered, the another, positive clutch or brake optionally downstream, wherein the respective drive connection via the Synchronized misappropriated even exist for a longer switching period frictionally can stay.

The auxiliary transmission according to the invention can be preset in an advantageous manner according to the independent claim 7 in different ways one or more ancillary components propelled:
First and foremost, it is possible to direct the supercharger directly to a single driven accessory or auxiliary work machine such as, in particular, an alternator, a power steering pump or an air conditioning compressor by coaxially and non-rotatably connecting the sun gear of the auxiliary transmission to a drive shaft of the accessory Belt ring is drivable by a belt, which in turn can be driven, for example, by a, arranged on a transmission or an engine of the vehicle pulley. In this case, the belt ring driven by the belt feeds the rotary power into the planetary gear set via the planetary gear carrier, which is rotationally rigidly connected to it. Depending on the switching state, the rotational power is output in the same direction, but with different translation via the sun gear to the rotatably connected to him drive shaft of the accessory. Insbesonde re at low engine speeds, ie in particular at engine idle or when starting or even with excessive speed demand, z. B. at increased requested cooling capacity is upshifted to the second switching state and translated into fast. In an advantageous manner, especially when the engine starts, falls below a predetermined speed limit, which may arise in particular from the gear ratio and idle speed, and / or extraordinary power demand in the second switching state with translation upshifted and upon reaching or exceeding the speed limit , Downshifted in particular at medium and high engine speeds in the first switching state with direct drive and spared the planetary gear set. It is also conceivable, for. B. at engine start, the auxiliary transmission briefly to switch to the third switching state, in this way load torque of the accessory is disconnected during the engine starting process.

moreover secondly, it is the same arrangement, but with exchange possible from input and output, the attachment gear a single, aborting accessory or an auxiliary engine, in particular auxiliary electric motors, Auxiliary internal combustion engines, directly to be put, whereby over the Belt wreath to a belt on, for example, an air conditioning compressor arranged pulley is driven off.

Besides that is Third, it is conceivable that the auxiliary gear of a group of several to be driven ancillary units or auxiliary working machines, in particular a group of three-phase alternator, power steering pump and air conditioning compressors, in common indirectly set by the sun gear coaxial with an output shaft a transmission or the main engine of the vehicle, in particular the crankshaft of the internal combustion engine, and the belt ring is connected via a common Belt drives the pulleys of the ancillaries of the group. The attachment gear can in this case with its fixed frame part preferably be attached directly to the engine block. The advantage of a short length comes in an arrangement in place of the crankshaft wheel even more Meaning too. By contrast, there is usually more radial space available. In Advantageously, when exceeded or below a predetermined speed limit, the in particular from the gear ratio and the idling speed can result for the group of ancillaries together to translate into slow or fast. If that Vehicle predominantly In city operation with long stance phases is operated, that can for a so arranged auxiliary gear even be gentle on the gear. in the third switching state, it is also conceivable, especially at engine start, to separate the common load moment of the group of ancillaries for a short time.

Finally is Fourth conceivable, several auxiliary gear in the aforementioned arrangements to combine in a common belt drive.

In a final one Generalization of the inventive idea, it is also conceivable instead of the belt ring another belt like a Chain wreath for a link chain or a cone pulley pair for a corresponding To provide pulling or pushing means, of which a cone pulley axially is displaceable. Furthermore Is it possible, the attachment gear also stationary outside of vehicles and not just for To use ancillaries.

following are six, each mounted on a driven accessory embodiments the attachment of the invention closer by means of drawings explained. It shows:

1 a section through a front-mounted gear, the planetary gear set is arranged axially between a multi-plate clutch and a multi-disc brake, both of which can be switched by closing switching principle and hydraulically,

2 a section through an auxiliary transmission with a multi-plate clutch of opening switching principle and a multi-disc brake of closing switching principle, which are mechanically rigidly coupled together and hydraulically switched,

3 a section through an auxiliary gear with a conical coupling of closing switching principle and a cone brake of opening switching principle, which are hydraulically coupled and hydraulically switched on,

4 a section through a front gear similar to that according to 3 , but with double-acting cone clutch and double-acting cone brake,

5 a section through a fly gear similar to that according to 3 , but with a clutch and a brake acting positively and each preceded by a single-cone lock synchronization devices, and

6 a section through a front gear similar to that according to 6 , but with double cone lock synchronization devices.

The auxiliary gear and the driven Ancillaries according to 1 to 6 have many common features. The outer shape of the attachment gear is characterized by a rotationally symmetrical gear housing. The circumference of the gear housing consists almost entirely of a belt rim which can be seen in the drawing above and below 1 , which is rotationally symmetrical and at the same time geometrically defines the one central transmission axis. The belt wreath 1 has in the scope of a mehrrilligen effective section. In addition, the coaxial widening of the belt ring 1 one or two circular-cylindrical sections provided on one or both sides next to the effective section, so that the belt rim 1 wrapped the auxiliary gear almost over its entire axial length in the scope. Since the Mehrrillige effective portion occupies a substantial part of the axial length of the attachment gear, it is externally very similar to an ordinary multi-grooved pulley, as it is used for vehicles.

The drive of the attachment gear is effected by a V-ribbed belt, which can be seen in dashed lines in the drawing above 2 , which is the effective section of the belt wreath 1 for this purpose, on a part of its circumference, drifting around. The V-ribbed belt 2 especially with a, from the belt ring 1 Axially spaced crankshaft sprocket of the internal combustion engine of a vehicle to be drivingly connected.

The auxiliary unit to be driven, for example a power steering pump arranged in a vehicle, is left in the drawing with its outer wall 3 and in the drawing center with its aggregate wave 4 shown in dashed lines. The aggregate shaft 4 has several shaft shoulders and protrudes vertically from the outer wall 3 out.

For mounting, the front-mounted gearbox is assembled in preassembled subassemblies in a suitable order on the unit shaft 4 coaxially mounted, suitably fastened and finally mounted on the front, in the drawing right side. In order to derive support moments, one is in the rear or rear of the attachment gear to the unit shaft 4 coaxial, fixed frame part 5 provided by several screws fixed to the outer wall 3 of the accessory is connected.

