DE102013203768A1 - Gear unit and differential device with the gear unit - Google Patents

Abstract

The invention has for its object to find an alternative for known transmission assemblies to produce a rotary or pivotal movement a linear movement. For this purpose, a transmission assembly (1) is proposed, with an axial lifting device (16), wherein the axial lifting device (16) is designed to generate an axial stroke based on the relative rotation between a first and a second transmission component (9, 4), wherein the axial lifting device ( 16) has at least one ramp disc (21a, b) and a ramp structure, wherein the axial movement is generated by the relative rotation of the ramp disc (21a, b) to the ramp structure (31a, b, 32a, b, 40), wherein the ramp structure (31a , b, 32a, b, 40) includes ramps (31a, b, 32a, b) disposed on at least one spoke (25a, b, c), the ramps (31a, b, 32a, b) being in The direction of rotation to the main axis of rotation (2) increase or decrease, at least three such spokes (25 a, b, c) are provided.

Description

The invention relates to a transmission assembly having a first transmission component and a second transmission component, wherein the first and the second transmission component are coupled in the direction of rotation about a main axis of rotation with each other such that a limited relative rotation between the first and the second transmission component is made possible, with an axial lifting wherein the Axialhubeinrichtung is adapted to generate an axial stroke based on the relative rotation between the first and the second transmission component, wherein the Axialhubeinrichtung has at least one ramp disc, wherein the ramp disc rotationally fixed to the first transmission component are arranged, wherein the Axialhubeinrichtung has a ramp structure the ramp structure is arranged rotationally fixed relative to the second transmission component, and wherein in the relative rotation between the first and the second transmission component by the relative rotation of the ramp The ramp structure is arranged on at least one radially extending spoke of the second transmission component, ramps of the ramp structure being arranged on the at least one spoke, the ramps increasing or decreasing in the direction of rotation relative to the main axis of rotation.

Modules in transmissions can take on a variety of tasks depending on the application. In many applications, it is necessary to provide in gear a means that converts a rotary or pivoting motion into a linear motion.

For example, from the document DE 411 29 06 C2 , which is probably the closest prior art, a self-locking vehicle differential known. The vehicle differential has a differential carrier in which a compensation gear is rotatably arranged on a compensation axis. Further, the vehicle differential on two balancing body, which are also arranged in the differential cage and via which a drive torque is introduced into the differential cage, wherein the drive torque is transmitted via the compensation body to the compensation axis. The compensating bodies are arranged displaceably in the axial direction in the differential cage, wherein the compensating axis is positioned between the compensating bodies. Between the compensation axis and the compensation bodies, a ramp is arranged, which causes the compensation body are moved in the axial direction in response to the height of the drive torque at an initiation of the drive torque and convert in this way a rotational movement in a linear movement.

Field of the invention

The invention has for its object to find an alternative to known transmission assemblies to produce a rotary or pivotal movement linear motion.

This object is achieved by a transmission assembly having the features of claim 1 and by a differential device having the features of claim 9. Preferred or advantageous embodiments of the invention will become apparent from the dependent claims, the following description and the accompanying drawings.

In the context of the invention, a transmission assembly is proposed, which is designed in particular for integration in a vehicle, in particular in a passenger car, truck, bus or the like. In particular, the transmission assembly is integrated with a drive train of the vehicle and serves to guide or relay a drive torque from one or more engines of the vehicle to driven wheels of the vehicle.

The transmission assembly includes first and second transmission components, wherein both transmission components are configured and / or arranged to rotate or pivot a common main axis of rotation of the transmission assembly. It should be emphasized that the two transmission components are not rigidly or rigidly coupled with each other, but are connected with each other with a pickup. The coupling is in particular designed such that the first and the second transmission components are so entrained about one or the main axis of rotation that the first and the second transmission component in the direction of rotation about the main axis of rotation take each other and at the same time a limited relative rotation between the transmission components is possible. In particular, the first transmission component relative to the second transmission component in the direction of rotation, in particular exclusively in the direction of rotation, floating or sliding mounted. In particular, the limited relative rotation is less than 10 degrees, in particular less than 5 degrees in the circumferential direction about the main axis of rotation.

Furthermore, the transmission assembly comprises an axial lifting device, which generates an axial stroke based on the relative rotation between the transmission components. Thus, the Axialhubeinrichtung forms a transducer between a rotational movement to a linear movement. Functionally considered, the axial stroke is generated as a function of the relative rotation between the transmission components.

The Axialhubeinrichtung has at least one, preferably two ramp discs, which are preferably arranged in the axial direction next to or on both sides of the first transmission component. The at least one ramp disc is rotationally fixed to the first transmission component, but arranged axially displaceable therewith. In particular, the axial stroke is generated by the displacement of the at least one ramp disc in the axial direction.

