differential gear

Abstract

Differential gear (100, 101, 102, 103, 104, 105, 106), in particular motor vehicle differential gear, for transmitting rotational energy between at least two rotary connections (2, 3, 6), each of which can be coupled to a drive or output shaft, with at least one planetary gear (41, 42) and at least one sun gear or ring gear (21, 31, 61, 71) meshing therewith, wherein at least one planetary gear (41, 42) is designed as a planetary gear shaft (41.0, 42.0), and the planetary gear shaft (41.0, 42.0) is preferably mounted in or on a planetary gear carrier (9) and has, in its axial longitudinal extent, at least three circumferential gear regions (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4) with different diameters, arranged offset from one another and each provided with a circumferential toothing, and a sun gear (21, 31, 61, 71) meshes with each toothed peripheral gear area (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4), and at least two of the sun gears (21, 31) are non-rotatably coupled or directly connected to one of the rotary connections (2, 3), characterized in that a transmission state is provided in which at least two of the sun gears (21, 31, 61, 71) and the at least one planet gear (41, 42) are operatively connected to one another in such a way that the transmission of a rotational force between at least one first rotary connection (2) to at least one second rotary connection (3) takes place without inhibition.

Description

The invention relates to a differential gear, in particular a motor vehicle differential gear, for transmitting rotational energy between at least two rotary connections. The rotary connections can each be coupled to a vehicle-side drive shaft or output shaft, in particular a main drive shaft and two output shafts, in particular to an output shaft per wheel arrangement of a wheel axle.The differential gear comprises at least one planetary gear and at least one sun or ring gear meshing therewith-hereinafter only called sun gear.At least one planetary gear is designed as a planetary gear shaft which is mounted in or on a planetary gear carrier, in particular rotatably, and has in its axial longitudinal extent at least three circumferential gear areas with respectively different diameters which are arranged offset with respect to one another and are each provided with circumferential toothing. The circumferential wheel regions in particular each have a different outer radius.The planetary gear shaft meshes with each toothed circumferential gear region in each case one sun gear, wherein each sun gear is coupled in a rotationally fixed manner to one of the rotary connections or is directly connected to it or comprises such a rotary connection.In the present case, the term motor vehicle is to be understood as meaning not only any land vehicles, such as passenger cars, trucks, industrial trucks, tractors and tracked vehicles, such as tanks and snow caterpillars, but also trailers, add-on parts, in particular those on a tractor, units, machines or devices, such as, for example, robots and / or self-propelled machines.The term "couplable" is understood in the present case to mean any type of connection for transmitting force; for example, a rotary connection can be operatively connected to a shaft via a toothed ring connection or connected in a rotationally fixed manner via a fastening.It has been found that, on the one hand, there is an increased customer demand for more agility and movement capability of a vehicle or of a machine, in particular for better turning and turning capability during maneuvering or parking, and, on the other hand, the manufacturer always strives to reduce the energy consumption of all vehicle or machine components, in particular also components which are predominantly installed in vehicles and can form frictional or rotational resistances per se, such as a customary differential gear, for example. In the field of electric vehicles as they are increasingly occurring nowadays in the field of passenger cars, improvements or initial applications of differential transmissions are also desirable.It is therefore the object of the present invention to provide a differential gear, in particular for motor vehicles and machines, which improves at least one or more of the above-mentioned disadvantages and in particular enables a flexible, agile and energy-saving transmission of force, even with regard to particular driving situations.The invention achieves the stated object by a differential gear having the features of the main claim, by a differential gear having the features of claim 3.According to the invention, in the differential transmission a first transmission state, in particular a freewheel, is provided, in which at least two of the sun gears and the at least one planetary gear shaft are operatively connected to one another in such a way that the transmission of a rotational force between at least one first rotary connection to at least one second rotary connection, in particular between at least one sun gear and at least one planetary gear shaft, takes place substantially free of inhibition. In particular, the force flow between the rotary connection connected to a drive and the two rotary connections connected to an output shaft is substantially free of inhibition.It should be clear that free of inhibition is to be understood as meaning, in particular, an un braked state. Although the usual frictional and resisting forces can occur in this case, there cannot be additionally initiated, for example by means of a device provided for this purpose, inhibition or braking of one of the components of the differential gear mechanism. The wheels connected to one another without any escapement can be rotated relative to one another in particular unimpeded, without a blocking effect or a resistance distributing or blocking the torque.With such a differential gear, a particularly energy-efficient compensation of a force transmission from a main drive shaft connected to a drive, such as a motor, to an output shaft connected to a wheel of an axle is provided. In order to make it possible to compensate for the wheel rotations, in particular when cornering, the differential gear, which is designed specifically in the present case, serves in the manner known per se. In addition, in this type of differential gear, a scaling of the torque processing is possible