The attachment gear has a simple, single-stage planetary gear set. This contains a sun wheel 6 , a ring gear 7 and a multi-part planet carrier with a front and a rear beam cheek 8th and 9 between which individual planet gears 10 rotatably mounted and axially slidably secured. The gears of the planetary gear are spur gears with uniform tooth width. In known manner, the planet gears 10 both with the ring gear 7 , which is only internally toothed, as well as with the sun gear 6 in the tooth mesh. The planet carrier is with the belt ring 1 always rigidly connected and thus carries the gearbox. The formed in this way rigid rotary assembly of the transmission housing with integrated belt ring 1 and the planet carrier with its two carrier cheeks 8th and 9 is common on the aggregate wave 4 via a radial ball bearing 27 rotatably mounted. The sun wheel 6 is connected via its hub with the aggregate shaft coaxial fixed and secured axially on both sides. Further, the ring gear 7 at least indirectly on one or both cheeks 8th and 9 Sliding radially mounted and for absorbing axial forces between the support cheeks 8th and 9 Slidably secured axially.

The auxiliary transmission further comprises a clutch and a brake, both of which are hydraulically controlled via guided in pressure chambers piston switched. A corresponding control hydraulics is not shown in detail. The brake is located in the rear of the attachment gear. With the brake is the ring gear 7 on the fixed frame part 5 retainable. Axially between the brake and the transmission front, the clutch is arranged, via which the planet carrier and the sun gear 6 are mutually blockable and thus the above-described Rotationsverbunde with the unit shaft 4 is gleichschaltbar. The opening directions of the clutch and the brake are aligned with each other. Here, in the upper half of the drawing, the clutch is closed and the brake is open, ie the first switching state with direct drive and opened in the lower half of the drawing, the clutch and the brake closed, ie the first switching state of a translation shown in Quick. With positioned on corresponding actuators in the drawing motion arrows indicate the axial direction of switching to get into the other switching state.

The gearbox forms with the belt ring 1 as its Hauptumfangsbestandteil a rigid, liquid-tight unit that rotates in gearbox operation. It contains the planetary gear set, the clutch and the brake. The effective section of the belt wreath 1 is hereby arranged so that it at least partially envelops at least two of the aforementioned parts axially at least partially. Only the frame part 5 and the aggregate shaft 4 protrude through a remaining, to the outer wall 3 of the accessory directed end opening out of the transmission housing. The opening is there radially to the frame part 5 out with a sealing ring 19 sealed, with radial between belt ring 1 and the sealing ring 19 a rear end part of the transmission housing is provided, which seals the seal 19 wearing. At its front end, the gearbox is also tightly closed. The gearbox can be damaged by leakage to the piston with Hydrauli köl be filled and, not shown in detail in the drawing, are returned via a suction and regulated the amount contained in the attachment gear.

In the auxiliary transmissions according to 1 and 2 is in each case provided as a clutch a multi-plate clutch and brake as a multi-disc brake. The multi-plate clutch and the multi-disc brake are made comparable. The multi-plate clutch or multi-disc brake has a number of outer disks 11a respectively. 11b carrying outer plate carrier 12a respectively. 12b and a plurality of inner plates 13a respectively. 13b carrying inner disk carrier 14a respectively. 14b , The outer disc carrier 12a respectively. 12b and its outer blades 11a respectively. 11b as well as the inner disc carrier 14a respectively. 14b and its inner fins 13a respectively. 13b are to the aggregate wave 4 arranged coaxially. All outer plates 11 a / b or all inner plates 13 a / b are the same parts, and the two outer disk carrier 12 a / b or the two inner disk carrier 14 a / b have the same cross-section. The individual outer and inner plates 11 a / b and 13 a / b of the multi-plate clutch or multi-disc brake are in a known manner to their respective outer or inner disc carrier 12 a / b and 14 a / b guided axially, rotatably held and alternately successively axially layered. The two disc packs thus formed are for transmitting or for braking a torque via an axially displaceable pressure ring 17a respectively. 17b with an axial force against an axially fixed support ring 18a respectively. 18b resilient, so that the respective outer and inner fins 11a and 13a respectively. 11b and 13b can get into frictional engagement with each other. According to the invention, the outer disk carrier 12a the multi-plate clutch the planet carrier and thus the belt ring 1 , the inner disc carrier 14a the multi-plate clutch the sun gear 6 and thus the aggregate wave 4 , the outer disc carrier 12b the multi-disc brake the ring gear 7 and the inner disc carrier 14b the multi-disc brake the fixed frame part 5 and thus the outer wall 3 the auxiliary unit rotatably assigned.

In the auxiliary gear according to 1 is first seen that the planetary gear set axially between the, shown on the left in the drawing disc brake and the right in the drawing disc clutch and the gears of the planetary gear over its entire tooth width and axially partially the multi-disc brake of the V-ribbed belt 2 usable, multi-grooved section of the belt wreath 1 are radially covered. The gearbox is on its front side with a on the belt ring 1 frontally rigidly mounted, circular cover disc 20 tightly closed. The cover disc 20 is thus part of the co-rotating in gear transmission housing and stands on the outer disc carrier 12a the multi-plate clutch with the front beam cheek 8th the planet carrier rigidly connected. Consequently, the transmission housing with its components forms belt ring 1 and cover disc 20 together with the outer disk carrier 12a the multi-plate clutch and the planet carrier with its two carrier cheeks 8th and 9 a rigid, to the aggregate wave 4 coaxial rotation composite.

The aggregate shaft 4 of the accessory points, in the drawing from right to left, a front end of the shaft and the intermittently increasing in diameter a front, a middle and a rear shaft shoulder 21 . 22 and 23 and a coaxial oil passage hole 26 which ends in an opening at the end of the shaft. Around the middle shaft shoulder 22 around the gears of the planetary gear set are arranged, wherein the sun gear 6 with his hub on the middle shaft heel 22 rotatably pressed and axially secured. The ring gear 7 is over one on the outer lamp carrier 12a Slip the ring radially in a sliding manner and between the two beam cheeks 8th and 9 Slidably secured axially.