Further, the Axialhubeinrichtung has a ramp structure, wherein the ramp structure on the second transmission component, in particular rotatably or takedown, is arranged. In the relative rotation between the first and the second gear component thus takes place a relative rotation of the at least one ramp disc to the ramp structure, which is generated by the latter relative rotation of the Axialhub between the at least one ramp disc and the ramp structure.

The second transmission component has at least one radially extending spoke, in particular strut, wherein ramps of the ramp structure are arranged on the at least one spoke. A spoke designates in particular a connecting portion, which can occupy a maximum of half the diameter of the second gear component. In particular, no later than the main axis of rotation or a hub of the second gear component forms a separation between two spokes. For example, the spokes may meet in the region of the main axis of rotation and / or are distributed uniformly in the direction of rotation about the main axis of rotation. The ramps are designed so that they increase or decrease in the direction of rotation about the main axis of rotation.

In the context of the invention, it is proposed that the second transmission component has at least three or more such spokes, that is to say spokes, which each carry a part of the ramp structure. In particular, the three spokes are of identical design, in particular with regard to the ramp structure.

It is a consideration of the invention that so far the use of spokes for axial actuators was significantly limited to the technical context with the double use as a compensation axis for a differential gear in a differential. By extending the number of spokes of two spokes running in alignment, as is known from the prior art, to at least three spokes, this usual way of thinking is resolved and a transmission assembly proposed which can unconditionally take full advantage of a "spoke actuator" , So the advantage is to see that the spokes can be built very solid and wear in this way are. Further advantages result from the fact that due to the radially extending interaction region between the ramps of the ramp structure and the ramp discs of the outer radius of the Axialhubeinrichtung can be kept very low.

In a preferred embodiment of the invention, a maximum of six such spokes are used. In this embodiment, the inventive idea is underlined to achieve the Axialhub by the interaction of individual elements with the at least one ramp disc.

In an advantageous embodiment of the invention, the ramps extend in the radial direction over more than 30%, preferably more than 40% of the length between an outer diameter of the ramps and the main axis of rotation. This embodiment emphasizes that the axial lifting device is controlled by the use of areas with a long radial extent and not by the use of long areas in the direction of rotation.

In particular, it is provided that free spaces of the second transmission component are arranged between the spokes. Specifically, in some embodiments, the circumferential oriented flanks of the spokes may support the ramps. In this embodiment, the weight of the second transmission component can be significantly reduced.

In a possible embodiment of the invention, the second transmission component is formed with integrated spokes, wherein the ramps are formed on or in the spokes. This embodiment is particularly inexpensive to manufacture.

In a further possible embodiment of the invention, the spokes are designed as an insert component in the second transmission component. Particularly preferably, the ramps in this embodiment are integrally formed on the insert component. This embodiment is based on the consideration that different materials can be used for the area for introducing an input torque into the second transmission component and for the area of the ramps. Due to the mix of materials, suitable metals or hardening can be used.

In a further embodiment of the invention, the second transmission component is formed with preferably integrated spokes, wherein the ramps are realized as intermediate components, in particular as inlays, on the spokes. In this embodiment, the second transmission component be supported over the spokes and executed in this way constructive very stiff. In order to still be able to realize a material mix between the ramps and the spokes or the second gear component, it is preferred that the ramps are realized as intermediate components and are placed and secured on the spokes.

In a further embodiment, it is provided that between the spokes and the ramp discs, a rolling bearing assembly is arranged, wherein the rolling bearing assembly rolling elements, in particular rollers, in particular cylindrical rollers, which are oriented parallel to the spokes and in the spokes, for example via the ramps in Reference to the direction of rotation are recorded positively, so that they can not slip out in the direction of rotation, but are carried along with the spokes. Thus, the rolling elements, in particular the rollers, together with the spokes form the ramp structure. This embodiment has the advantage that the rolling elements can rotate relative to the spokes and relative to the ramp discs, so that the friction and thus the wear in the Axialhubeinrichtung is minimized. The rolling bearing arrangement preferably has a cage. In particular, the rolling bearing assembly has a number of spokes corresponding number of rolling elements in the direction of rotation.

Another object of the invention relates to a differential device for a vehicle with the transmission assembly, as described above. The differential device is in particular designed as a transverse differential gear, which distributes an input torque of one or more motors in a normal straight ahead driving of the vehicle 50:50 on the wheels of a common driven axle.