by increasing the number of planetary axles without enlarging the overall structural body. This is desirable and advantageous inter alia in engine sports, in the commercial vehicle sector or in military vehicles-which is not possible in this way in conventional differentials. In tracked vehicles, it is possible to save a differential, in particular a steering differential or superposition gearing.In this case, it may occur in the mode of operation of the differential gear that, in a situation in which a first vehicle wheel of one axle can be rotated more easily than another second wheel of this axle, the first wheel would spin, for example if the first wheel is located on an ice surface and the second wheel is located on an asphalt. While the first wheel spins, the other second wheel of this axle remains stationary, in particular due to the static friction of the tire, or does not experience any force transmission. In this case, since the differential gear is free of inhibition, the force flow from the drive shaft would therefore be transmitted exclusively to the more readily rotating wheel, while a force transmission to the wheel which is more difficult to rotate is not driven by its own static friction with the asphalt.Furthermore, it should be clear that on the planetary gear shaft-depending on the configuration of the differential gear-also more than three circumferential gear areas provided with circumferential toothing are provided. In an advantageous embodiment, in which the rotation of the planetary gear shaft can be manipulated, five such circumferential gear areas provided with circumferential toothing are provided in particular. It should also be clear that the peripheral wheel regions do not necessarily have to be connected integrally to the planetary wheel shaft; in particular, the wheels forming such peripheral wheel regions can be formed separately and fastened, in particular shrunk-fit, to the planetary wheel shaft. It is thus also possible for one of these wheels provided on the planetary gear shaft and having the peripheral gear region to be arranged at least partially surrounded by the planetary carrier, and for another such wheel to be arranged on a portion of the planetary gear shaft which is arranged outside the planetary carrier and is therefore not surrounded by the latter.Particularly preferably, in the first transmission state, the at least two sun gears and the at least one planetary gear shaft are operatively connected to one another in such a way that a rotation between all sun gears and the at least one planetary gear shaft takes place without inhibition.According to the invention, in a further developed differential gear for transmitting rotational energy between at least three rotary connections, which can each be coupled to a vehicle-side drive shaft or output shaft, in particular a differential gear having the features explained above, it is additionally provided that a manipulation device is provided for manipulating or for changing a relative force transmission, in particular a force transmission to at least one output shaft, in particular directly on this differential gear, wherein the manipulation device is configured to be individually controllable, so that the magnitude of the influence on the force transmission can be individually controlled and / or regulated. As a result, a force flow from an input shaft connected to the differential gear can be distributed or directed individually to two output shafts connected to the differential gear. In this way, in certain driving situations, the rotation of individual wheels of an axle can be actively influenced, in particular braked or driven.The manipulation device is preferably designed as an inhibiting device for inhibiting a transmission of force, in particular a transmission of force to at least one output shaft, wherein the inhibiting device is designed to be individually controllable, so that the size of the reduction in the transmission of force can be individually controlled and / or regulated.In an alternative embodiment, the manipulation device is designed as a drive device for amplifying a force transmission, in particular a force transmission to at least one output shaft, wherein the drive device is designed to be individually controllable, so that the magnitude of the amplification of the force transmission can be individually controlled and / or regulated.It should be clear that the differential gear can also have a combination of a manipulation device designed as an inhibiting device and a manipulation device designed as a drive device, in particular two or more manipulation devices.Preferably, the manipulation device is coupled or connected to the at least one sun wheel, to the at least one planetary gear shaft and / or to the at least one planetary gear carrier directly, or to a shaft connected to this rotary connection in a rotationally fixed manner.The manipulation device is preferably designed as a braking device, as a motor, in particular as an electric motor, and / or as a generator. The brake device can be designed, for example, as a liquid brake, magnetic brake or mechanical brake, in particular as a hydraulic-mechanical brake or magnetic-mechanical brake. The electric motor can be designed in particular as an additional auxiliary motor provided on a vehicle.Particularly preferably, a transmission state is provided, in particular a second transmission state, also called sun gear inhibition state, in which for the transmission of force the at least one planetary gear shaft is operatively connected to at least one sun gear connected to a drive shaft and to at least two sun gears each connected to an output shaft, wherein the transmission of force to at least one of the sun gears connected to an output shaft or to a component connected to this sun gear in a rotationally fixed manner is actively influenced, in particular actively reduced or enlarged, by means of the manipulation device. In other words: The manipulation device is suitable for influencing, in particular for braking or accelerating, the rotation of the at least one sun wheel. The influenceable sun gear is connected to one of the at least two output shafts, so that with this transmission state an active braking or additional acceleration of an individual wheel can take place.This transmission state is particularly useful when cornering. In this case, for example, the