The front shaft shoulder 21 carries a radial ball bearing 27 , which is designed as a double row deep groove ball bearing, and a support ring 28 , The radial ball bearing 27 Firstly, it sits firmly with its outer ring in a radially outer bearing bush of the front beam cheek 8th the Planetenradträgers and secondly with its inner ring fixed in a radially inner bearing bush of the support ring 28 , The support ring 28 is with its inner bearing bush on the front shaft section 21 rotatably pressed and axially secured. About the radial ball bearing 27 is the above-described rigid rotary joint together on the aggregate shaft 4 coaxially mounted rotatably.

To the front shaft shoulder 21 In addition, the multi-plate clutch including actuating means is arranged coaxially. The outer disc carrier 12a The multi-plate clutch is axially between the front beam cheek 8th and the cover disc 20 arranged and has a comparable outer diameter as the ring gear 7 on. The inner disc carrier 14a the multi-plate clutch, however, is with the support ring 28 rigidly connected and to the unit shaft 4 Consequently, also rotatably and axially secured.

The multi-plate clutch has a hydraulically actuatable pressure in a pressure chamber 16a axially displaceable piston 15a , The piston 15a is in the pressure room 16a from the support ring 28 held against rotation and over guide pins 29 axially guided. The pressure room 16a is here together with the piston 15a radially inside the disk pack the multi-plate clutch. Axial between the rear side of this plate pack and the front beam cheek 8th is the axially displaceable pressure ring 17a and on the opposite, front side of this plate pack, the axially fixed support ring 18a intended. So that the pressure ring 17a can act on this disk set with an axial force, he is with the piston 15a rigidly connected and axially guided over this. To close the multi-plate clutch, the piston 15a hydraulically forward towards the support ring 18a operated, whereby the pressure ring 17a the disk pack pushes together and against the support ring 17a suppressed. The hydraulic oil required for closing becomes the pressure chamber 16a next to the piston 15a from the support ring 28 and the shaft end at the front shaft portion 21 is limited, over the oil passage hole 26 fed.

Finally, around the rear shaft section 23 axially between the rear beam cheek 9 of the planet carrier and the outer wall 3 the auxiliary unit, the multi-disc brake including actuating means and the frame part 5 arranged coaxially. The outer disc carrier 12b the multi-disc brake and the ring gear 7 have a comparable outer diameter and are on the outside by an axial web 35 rigidly connected with each other. The outer disc carrier 12b is therefore on the ring gear 7 on the aggregate shaft 4 rotatably held and secured axially. The inner disc carrier 14b is, however, rigid on the radial outer side of the unit shaft 4 coaxial cylinder wall 30 of the frame part 5 attached.

The multi-disc brake also has a hydraulically actuatable pressure in a pressure chamber 16b axially displaceably arranged pistons 15b , The piston 15b and the pressure room 16b are annular, wherein the piston 15b along the radial cylinder wall 30 of the frame part 5 axially guided and sealed by two sealing rings and together with the frame part 5 is determined in gear operation. The pressure room 16b is located together with the piston 15b radially inside the disk pack of the multi-disc brake. Axial between the front side of this plate pack and the rear beam cheek 9 is the axially displaceable pressure ring 18b and on the opposite, rear side of the disk pack, the axially fixed support ring 17b intended. So that the pressure ring 18b can act on the disk set with an axial force, he is with the piston 15b rigidly connected and on the inner disk carrier 14b held against rotation and additionally guided axially. To close the multi-disc brake, the piston 15b hydraulically backwards towards the support ring 18b operated, whereby the pressure ring 17b the disk pack pushes together and against the support ring 17b suppressed. The hydraulic oil required for closing becomes the pressure chamber 16b supplied over, not shown in detail in the drawing oil passageways. The pressure chamber 16b is next to the piston 15b radially outward of the cylinder wall 30 the frame part, radially inward of a cylindrical wall of the piston 15b and axially opposite the piston 15b bounded by a ring insert.

The multi-plate clutch and the Lammellenbremse are each of closing switching principle and open automatically without bias. In the first switching state, ie in the direct drive, only the piston is 15a or in the second in the second switching state, ie in overdrive, only the piston 15b hydraulically acted upon by an actuating pressure, whereby the pressure ring 18a respectively. 18b presses on the respective disk set so that it is frictionally closed and can transmit or decelerate a rotational movement. Accordingly, in the first switching state of the planet carrier against the sun gear 6 blocked and in the second switching state, the ring gear 7 on the fixed frame part 5 braked holding. To change the switching state, the corresponding actuation pressures can be alternately generated and released in timed sequence. The multi-plate clutch and the multi-disc brake can be switched independently of each other, so that the third, fourth or further switching states are possible. The two pressure chambers 16a respectively. 16b However, also not shown in the drawing, be coupled via a hydraulic household, with the same actuating pressures the piston surface of the piston 15a may be considered appropriate.

This in 2 shown intent gear differs from the above according to 1 On the one hand, the planetary gear set is arranged directly on the front side of the attachment gear, on the right in the drawing, and the multi-plate clutch is arranged axially between the planet gear carrier and the multi-disc brake. On the other hand, the multi-plate clutch and the multi-disc brake are mechanically rigidly coupled and have in common only one piston 15c and a pressure room 16c , however, almost identical to the piston 15b and the pressure room 16b of the attachment gear according to 1 are constructed. The multi-plate clutch is of closing and the multi-disc brake of opening switching principle.

The transmission housing co-rotating gearbox is at its front end by the front support cheek 8th the planet carrier formed. A central mounting opening provided therein is provided with a removable round cover 31 tightly closed. The front support cheek 8th and the round lid 31 are components of the gearbox. The rear beam cheek 9 of the planet carrier is with the outer disc carrier 12a the multi-plate clutch rigidly connected. Consequently, the transmission housing with its components forms belt ring 1 , front support cheek 8th and round covers 31 , together with the rear beam cheek 9 the planet carrier and the outer disc carrier 12a the multi-plate clutch a rigid, the unit shaft 4 coaxial rotation composite.

The aggregate shaft 4 the auxiliary unit has, in the drawing from right to left, a front end of the shaft and in the intermittently increasing in diameter a front and a rear shaft shoulder 21 and 23 on.

Around the front section of the front shaft shoulder 22 around and adjacent to the shaft end, the gears of the planetary gear set are arranged, wherein the sun gear 6 with his hub on the front shaft heel 22 rotatably pressed and axially secured. The ring gear 7 is over the web rigidly connected to it 35 on the rear beam cheek 9 the planet carrier slidably radially mounted and also between the support cheeks 8th and 9 Slidably secured axially.