The differential device comprises, as the first transmission component, a planet carrier and, as second transmission components, an input member which is designed to introduce one or the input torque into the differential device. The input torque is - as already explained - the torque, in particular torque, of the one or more engines of the vehicle. The input member particularly preferably comprises a mechanical interface surrounding a main axis of rotation of the differential device, wherein the mechanical interface is particularly preferably designed as a circumferential spur gear toothing or as a revolving crown wheel.

The differential device comprises a first planetary gearset and a second planetary gearset, wherein the planetary gears are rotatably mounted on the planet carrier. For example, the planet gears are mounted on the planet carrier via bolts. Particularly preferably, the planet carrier is constructed from two housing halves, wherein the bolts connect the housing halves with each other. The planetary gears are designed in particular as spur gears, ie peripherally toothed gears. The differential device comprises a first and a second sun gear, wherein each of the sun gears can be coupled or coupled to output shafts of the differential device. The output shafts are optionally rotationally fixed or drivingly connected via a further gear stage with the wheels of the common axis. In particular, the output shafts define the main axis of rotation of the differential device and the transmission assembly. Particularly preferably, in operation, the input member rotates together with the planet carrier about the main axis of rotation of the differential device.

The differential device comprises two coupling devices, wherein the coupling devices are each designed to frictionally couple one of the sun gears with the planet carrier. The coupling devices are thus each designed to increase a coefficient of friction between the respective sun gear and the planet carrier upon actuation of the coupling devices. By increasing the coefficient of friction at the same time the locking value of the differential device is increased. The actuation of the coupling devices takes place by the Axialhubeinrichtung.

In one possible constructive embodiment, it is provided that the planet gears of the first planetary gear set mesh with the first sun gear and the planetary gears of the second planetary gear set with the second sun gear and that the planet gears of the two planetary gear sets mesh in pairs. In other words, a planetary gear of the first planetary gearset meshes with the first sun gear on the one hand and with an adjacent planetary gear of the second planetary gearset on the other hand, with the planetary gear of the second planetary gear meshing in turn with the second sun gear. In this way, a very simple compensation mechanism and at the same time a simple Sperrwertanpassung implemented. In particular, in this way it is very simple to constructively design the differential device in such a way that in normal operation the drive torque 50:50-that is, uniformly-is distributed to both sun gears and thus output shafts. Such ausgestaltetes Stirnradplanetengetriebe is structurally simple and at the same time has enough usable space for the integration of Axialhubeinrichtung. Characterized in that the support portion rotatably connected to the planet carrier or forms an integral part thereof, it is achieved that the coupling means each one of the sun gears frictionally engaged with the planet carrier or so rotatably coupled components. In order to increase the blocking value, the sun gears are thus connected to the planet carrier.

It is particularly preferred that the Axialhubeinrichtung is disposed between the sun gears and that the Axialhub is transmitted via an axial displacement of the sun gears on the coupling device. The space between the sun gears can be used in particular because the Axialhubeinrichtung exploits the length of the ramps in the radial direction and because the two sun gears due to the coupling with the first and the second planetary gear set may be axially symmetrical or at least in the middle area similar. In particular, none of the sun gears must reach into the axial region of the other sun gear. The Axialhubeinrichtung is preferably at least partially arranged in relation to the radial extent between the sun gears. Particularly preferably, this is positioned coaxially to the main axis of rotation. The axial displacement of the sun gears is preferably realized via a displacement of one of the sun gears of at least 0.2 millimeters, preferably at least 0.4 millimeters. The coupling between the sun gears and the output shafts is in particular designed so that this axial stroke of the sun gears can optionally be tolerated or compensated for by a relative displacement in the axial direction between the sun gear and the output shaft.

In a preferred embodiment of the invention, the differential device has a centering device for relative centering of the input member and planet carrier, wherein the centering device is arranged radially outward to the Axialhubeinrichtung. After preferably the Axialhubeinrichtung is arranged in the radially inner region with respect to the main axis of rotation, input member and planet carrier to each other allow a relative rotation, the radially arranged outside of the Axialhubeinrichtung centering ensure that a rotation axis of the input member is always identical to a rotation axis of the planet carrier and both axes of rotation coaxially stay to the main axis of rotation.

In a preferred structural embodiment of the invention, the centering device has a plurality of centering bodies distributed in the circumferential direction, in particular bolts, which are fixed on one of the centering and extending in the direction of elongated holes in the other centering, wherein the centering in the radial direction through the slots positively guided, in particular forced. Preferably, the centering device has at least three centering, so that the coaxiality of the axes of rotation is ensured by the radial guidance of the elongated holes. In contrast, the centering bodies are arranged in the direction of rotation about the main axis of rotation slidably in the oblong holes, so that the relative rotation described above is possible.