The front shaft shoulder 21 also carries on its rear section, adjacent to the sun gear 6 a radial ball bearing 27 , which is designed as a double row deep groove ball bearing and a support ring 28 , The radial ball bearing 27 Firstly, it sits firmly with its outer ring in a radially outer bearing bush of the rear beam cheek 9 the Planetenradträgers and secondly with its inner ring fixed in a radially inner bearing bush of the support ring 28 , The support ring 28 is with its inner bearing bush on the front shaft section 21 rotatably pressed and axially secured. About the radial ball bearing 27 is the above-described rigid rotary joint together on the aggregate shaft 4 coaxially mounted rotatably. The inner disc carrier 14a the multi-plate clutch is with the support ring 28 rigidly connected and to the unit shaft 4 Consequently, also rotatably and axially secured.

Around the rear shaft section 23 axially between the disk pack of the multi-plate clutch and the outer wall 3 of the accessory are the multi-disc brake, the frame part 5 and common actuating means of the multi-disc brake and multi-plate clutch arranged. The outer disc carrier 12b the multi-disc brake and the ring gear 7 are on the outside of the outer disk carrier 12a the multi-plate clutch radially outward by a bridge 35 rigidly connected with each other. The outer disc carrier 12b is therefore on the ring gear 7 on the aggregate shaft 4 rotatably held and secured axially. The inner disc carrier 14b is, however, rigid on the radial outer side of the unit shaft 4 coaxial cylinder wall 30 of the frame part 5 attached.

The common, hydraulically acted upon by an actuating pressure, annular piston 15c , the common, annular pressure chamber 16c and the pressure plate associated with the disk pack of the multi-disc brake 17b differ in arrangement and function, as far as the operation of the multi-disc brake, only slightly from the piston 15b , the pressure room 16b and the pressure ring 17b of the attachment gear according to 1 , The disk pack of the multi-plate clutch is the pressure ring 17a assigned. The pressure ring 17a is to the piston 15c and to the pressure ring 17b mounted axially fixed and uniformly rotatable and beyond the inner disc carrier 14a held against rotation and additionally guided axially. For rotary mounting is axially between the pressure ring 17b and the pressure ring 17a , which are arranged axially mirror images of each other, a rolling bearing 32 provided that is designed as angular contact ball bearings. Further, the piston 15c , the two pressure rings 17 a / b and the rolling bearing 32 , which together form an axially displaceable composite, coaxial with the unit shaft 4 a leaf spring 33 and a coil spring 34 assigned coaxially. The coil spring 34 clamps this composite in the closing direction of the multi-plate clutch, that is, to the front of the attachment gear towards, so that open without actuation pressure the multi-disc brake and the multi-plate clutch is closed. The coil spring 34 this is radially between the rear shaft portion 23 and the frame part 5 arranged in a cavity and on the outer wall 3 the auxiliary unit and axially supported against the displaceable composite The leaf spring 33 is axially fixed to the support ring 28 supported and presses the pressure ring 17a axially backwards against the rolling bearing 32 to pre-tension this or around the pressure ring 17a axially fixed to the pressure ring 17b and to the piston 15c to keep.

In the first switching state is the piston 15c not acted upon by the operating pressure, so that the coil spring 34 against the leaf spring 33 the pressure ring 16a axially presses on the disk set of the multi-plate clutch and the pressure ring 16b is released from the disk set of the disk brake. In the second switching state is the piston 15c against the coil spring 34 subjected to the actuating pressure, whereby the pressure ring 16b axially presses on the disk set of the multi-disc brake and the pressure ring 16a is released from the disk pack. To change the switching state of the operating pressure is generated or released in a suitable manner.

In the auxiliary gear according to 3 is as a clutch a conical clutch with closing switching principle and as a brake with a cone brake opening switching principle provided, which are hydraulically coupled and hydraulically switched on and spring-biased off automatically. The cone clutch or the cone brake has an outer ring which has an internal conical friction surface 50a respectively. 50b and one, an outer conical friction surface having inner ring 51a respectively. 51b , The outer ring 50a respectively. 50b and its internal conical friction surface and the inner ring 51a respectively. 51b and its outer conical friction surface are coaxial with the unit shaft 4 arranged, wherein the outer and the inner conical friction surface of the conical coupling or the cone brake surface-parallel spaced from each other and between a conical auxiliary friction ring 52a respectively. 52b in the form of a truncated cone shell and loosely inserted with suitable friction surfaces. The outer and inner conical friction surface and the additional friction ring 52a the cone clutch are to the corresponding friction surfaces and the auxiliary friction ring 52b the cone brake arranged in a mirror image in such a way that the front circumference and the latter circumference are the front of the attachment gear towards. In addition, the two additional friction rings 52 a / b and the two outer rings 50 a / b each identical parts and the outer conical friction surfaces of the two inner rings 51 a / b executed the same. The outer ring 50a respectively. 50b and the inner ring 51a respectively. 51b as well as the intermediate additional friction ring 52a respectively. 52b the conical coupling or the cone brake form an inner and an outer friction pair, which together with the frictional transmission or the frictional braking of a rotary power with an axial force can be loaded.

For this purpose, the two outer rings 50 a / b axially fixed and the two inner rings 51 a / b axially guided and controlled sliding performed. According to the invention here is the outer ring 50a the cone clutch the planet carrier, the inner ring 51a the cone clutch of the aggregate shaft 4 and with it the sun wheel 6 , the outer ring 50b the cone brake the ring gear 7 and the inner ring 51b the cone brake the fixed frame part 5 assigned rotationally fixed.