In a preferred embodiment of the invention, the Axialhubeinrichtung is designed as Endbegrenzung the relative rotation in the direction of rotation, so that the centering device, in particular the slots are dimensioned so that the centering device is realized in the endanschlagfrei normal operation of the differential device. In particular, the centering are always spaced, so in particular not fitting, to the end portions of the slots in the circumferential direction.

In a preferred structural embodiment, the Axialhubeinrichtung on a disc holder, which receives the ramp discs in the circumferential direction, for example by means of a circumferential toothing in the disc holder and a counter-toothing in the ramp discs, positively and axially displaceable. In the embodiment with the circumferential toothing, the teeth extend in the axial direction, so that the axial displacement is possible.

In a preferred embodiment of the invention, the Axialhubeinrichtung, in particular the ramp discs and the ramp structure is formed so that there is a different Axialhubsteigung in one direction and in the opposite direction of the relative rotation. Under the Axialhubsteigung the quotient of stroke in millimeters divided by relative rotation in degrees is considered. This refinement is based on the consideration that, for example, when driving forward the vehicle, ie the introduction of the drive torque in one direction of rotation, another blocking value should be set as a function of the drive torque than when the vehicle is reversed, ie when the drive torque is introduced in the opposite direction , Alternatively, different pitches of the axial lift device for pull and push operation, e.g. be selected for acceleration and braking. Compared to the known from the prior art and in principle also possible embodiment that the ramp structure is arranged continuously in the circumferential direction, very long ramps can be generated by the ramp structure on the spokes in the radial direction, which allow to generate a high axial force ,

Further features, advantages and effects of the invention will become apparent from the following description of preferred embodiments of the invention. Showing:

1a , b is a plan view in the axial direction or in the radial direction of a differential device as a first embodiment of the invention;

2 a schematic three-dimensional representation of a section AA in the 1 ;

3 a schematic two-dimensional representation in the sectional plane BB of 1a , b;

4 a schematic two-dimensional representation in the sectional plane EE in the 1a , b;

5 a first alternative embodiment for an input gear in the differential device in the preceding figures;

6 a second alternative for the input gear in the differential device of 1 to 4 ;

7 a three-dimensional representation of the input gear in the 6 ;

8th a section through the input gear in the 6 ;

9 a further alternative embodiment for the Axialhubeinrichtung in the differential device in the preceding figures in exploded view;

10 a two-dimensional representation in the sectional plane BB in the 1a , b with the embodiment according to the 9 ;

11 a two-dimensional representation in enlargement of the sectional plane EE in the 1a , b with the embodiment according to the 9 and 10 ,

The 1a and 1b each show a differential device 1 in an axial plan view or in a radial plan view with respect to a main axis of rotation 2 the differential device 1 as an embodiment of the invention.

The differential device 1 is used to distribute an input torque at an input E to two outputs A. The outputs A is associated with a respective output shaft, not shown, which are drivingly coupled to wheels of a vehicle. The differential device 1 is formed as a transverse differential, which distributes the input torque at the input E halfway to the outputs A, for example, when driving straight ahead of the vehicle.

The differential device 1 is designed as a Stirnradplanetengetriebe, the input E as an input member one, the main axis of rotation 2 circumferential spur toothing 3 having. Upon application of the differential device 1 with the input torque is the illustrated differential device 1 completely around the main axis of rotation 2 rotates.

In the 1a , b are various cutting lines indicated, the sectional planes, which are shown in the following figures.

That's how it shows 2 the sectional plane AA in a schematic three-dimensional representation. As can be seen from the illustration, the input E is an input wheel 4 formed, which circumferentially the spur toothing 3 wearing.

The differential device 1 has a housing 5 on, which consists of housing halves 6a , b is constructed, being between the housing halves 6a , b the input wheel 4 is arranged. The housing 5 is about storage facilities 7a , B mounted rotatably relative to a surrounding structure in the vehicle. The storage facilities 7a , b are designed as ball bearings in radial design. The housing halves 6a , B are realized as forming parts.

The housing halves 6a , b are about bolts 8a rigidly coupled with each other and form a planet carrier 9 for the Stirnradplanetengetriebe. The planet carrier 9 forms a first transmission component and the input gear 4 a second transmission component of Stirnradplanetengetriebes.

How better off 3 reveals a two-dimensional sectional view of the differential device 1 in the sectional plane BB points are on the bolt 8a , b planet gears 10a a first planetary gear set and planet gears 10b a second planetary gear set. The planet wheels 10a , b are arranged in three groups, wherein in each group one of the planet gears 10a with a planetary gear 10b combs.