Similar to the in 2 shown attachment gear, the planetary gear set is arranged directly on the front of the attachment gear and the cone clutch axially between the planet carrier and the cone brake. The gearbox housing with the integrated belt ring 1 However, is axially much narrower than in the embodiments described above, so that the mehrrillige effective portion of the belt ring 1 directly on the front end of the gear housing ends and the belt ring 1 only on its rear, the outer wall 3 the accessory facing side is slightly extended with a neutral peripheral portion. The gears of the planetary gear set are therefore again over the entire tooth width of the multi-groove active portion of the belt ring 1 covered. In addition, the cone clutch is complete and the cone brake partially covered. The gear housing is at its rear end radially to the frame part 5 out with a sealing ring 19 sealed. The front end face of the gear housing is essentially through the front beam cheek 8th of the planet carrier in the manner of a cup wheel formed in the central area by an inserted round cover 31 is tightly closed. As the rear beam cheek 9 of the planet carrier also with the outer ring 50a the cone clutch is rigidly connected, forms the gear housing with its components belt ring 1 , front support cheek 8th the planet carrier and round cover 31 , together with the rear beam cheek 9 of the planet carrier and with the outer ring 50a the cone clutch a rigid, the unit shaft 4 coaxial rotation composite.

The aggregate shaft 4 of the accessory has, in the drawing from right to left, a front end of the shaft and in diameter ascendingly a front, a first spur gear, a second spur gear, and rear shaft shoulder 21 . 24 . 25 , and 23 on. Together around the front and first toothed shaft shoulder 21 and 24 around the planetary gear is arranged, with its sun gear 6 with its straight toothed hub rotationally fixed on the first straight toothed shaft shoulder 24 deferred and secured axially. The front support cheek 9 the Planetenradträgers has radially outward on a cylindrical extension which engages around the ring gear on its outer circumference, whereby the Holrad 7 is radially slidably mounted on the planet carrier. In addition, the ring gear 7 between the two axial inner sides of the rear and front beam cheeks 8th and 9 Sliding axially secured on both sides. On the front shaft shoulder 21 is a designed as a double row deep groove ball bearing radial ball bearing 27 Pressed tightly over its inner ring and axially secured. With its outer ring sits the radial ball bearing 27 firmly in a radially outer, folded bushing of the front beam cheek 8th of the planet carrier. About the radial ball bearing 27 is the above-described rigid rotary joint together on the aggregate shaft 4 coaxial rotatably mounted and secured axially.

Axially between the rear beam cheek 9 and the outer wall 3 the accessory are the components of the cone clutch and the cone brake described above and their actuators coaxial with the unit shaft 4 arranged. The inner ring 51a the cone clutch has a straight hub teeth, with this on the second straight toothed shaft shoulder 25 axially slidably and rotatably engaged. To Vorspan tion of the inner ring 51a in the opening direction is a first cone helical spring 53a provided with the one end turn on the inner ring 51a abuts and with the other end turn on the sun gear 6 is axially supported. The outer ring 50b the cone brake and the ring gear 7 are on the outside radially outward on the outer ring 50a the cone clutch over by a bridge 35 rigidly connected with each other. The outer ring 50b is here via the ring gear 7 also coaxial with the unit shaft 4 rotatably held and secured axially. The inner ring 51b The cone brake, however, is on the frame part 5 arranged rotationally fixed and guided axially on this. For this purpose, the inner ring 51b an internal toothing, which has an external toothing on a first, radially outer cylinder wall 54 of the frame part 5 slidably engaged. For preloading the inner ring 51b in the opening direction is a second cone helical spring 53b provided with the one end turn on the inner ring 51b abuts and with the other end turn on a snap ring on the frame part 5 is axially supported. The spring force of the second conical spring 53b is sufficient, the inner ring 51b over the additional friction ring 52b so against the outer ring 50b to press that during transmission operation under load a frictional connection is possible.

To actuate the multi-plate clutch or the multi-disc brake, this is a hydraulically acted upon by a switching pressure, in a first or second annular pressure chamber 56a respectively. 56b axially guided first and second annular piston 57a respectively. 57b assigned. The two pressure chambers 56 a / b are by a plurality of obliquely radial oil passage channels in the inner cylinder wall 55 of the frame part 5 connected with each other. By means of the pressurizable ring piston 57a respectively. 57b is the inner ring 51a respectively. 51b the clutch or the brake axially against the shaft end against the spring force of the first and second conical helical spring 53a respectively. 53b axially displaceable. The axial switching path of the inner ring 51a respectively. 51b is here in the open position by the on the outer ring 50a respectively. 50b adjacent auxiliary friction ring 52a respectively. 52b and in the closed position of an abutment shoulder between shaft sections 25 and 23 or through one in the cylinder wall 55 bounded radially outside snap ring limited. The first pressure room 56a is next to the ring piston 57a radially inward from the rear shaft section 23 and radially outward of an inner cylinder wall 55 of the frame part 5 as well as axially from the outer wall 3 limited. The first ring piston 57a is rigid with the inner ring 51a connected to the cone clutch. He can, as in 4 shown, also loosely abut on this and be suitably spaced in the rear region for keeping open the oil passage channel with respect to the outer wall with a ring member. The second pressure chamber 56b is next to the second ring piston 57b axially from the frame part 5 as well as radially from the cylinder wall 54 and 55 of the frame part 5 limited. The second ring piston 57b is a part of the inner ring 51b or executed in one piece with this. The hydraulic oil required for switching becomes the two pressure chambers 56 a / b supplied by at least one, not shown in the drawing, another oil passageway. As the ring piston 57a respectively. 57b in the pressure room 56a respectively. 56b is performed without sealing ring, the hydraulic oil can escape into the auxiliary gear and, not shown in detail in the drawing, are returned.

In the first switching state, both ring pistons 57 a / b is not acted upon by the switching pressure, so that by the axial spring force of the respective cone helical spring 53a respectively. 53b the cone clutch is opened in a preloaded manner and the cone brake is closed in a pretensioned manner. Consequently, the ring gear 7 on the frame part 5 holding braked and the planet carrier opposite the sun gear 6 and the aggregate shaft 4 rotating freely. To achieve the second switching state both ring pistons 57 a / b hydraulically with the switching pressure against the spring forces of the conical helical springs 53 a / b overrun. Because the two inner rings 51 a / b are biased with the same spring force and the piston surface of the ring piston 57b of the inner ring 51b is significantly larger than that of the ring piston 57a of the inner ring 51a the cone brake pushes the inner ring 51b the cone brake correspondingly faster than the inner ring 51a the cone clutch, so that the cone brake opens in a suitable time before closing the cone clutch. If the cone brake is completely released and the cone clutch frictionally closed, the second switching state is reached. Consequently, first, the ring gear 7 unrestrained and secondly the rotational connection via the inner ring 51a the cone clutch with the aggregate shaft 4 brought into line. To re-attain the first switching state, the two conical screw spring 53 a / b also designed to fit the two pressure chambers 56 a / b can be emptied against any residual pressure. Due to the different piston area, the cone brake can close in a suitable manner in time before opening the cone clutch.