In conjunction with the 2 and the 4 it can be seen that the outputs A of the differential device 1 as sun wheels 11a , b are realized, with the first sun gear 11a with a planetary gear 10a and the second sun wheel 11b with the other planetary gear 10b combs. In this way, a differential gear is realized, which is a on the planet carrier 9 guided moment on the sun gears 11a , b distributed. planetary gears 10a , b and sun gears 11a , B are each formed as spur gears. The sun wheels 11a , b have mounts 12a , b in the axial direction to the main axis of rotation 2 running teeth, so the output shafts in the sun gears 11a , B can be inserted in the axial direction.

The differential device 1 has two coupling devices 13a , b on, which each have a first set of slats 14aa and a second set of laminations 14ab respectively 14ba and 14bb include. The slat set 14aa and 14ba is with the case 5 and thus with the planet carrier 9 rotatably coupled, but slidable in the axial direction. In contrast, the lamella set 14ab respectively 14bb with the sun wheel 11a respectively 11b in the direction of rotation about the main axis of rotation 2 rotatably coupled and also axially displaceable. Thus, each coupling device 13a , b a lamella set 14aa , ba, with the case 5 and a blade set 14ab , bb on that with the sun gear 11a rotatably coupled.

On the axially outer side of the sliding chamber of the disk packs 14aa , off, ba, bb by a shoulder 15a respectively 15b limited. On the axially inner side of the sliding chamber of the disk packs 14aa , ab, ba, bb by direct or indirect contact with the first sun gear 11a or to the second sun gear 11b limited. The first sun wheel 11a and the second sun wheel 11b are each formed axially displaceable, wherein by a displacement of the sun gears 11a , B to an axial stroke to axially outside the disk packs 14aa , ab, ba, bb be squeezed, so the sun gears 11a , b in frictional coupling with the housing 5 or the housing halves 6a , b resp. the planet carrier 9 come.

Through the coupling devices 13a , b it is possible to have a locking value of the differential device 1 adjust. It is true that with a locking value of 0%, the coupling devices 13a , b are open and at a locking value of 100%, the coupling devices 13a , b are closed, so that the over the coupling devices 13a , b connected pairs sun wheel 11a and housing halves 6a respectively 11b and 6b each the same angular velocity about the main axis of rotation 2 exhibit. Depending on the axial stroke of the sun gears 11a , b the lock value can be set between 0% and 100%. It is also possible for the blocking value to be adjustable only in a restricted range, for example between 10% and 90% etc. By integrating the coupling devices 13a , b becomes the differential device 1 to a so-called limited slip differential.

The axial stroke of the sun gears 11a , b is by a Axialhubeinrichtung 16 implemented, which in a space between the sun gears 11a , b is arranged. The Axialhubeinrichtung 16 is designed to change its axial width and to produce in this way the Axialhub. Functionally, the axial stroke is due to a relative rotation between input gear 4 and planet carrier 9 initiated, wherein the Axialhubeinrichtung 16 converts this rotational movement into a linear movement.

It is remarkable that the planet carrier 9 and the input wheel 4 are not rigidly coupled together in the direction of rotation, but can rotate by a few degrees, for example less than 20 degrees, in particular less than 10 degrees, in particular less than 3 degrees, relative to one another. This relative rotation is achieved by the planet carrier 9 and the input wheel 4 not rigidly bolted together, but via a centering device 17 coupled to each other, wherein the centering device 17 allows that planet carrier 9 and input wheel 4 in the direction of rotation about the main axis of rotation 2 can be rotated to each other, but at the same time with respect to the main axis of rotation 2 remain centered.

As best of the 3 in conjunction with the 2 can be seen, includes the centering device 17 three distributed in the direction of rotation centering in the form of bolts 18 , which the two housing halves 6a , b connect with each other. In the entrance wheel 4 are longholes 19 introduced, which in the radial direction, the bolts 18 hold positively, but a shift or pivoting of the bolts 18 in the direction of rotation about the main axis of rotation 2 enable. In this way, one degree of freedom for the relative rotation between planet carrier 9 and input wheel 4 created. Around the interior of the differential device 1 seal is between the input wheel 4 and the housing 5 on each side an O-ring 20 inserted.

The Axialhubeinrichtung 16 has two ramp discs 21a , b on, which are coaxial and concentric with the main axis of rotation 2 are arranged. The ramp discs 21a , B show in axial plan view according to the 3 a circular coarse mold with an external toothing on and are of a disc holder 22 added. The disc holder 22 also comprises on its inner circumference a toothing which is complementary to the toothing of the ramp discs 21a , b is formed so that these in the disc holder 22 guided axially displaceable, but are positively secured in the direction of rotation against rotation. The disc holder 22 points - as it is from the 6 gives - three connection arms 23a , b, c, over which these on the housing 5 is fixed. For example, the connecting arms 23a , b, c through the bolts 8a or 8b be penetrated so that the disc holder 22 on the housing 5 is fixed.

The entrance wheel 4 is with a spoke section 24 rotatably connected, wherein the spoke portion 24 three spokes 25a , b, c, which is rigid with the input gear 4 are connected. In the illustrated embodiment of the previous figures is the spoke portion 24 formed as a separate component.

The 4 shows a sectional view of the differential device 1 in the plane EE, where it can be seen that the ramp discs 21a and 21b for each of the spokes 25a , b, c together a spokes receptacle 28 form, in which the spokes 25a , b, c are respectively inserted. For this purpose, each of the ramp discs 21a , B a receiving structure which the spoke portion 24 facing and which in the present embodiment as three grooves 27a , b, c on each of the ramp discs 21a , b are formed, in which the spokes 25a , b, c are guided.

In a relative rotation between planet carrier 9 and input wheel 4 become the spoke section in the same way 24 relative to the ramp discs 21a , b twisted. How now from the 4 results is the spoke pickup 28 Tapered in the end areas in the circumferential direction, so that on each ramp disc 21a , b a ramp 29a , b in a first direction of rotation with a ramp angle α and a ramp 30a , b in the opposite direction with a ramp angle β, where α can be equal to or different than β, as will be explained below. The spoke 25a , b, c has ramps on both sides in the same way 31a , b respectively 32a , b on. In a relative twist between the spoke section 24 and the ramp discs 21a , b will be the spokes 25a , b, c against the end portions of the spoke receiver 28 pressed and pressed due to the ramp structure of the spokes 25a , b, c the ramp discs 21a , b apart in the axial direction. In this way, a relative rotation in the form of a rotational movement of the Axialhubeinrichtung 14 converted into a linear axial stroke in the axial direction.

The overlapping in axial plan length of the ramps 29a , b, 30a , b, 31a , b, 32a , b on the ramp discs 21a , b, respectively on the spokes 25a , b, c, which interact in the relative rotation amount to more than 40%, in particular more than 50% of the outer diameter R of the ramps 29a , b, 30a , b, 31a , b, 32a , b, so that sufficient stability of the Axialhubeinrichtung 16 is given against wear.

With their free tops 33a , b press the ramp discs 21a , b against the sun gears 11a , B, so that they are also displaced by the Axialhub in the axial direction and the coupling means 13a Press b. Depending on the input torque introduced via the input level 4 Thus, the coupling devices 13a , b, so that there is a torque-dependent locking effect in the differential device 1 results.

The different design of the ramp angles α and β can be advantageously used to achieve a different Sperrwertverlauf depending on the input torque introduced, in particular in the push or close operation or, for example, with respect to a forward drive and a reverse drive of the vehicle.

Returning to the 2 it can be seen that the differential device 1 an adjustment device 45 having, which as a screw 46 is formed, which is coaxial with the main axis of rotation 2 is arranged and in the housing 5 is screwed. The free end of the screw sleeve 46 make the shoulder 15a so that these on the coupling device 13a between the lamella set 14aa or 14ab is applied. By the adjustment 45 can apply a biasing force to the coupling devices 13a , b, so that a basic value or offset value for the blocking value by screwing or unscrewing the screw 46 can be adjusted. For the differential device 1 is only a single screw 46 provided because the biasing force on the sliding sun gears 11a , B to the lying on the opposite side coupling devices 13b is weitergeleiltet, so that by a one-sided application of the biasing force both coupling devices 13a , b be preloaded.

The 5 shows an alternative embodiment of the input gear 4 the previous figures, wherein the spoke portion 24 now an integral part of the input gear 4 forms. This variant is characterized by a cheap production. The representation in the 5 can be seen that the ramps 31a such as 32a in the radial direction with respect to the main axis of rotation 2 extend over a wide range, in particular over a length greater than 1 cm or 2 cm. The ramps 31b . 32b are formed in the same way.

In the 6 is the input wheel 4 with the spoke section 24 one-piece, the ramps 31a , b, 32a , b, however, sit on intermediate components in the form of hardened inlays 34 that have threaded pins 35 at the entrance wheel 4 are attached. In this embodiment, the input wheel 4 made of a lightweight material, such as EN AL 7075 F52 be made. The inlays 34 On the other hand, they can be made of a hardened material, such as 100Cr6. Through the use of lightweight materials for the input wheel 4 can save more than 20% of weight, especially about 50% be achieved with respect to the embodiment in the preceding figure.

In the 7 is the drive wheel 4 of the 6 without inlays 34 shown. It can be seen that the input wheel 4 rough ramps 36a , b as well 37a , b which is parallel to the ramps 31a , b or 32a , b are formed. There are also holes 38 for holding the pins 35 provided for fixing the inlays.