This in 4 shown attachment gear is the following exceptions identical to the attachment gear according to 3 Executed: The cone clutch and the cone brake are each double-acting. The cone clutch or the cone brake has this one, an inner conical friction surface having outer ring 60a respectively. 60b , via an inner ring having an outer conical friction surface 61a respectively. 61b , over one, intermediate ring 62a respectively. 62b with an internally conical and an outer conical friction surface in the form of a truncated cone shell and a support ring 63a respectively. 63b , The internal conical friction surface of the outer ring 60a respectively. 60b and the outer conical friction surface of the inner ring 61a respectively. 61b stand face to face spaced apart from each other, between which the conical intermediate ring is arranged. The aforementioned components are all to the aggregate shaft 4 arranged coaxially. The support ring 63a respectively. 63b is with the rear support cheek 9 of the planet carrier or over the bridge 35 with the ring gear 7 rigidly connected. The support ring 63a respectively. 63b has an inner cylindrical and an end-side support surface, wherein the outer ring 60a respectively. 60b is slidably radially mounted on its outer cylindrical circumference on the inner cylindrical support surface and is axially supported on its end face in the closing direction of the clutch or the brake on the front-side support surface. The intermediate ring 62a respectively. 62b is on the support ring 63a respectively. 63b rotatably held and axially displaceable. For this purpose, the support ring on axial claws, which are in corresponding recesses in the support ring 63a respectively. 63b intervention. The inner ring 61a respectively. 61b different from the inner ring 51 respectively. 51b according to 3 only in that it has recesses in the axial claws of the outer ring 60a respectively. 60b engage, leaving the outer ring 60a respectively. 60b with the inner ring 61a respectively. 61b rotatably and axially movably connected.

In particular, the inner ring 61a respectively. 61b again with the aggregate shaft 4 or the frame part 5 rotatably and on the pressurizable piston 57a respectively. 57b controlled axially displaceable. When closing the clutch or the brake pushes the piston 57a respectively. 57b the inner ring 61a respectively. 61b with its inner conical friction surface against initially against the outer conical friction surface of the intermediate ring 62a respectively. 62b , whereby it is displaced axially in the closing direction and thereby with its outer conical friction surface against the inner conical friction surface of the outer ring 60a respectively. 60b suppressed. Because the outer ring 60a respectively. 60b supported axially in the closing direction and with the inner ring 61a respectively. 61b rotatably connected, embrace this the intermediate ring 62a respectively. 62b from both sides concurrently and frictionally, ie double acting, so that a rotational power can be transmitted or braked by friction. For safe release of the intermediate ring 62a respectively. 62b when opening the clutch or the brake, a, not shown in detail in the drawing, solvent provided or the intermediate ring 62a respectively. 62b , z. B. be self-solvent by ovalization.

The opening and closing operation of the clutch or the brake and the change between the first and the second switching state otherwise takes place as in the 3 illustrated embodiment.

The front gears according to 5 and 6 are similar to the header gear according to 3 and 4 executed, wherein in each case the clutch and the brake are formed positively. The clutch or the brake is preceded by a lock synchronization device, which in 5 as single acting and in 6 designed as a double-acting cone clutch with a blocking function. The clutch is of closing and the brake of opening switching principle. The clutch and the brake are coupled via a hydraulic household and controlled hydraulically switched on and ferdervorgespannt off automatically. The lock synchronization device of the clutch or the brake is mechanically coupled on and off by the clutch or the brake.

The clutch or the brake of the attachment gear according to 5 has a switching ring 74a respectively. 74b with a radially external switching toothing 76a respectively. 76b and over an outer ring 70a respectively. 70b with a radially inner gear teeth 77a respectively. 77b , The switching ring 74a The coupling is similar to the inner ring 51a according to 3 via its straight-toothed hub with the second straight-toothed shaft section 25 the aggregate shaft 4 rotatably connected and axially guided and connected via the annular piston 57a controlled axially displaceable and over the cone helical spring 53a biased in the opening direction. Also the switching ring 74b the brake is similar to the inner ring 51b according to 3 about its internal teeth with the external teeth of the outer edge of the cylinder 54 of the frame part 5 rotatably and axially guided connected and the integrated annular piston 57b controlled axially displaceable and over the cone helical spring 53b biased in the closing direction. The axial switching path of the gear rim 74a respectively. 74b is in the open position of an abutment shoulder on the unit shaft 4 or a snap ring on the frame part 5 limited. In the closed position is the axial switching path of the switching ring 74a respectively. 74b also from the hub of the sun gear 6 or from the front end of the outer ring wall 54 of the frame part 5 limited. The switching ring 74a respectively. 74b and the outer ring 70a respectively. 70b can be positively connected to each other by the axial by switching the gear 74a respectively. 74 the outer switching teeth 76a respectively. 76bb into the internal gear teeth 77a respectively. 77b of the outer ring 70a respectively. 70b intervenes.

The switching ring 74a respectively. 74b bears radially on the outside via its gear teeth 76a respectively. 76b rotatably and axially guided a ring pressure piece 71a respectively. 71b , For this purpose, a corresponding internal toothing 75a respectively. 75b has, with the gearing 76a respectively. 76b axially sliding always in one handle stands. The ring pressure piece 71a respectively. 71b is from the circuit 74a respectively. 74b spring-coupled in both switching directions. For this purpose are axially between the ring pressure piece 71a respectively. 71b and the gear rim 74a respectively. 74b on guide pins 78a respectively. 78b guided pressure springs 79a respectively. 79b provided the ring pressure piece 71a respectively. 71b press biased in closing direction. The guide pins 78a respectively. 78b lead and center additionally the Rint piece 71a respectively. 71b opposite the gear rim 74a respectively. 74b , There is also a pullback tab 80a respectively. 80b provided the ring pressure piece 71a respectively. 71b when opening the gearshift 74a respectively. 74b pulls back into an open position.

The clutch also has a, an inner conical friction surface having outer ring 70a respectively. 70b and via a, an outer conical friction surface having synchronizer ring 72a respectively. 72b , Their friction surfaces form a friction pair, which can be loaded with an axial force for frictional-force transmission or for frictional-deceleration braking. This is the outer ring 70a respectively. 70b with the rear support cheek 9 or over a bridge 35 with the ring gear 7 rigidly connected and thus to the unit shaft 4 axially fixed and rotatably mounted. The synchronizer ring 72a respectively. 72b is, not shown in the drawing, to the ring pressure piece 71a respectively. 71b due to friction on the outer ring 70a respectively. 70b rotatable by a small angle to a stop. For this purpose, in the synchronizer ring 72a respectively. 72b be provided in particular in the scope regularly arranged grooves, between the side walls in each case a circumferentially smaller stop element of the ring pressure piece 71a respectively. 71b is limited in the turning path. It is conceivable, for. B. grooves in synchronizer ring 72a respectively. 72b To arrange circumferentially and as axially projecting into the grooves stop elements the corresponding axially elongated guide pins 78a respectively. 78b to use. The synchronizer ring 72a respectively. 72b has radially inward continued via an internal locking teeth, which the shift teeth 76a respectively. 76b of the outer ring 70a respectively. 70b in position on the stop prevents it from switching on and can release in the other position. Furthermore, the synchronizer ring 72a respectively. 72b from the ring pressure piece 71a respectively. 71b centered and axially against the outer ring 70a respectively. 70b displaceable. With the exception of the switching ring 74a respectively. 74b Both the clutch and the brake including their Sperrsynchronisationseinrichtungen are the same and to the unit shaft 4 coaxial. In addition, the clutch and the brake are arranged mirror-inverted in such a way that the friction surfaces of the conical coupling Umfangssenger and the friction surfaces cone brake are weitweitger to the front of the attachment gear.

The attachment gear according to 5 with the exception of the clutch and the brake is almost identical to the embodiment according to 3 executed, so that the local drawing description applies mutatis mutandis. The attachment gear according to

5 However, due to the more complex design of the clutch or brake axially slightly longer running. So is the belt wreath 1 extended slightly further axially on its rear side. Also the jetty 35 and the second straight toothed shaft shoulder 25 and the rear shaft shoulder 23 are longer dimensioned.

The clutch or brake and their bevel clutch or conical brake acting as a blocking synchronizer act as follows: In the open position, the gear rim is 74a respectively. 74b through the cone screw spring 53a or the ring piston 57b axially held so that the shift teeth 76a respectively. 76b the switching ring 74a respectively. 74b only in the internal toothing 75a respectively. 75b of the ring pressure piece 71a respectively. 71b , ie neither in the gear teeth 77a respectively. 77b of the outer ring 70a respectively. 70b still in the locking teeth 73a respectively. 73b of the synchronizer ring 72a respectively. 72b engage axially. Consequently, there is between the switching ring 74a respectively. 74b and the outer ring 70a respectively. 70b no positive rotary connection. The synchronizer ring 72a respectively. 72b with the locking teeth 73a respectively. 73b is in the open position to the small angle of rotation relative to the ring pressure piece 71a respectively. 71b rotatably released. In addition, the outer ring 70a respectively. 70b and the synchronizer ring 72a respectively. 72b axially spaced apart so far that ideally no torque is transmitted.

When closing the ring gear 74a respectively. 74b through the ring piston 57a or the cone screw spring 53b pushed axially in the closing direction. Here is the ring pressure piece 71a respectively. 71b from the gear rim 74a respectively. 74b through the compression springs 79a respectively. 79b mitverschoben and axially against the synchronizer ring 72a respectively. 72b pressed. The ring pressure piece 71a respectively. 71b shifts the synchronizer ring 72a respectively. 72b axially and presses it with its outer conical friction surface against the inner conical friction surface of the outer ring 70a respectively. 70b , As long as the ring pressure piece 71a respectively. 71b and the outer ring 70a respectively. 70b rotate at different speeds, creates a friction torque that the synchronizer ring 72a respectively. 72b with the locking teeth 73a respectively. 73b until reaching the stop so far twisted, preferably only by half a tooth width, until the ratchet teeth of the ratchet teeth 73a respectively. 73b before the gear teeth 76a respectively. 76b stand and the indexing of the switching ring 74a respectively. 74b lock. Due to the friction between the conical friction surfaces of synchronizer ring 72a respectively. 72b and outer ring 70a respectively. 70b becomes the ring pressure piece 71a accelerated or decelerated or the outer ring of the clutch 70b braked holding the brake and so the synchronization between the outer ring 70a , Ring pressure piece 71a and gear rim 74a the coupling made or the standstill of the outer ring 70b the brake causes. After synchronism or standstill is established, no friction torque acts on the synchronizer ring 72a respectively. 72b , It can be adjusted by tooth chamfers of the gearing 76a respectively. 76b turn back. This is the switching ring 74a respectively. 74b no longer locked and can be in the gear teeth 77a respectively. 77b of the outer ring 70a respectively. 70b be pushed. The positive rotational connection between the unit shaft 4 or frame part 5 and the outer ring 70a respectively. 70b is manufactured, and the cone clutch or the cone brake is load-free.

When opening the ring gear 74a respectively. 74b through the cone screw spring 53a or the annular piston 57b axially in the opposite, ie pushed in the opening direction. Here are the gearing 76a respectively. 76b the switching ring 74a respectively. 74b first the gear teeth 77a respectively. 77b of the outer ring 70a respectively. 70b and then the locking teeth 73a respectively. 73b of the synchronizer ring 72a respectively. 72b free. The ring pressure piece 71a respectively. 71b gets over the pull tabs 80a respectively. 80b when reaching the opening position of the switching ring 74a respectively. 74b forcibly withdrawn. So that the synchronizer ring 72a respectively. 72b safe from the outer ring 74a respectively. 74b can solve, is on the ring pressure piece 71a respectively. 71b radially outside a snap ring provided in a suitably axially wider annular groove in the synchronizer ring 72a respectively. 72b projects radially, and the synchronizer ring 72a respectively. 72b on withdrawal of the pressure piece 71a respectively. 71b retires with a delay. After releasing acts between the synchronizer ring 72a respectively. 72b and the outer ring 70a respectively. 70b ideally no friction torque anymore.