In the 8th is a detail view of the input gear 4 the previous figures in the sectional plane AA in the 6 shown again, where it can be seen again that the ramps 31a , Federation 32a , b parallel to the coarse lamps 36a , Federation 37a , b are aligned. In this embodiment, the ramps form 31a , b, 32 a, b on the spokes 25a , b, c a radial groove. The ramps 29a , b, 30a , b on the ramp discs 21a , b, however, are formed as webs. The inlays 34 can be made very thin, so this essentially just a protective layer for the coarse lamps 36a , and 37a , form.

In the 9 is in a schematic three-dimensional exploded view, the Axialhubeinrichtung 16 shown in a further variant. However, the basic operation of the Axialhubeinrichtung 16 also be explained for the alternative embodiments with reference to this illustration. In the illustration is the disc holder 22 to see how this can also be used in the previous embodiments. Also the ramp discs 21a , B are shown in individual representation, on the one hand, the circumferential toothing, which in a corresponding counter-toothing of the disc holder 22 engages, can be seen. Furthermore, it can be clearly seen that the ramp discs 21a , b on both sides of the input wheel 4 are arranged. At the rear ramp disc 21b are the grooves 27a to clearly see b, c, which extend in the radial direction. The spoke section 24 of the input gear 4 is formed as in the previous figures.

The in the 9 illustrated alternative embodiment differs in that between the input gear 4 and the ramp discs 21a , b each have a rolling element arrangement 39a , B is arranged, which each have three trained as rollers rolling elements 40 carries, wherein the rolling elements 40 parallel extending and in axial projection congruent to the spokes 25a , b or grooves 27a , b, c are arranged. The rolling elements 40 are in a rolling element cage 41 absorbed, so that the rolling elements 40 can rotate freely.

In the 10 is similar to the one in the 3 the alternative of execution in the 9 showing, on the one hand, that the disc holder 22 over the bolts 8b is attached. On the other hand it can be seen that the rolling elements 40 in radially extending grooves 42 a, b, c of the spoke section 24 or the spokes 25 a, b, c are inserted, which are the ramps 31a , b, or 32a , b (cf. 11 ) form.

In the 11 is the Axialhubeinrichtung 16 shown in a section, wherein it can be seen that the rolling elements 40 or the rolling element arrangement 39a , b together with the grooves 42a , b, c form the ramp structure and being on the ramp discs 21a , b again ramps 29a , b or 30a , b are arranged. This embodiment has the advantage that in a relative rotation between planet carrier 9 and input wheel 4 the relative displacement between ramp discs 21a , b and spoke section 24 over the rolling elements 40 is stored so that the friction is significantly reduced. In this embodiment, the rolling elements form 40 together with the grooves 42a , b, c the ramp structure of the input gear 4 , Also in this embodiment, the ramp slope may be formed differently in one direction of rotation than in the other direction of rotation.

LIST OF REFERENCE NUMBERS

1

 differential device

2

 Main axis of rotation

3

 spur gearing

4

 input gear

5

 casing

6a, b

 housing halves

7a, b

 Storage facilities (ball bearings)

8a, b

 bolt

9

 planet carrier

10a, b

 planetary gears

11a, b

 sun gears

12a, b

 receptacles

13a, b

 coupling devices

14aa, ba

plate sets

14ab, bb

 plate sets

15a, b

 shoulder

16

 Axialhubeinrichtung

17

 centering

18

 bolts

19

 slots

20

 O-ring

21a, b

 ramp discs

22

 disc holder

23a, b, c

 terminal arms

24

 spoke portion

25a, b, c

 spoke

27a, b, c

 groove

28

 spoke receiving

29a, b

 Ramp ramp ramps

30a, b

 Ramp ramp ramps

31a, b

 Ramps of spokes

32a, b

 Ramps of spokes

33a, b

 Ramp discs Tops

34

 inlays

35

 screws

36a, b

 rough ramps

37a, b

 rough ramps

39a, b

 rolling body

40

 rolling elements

41

 Rolling Element

42a, b, c

 groove

45

 adjustment

46

 threaded

A

 outputs

e

 entrance

R

 outer diameter

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 4112906 C2 [0003]

Cited non-patent literature

• EN AL 7075 F52 [0068]

Claims (10)