In the first switching state, the clutch and the brake is off, accordingly, the two ring pistons 57 a / b is not hydraulically loaded with the switching pressure. As a result, the clutch is opened and the brake is closed. Consequently, the ring gear 7 on the frame part 5 braced in a form-fitting manner and the planet carrier with respect to the sun gear 6 rotating freely. In the second switching state clutch and the brake is turned on. Consequently, the two ring pistons 57 a / b acted upon hydraulically with the switching pressure, so that the clutch is positively closed and the locking brake is open. Consequently, first, the ring gear 7 unrestrained and secondly the rotational connection via the pressure piece 71a and the gear rim 74a with the aggregate shaft 4 is the same.

Finally, in 6 an attachment gear shown, which is almost identical to the embodiment according to 5 is carried out, in contrast, the cone clutch and the cone brake of the respective locking synchronization device is double-acting. The cone clutch or the cone brake therefore has an outer synchronous ring having an internal conical friction surface 90a respectively. 90b , via an inner synchronizing ring having an outer conical friction surface 91a respectively. 91b , via an intermediate ring 92a respectively. 92b with an internally conical and an outer conical friction surface in the form of a truncated cone shell and a gear wheel 98a respectively. 98b , The internal conical friction surface of the outer synchronizer ring 90a respectively. 90b and the outer tapered friction surface of the inner synchronizer ring 91a respectively. 91b stand face to face spaced apart from each other, between which the conical intermediate ring 92a respectively. 92b is arranged. The aforementioned components are all to the aggregate shaft 4 arranged coaxially. Instead of the outer ring 70a respectively. 70b according to 5 is the gear wheel 98a respectively. 98b provided, however, a comparable gear teeth 97a respectively. 97b and also with the rear beam cheek 9 of the planet carrier or over the bridge 35 with the ring gear 7 is rigidly connected. The gear wheel 98a respectively. 98b has an inner cylindrical and an end-side support surface, wherein the outer synchronizer ring 90a respectively. 90b on its outer cylindrical circumference on the inner cylindrical support surface of the gear wheel 98a respectively. 98b slidably mounted radially and on its front side in the closing direction of the clutch or the brake on the front-side support surface of the gear wheel 98a respectively. 98b slidably supported axially. The intermediate ring 92a respectively. 92b is at the gear wheel 98a respectively. 98b rotatably held and axially displaceable. For this purpose, the intermediate ring 92a respectively. 92b axial claws on which in corresponding recesses in the gear wheel 98a respectively. 98b intervention. The inner synchronizer ring 91a respectively. 91b differs from the synchronizer ring 72a respectively. 72b according to 5 merely by having recesses in the axial claws of the outer synchronizer ring 90a respectively. 90b engage, leaving the outer synchronizer ring 90a respectively. 90b with the inner synchronizer ring 91a respectively. 91b rotatably and axially movably connected. In particular, the inner synchronizer ring 91a respectively. 91b with the ring pressure piece 71a respectively. 71b in the same way as in 5 connected.

When closing the clutch or the brake presses the ring pressure piece 71a respectively. 71b the inner synchronizer ring 91a respectively. 91b with its innenkonischen friction surface first against the outer conical friction surface of the intermediate ring 92a respectively. 92b , whereby it is displaced axially in the closing direction and thereby with its outer conical friction surface against the internal conical friction surface of the outer synchronizing ring 90a respectively. 90b suppressed. Because the outside synchronizer ring 90a respectively. 90b axially in the closing direction supported and with the inner synchronizer ring 91a respectively. 91b rotatably connected, embrace this the intermediate ring 92a respectively. 92b from both sides concurrently and frictionally, ie double acting, so that a rotational power can be transmitted or braked by friction. For safe release of the inner synchronizer ring 91a respectively. 91b when opening the clutch or the brake is the inner synchronizer ring 91a respectively. 91b in the recess in the gear wheel 98a respectively. 98b biased in the opening direction, so that at the latest when retraction of the inner synchronizer ring 91a respectively. 91b through the ring pressure piece 71a respectively. 71b the intermediate ring 92a respectively. 92b from the outer synchronizer ring 90a respectively. 90b can solve.

The opening and closing operation of the clutch or the brake and the change between the first and the second switching state otherwise takes place as in the 5 illustrated embodiment.

Claims (7)

Auxiliary gearbox for auxiliary units in vehicles, With - one single-stage planetary gear, which has a sun gear, a planetary gears planet and a ring gear contains, and its sun gear with a driven or drive side shaft coaxial and rotatable connected or connected, - one Belt ring connected to the planet carrier coaxial and rotationally fixed is - one Clutch, which is switchable and driveable between the planet carrier and the sun wheel is arranged, A fixed frame part, and - one Brake, which is shiftable and driveable between the ring gear and the frame part is arranged. Auxiliary transmission according to claim 1, characterized that exactly a gearbox is provided, which is at least partially formed by the belt ring is. Auxiliary transmission according to claim 1 or 2, characterized that one, for a belt usable effective portion of the belt rim at least an element from the group planetary gear set, clutch and brake axially complete and / or At least two elements from this group partially covered axially. Auxiliary transmission according to claim 1, characterized that the clutch is a multi-plate clutch or a simple or Double-acting cone clutch is and / or the brake is a multi-plate clutch or a single or double acting cone brake. Auxiliary transmission according to claim 1, characterized that the coupling is form-fitting acts and has a synchronization device and / or the Brake positive locking acts and has a synchronization device. Auxiliary transmission according to claim 5, characterized in that in that the synchronization device has a blocking synchronization device is. Drive arrangement of a fly gear after a claims 1 to 6, characterized in that - the sun gear coaxial with a drive shaft of precisely one driven accessory rotatably connected is, or - the Sun gear coaxial with an output shaft of exactly one abortive Auxiliary unit is rotatably connected, or - the sun bath coaxial with an output shaft of a transmission or an engine rotatably connected, with the belt ring over exactly one belt with each to drive shafts of a group to be driven ancillaries arranged pulleys is connectable.