Transmission assembly ( 1 ) with a first transmission component ( 9 ) and with a second transmission component ( 4 ), wherein the first and second transmission components ( 9 . 4 ) in the direction of rotation about a main axis of rotation ( 2 ) are coupled with each other in such a way that a limited relative rotation between the first and the second transmission component ( 9 . 4 ) is provided with an Axialhubeinrichtung ( 16 ), wherein the Axialhubeinrichtung ( 16 ) is formed, based on the relative rotation between the first and the second transmission component ( 9 . 4 ) to produce an axial stroke, wherein the Axialhubeinrichtung ( 16 ) at least one ramp disc ( 21a , b), wherein the ramp disc ( 21a , b) rotationally fixed to the first transmission component ( 9 ) are arranged, wherein the Axialhubeinrichtung ( 16 ) has a ramp structure, the ramp structure ( 31a , b, 32a , b, 40 ) on the second transmission component ( 4 ), and wherein in the relative rotation between the first and the second transmission component ( 9 . 4 ) by the relative rotation of the ramp disc ( 21a , b) to the ramp structure ( 31a , b, 32a , b, 40 ) the axial stroke is generated, wherein the ramp structure ( 31a , b, 32a , b, 40 ) on at least one radially extending spoke ( 25a , b, c) of the second transmission component ( 4 ), wherein the ramp structure ( 31a , b, 32a , b, 40 ) Ramps ( 31a , b, 32a , b) on the at least one spoke ( 25a , b, c) are arranged, the ramps ( 31a , b, 32a , b) in the direction of rotation relative to the main axis of rotation ( 2 ) increase or decrease, characterized in that the second transmission component ( 4 ) at least three such spokes ( 25a , b, c). Transmission assembly ( 1 ) according to claim 1, characterized in that the second transmission component ( 4 ) a maximum of six such spokes ( 25a , b, c). Transmission assembly ( 1 ) according to claim 1 or 2, characterized in that the ramps ( 31a , b, 32a , b) in the radial direction over more than 30%, preferably 40% of the distance between the outer radius (R) of the ramps ( 31a , b, 32a , b) and the main axis of rotation ( 2 ). Transmission assembly ( 1 ) according to one of the preceding claims, characterized in that between the spokes ( 25a , b, c) free spaces of the second transmission component ( 4 ) are arranged. Transmission assembly ( 1 ) according to one of the preceding claims, characterized in that the spokes ( 25a , b, c) an integral part of the second transmission component ( 4 ) form. Transmission assembly ( 1 ) according to one of the preceding claims 1 to 4, characterized in that the spokes ( 25a , b, c) as an insert component in the second transmission component ( 4 ) are formed. Transmission assembly ( 1 ) according to one of the preceding claims, characterized in that between the spokes ( 25a , b, c) and the at least one ramp disc ( 21a , b, c) intermediate components ( 34 . 40 ), wherein the intermediate components, the ramp structure, in particular the ramps ( 31a , b, 32a , b) form. Transmission assembly ( 1 ) according to one of the preceding claims, characterized in that between the spokes ( 25a , b, c) and the at least one ramp disc ( 21a , b, c) a rolling bearing arrangement ( 39a , b) with rolling elements ( 40 ) is arranged as intermediate components, the relative rotation between the spokes ( 25a , b, c) and the at least one ramp disc ( 21a , b), wherein the ramp structure the rolling elements ( 40 ) and the spokes ( 25a , b, c). Differential device ( 1 ) for a vehicle, characterized by a transmission assembly ( 1 ) according to any one of the preceding claims, wherein the second transmission component acts as an input member ( 4 ) for introducing an input torque into the differential device ( 1 ) and the first transmission component as a planet carrier ( 9 ), wherein the planet carrier ( 9 ) with the input member ( 4 ) is coupled, so that the input torque at least partially on the planet carrier ( 9 ) is transferable, wherein the planet carrier ( 9 ) a first planetary gear set with planetary gears ( 10a ) and a second planetary gear set with planetary gears ( 10b ), with a first and a second sun gear ( 11a , b), each of the sun gears ( 11a , b) with output shafts of the differential device ( 1 ) can be coupled, with two coupling devices ( 13a , b), wherein the coupling devices ( 13a , b) are each formed, one of the sun gears ( 11a , b) frictionally engaged with a support section ( 5 . 6a , b, 9 ) of the coupling device ( 13a , b,), wherein the axial lifting device ( 16 ) is formed, based on the relative rotation between the input member ( 4 ) and the planet carrier ( 9 ) to produce the Axialhub, the coupling devices ( 13a , b) operated. Differential device ( 1 ) according to claim 9, characterized in that the support portion rotatably with the planet carrier ( 9 ) or forms an integral part of it, that the planetary gears ( 10a ) of the first planetary gear set with the first sun gear ( 11a ) and the planetary gears ( 10b ) of the second planetary gear set with the second sun gear ( 11b ) and that the planetary gears ( 10a , b) the two planetary gear sets mesh in pairs.

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