wheel on the inside of the curve can be actively braked in order to assist the steering movement of the vehicle into the curve. In particular, when braking an output shaft, the force flow can be transmitted to the other output shaft without additional mechanics, with significantly less energy loss than in a conventional differential. This mode of operation can therefore also be referred to as a semi-locking differential.Alternatively or additionally, the wheel on the outside of the curve can be additionally accelerated. This is to be understood in particular as an additional support relative to the other wheel. As a result, the vehicle can in turn be guided supported by the curve, in particular without deceleration by means of a restraining of the wheel on the inside of the curve. This force transmission state is desirable and advantageous in particular for a sport driving style and / or the motor sport.In a further possibility, both output shafts are simultaneously influenced by means of the manipulation device. As a result, a parking brake can be realized, for example. A parking brake can be achieved even more efficiently by locking the planet carrier. Alternatively, additional torque may be provided for very powerful acceleration.In a further embodiment of the invention, a transmission state is provided, in particular a third and fourth transmission state, also called planetary inhibition or planetary acceleration, in which, for the transmission of force, the at least one planetary gear shaft is operatively connected to at least one sun gear connected to an input shaft, to at least two sun gears each connected to an output shaft and to at least one sun gear directly operatively connected to a manipulation device, wherein the transmission of force to the at least one planetary gear shaft or planetary gear carrier or to a component rotationally fixedly connected to the planetary gear shaft or the planetary gear carrier is actively influenced, in particular actively reduced or enlarged, by means of the manipulation device. In other words: The manipulation device is suitable for influencing, in particular for braking or accelerating, the rotation of the at least one planetary gear shaft or of the at least one planetary gear carrier. The influenceable planetary gear shaft and also the influenceable planetary gear carrier are each operatively connected to one of the at least two output shafts, so that with this transmission state an active braking or additional acceleration of an individual wheel of an axle can likewise take place. It should be noted here that very much less force is required for manipulating the planet gear shaft or the planet gear carrier, in comparison to a manipulation directly at an output. An electric motor which may be applied to at least one planetary gear shaft or at least one planetary gear carrier for this purpose can therefore be embodied to be comparatively much smaller in comparison with embodiments in which the output shaft connected to one of the vehicle wheels is directly manipulated, in order to be able to bring about the same effect.This is again expedient, for example, when cornering. In this case, in the case of a right turn, the wheel on the inside of the curve can be actively braked, for example by braking the planet wheel carrier, in order to assist the steering movement of the vehicle into the right turn. In the case of a left turn, the wheel on the inside of the turn can be actively braked, for example by braking the planetary gear shaft-in particular the same differential gear-in order to assist the steering movement of the vehicle into the left turn. Furthermore, a parking brake can also be realized in turn as a result.Alternatively or additionally, the wheel on the outside of the curve can be additionally accelerated when cornering, such as a left-hand curve, by driving the planetary gear carrier in the aforementioned example. Accordingly, the travel by a right turn can also be assisted by an additional driving of the planetary gear shaft. As a result, the vehicle can in turn be guided supported by the curve, in particular without deceleration by means of a restraining of the wheel on the inside of the curve. This force transmission state is desirable and advantageous in particular for a sport driving style and / or the motor sport.In a further possibility, both the planetary gear shaft and the planetary gear carrier are simultaneously influenced by means of the manipulation device. As a result, an additional torque for a very forceful acceleration can be provided.It is of course possible that a combination of an arrangement of a first manipulation device on at least one of the output shafts and a second or more manipulation devices on at least one planetary gear shaft and / or the planetary gear carrier is also provided.Preferably, the manipulation device is connected to the sun gear, the planetary gear shaft or the planetary gear carrier via a clutch, so that the connection between the manipulation device and the sun gear, the planetary gear shaft or the planetary gear carrier can be established or released as required. In this way, in particular, energy-efficient support-whether for inhibition or for drive-can be provided.The clutch is preferably designed as a hydraulic or mechanical clutch. The clutch between the planetary gear shaft and a brake device is preferably designed as a mechanical clutch. As a result, the planetary gear shaft can rotate substantially free of inhibition if there is no need for influencing. Furthermore, in an emergency situation or in the event of a failure of the sensor system or the active manipulation, safe operation can be established, inter alia also by decoupling the manipulator. In addition, an ESP / ABS control can be placed directly on the differential, for example, without requiring further components than the manipulator.Preferably, at least one planetary gear shaft has in its axial longitudinal extension at least four circumferential gear areas which are arranged offset with respect to one another and are each provided with circumferential toothing, wherein each toothed circumferential gear area meshes with a respective sun gear, wherein the fourth sun gear is operatively connected directly to the manipulation device, for example.Preferably, at least two planetary gears are each designed as a planetary gear shaft, wherein the two planetary gear shafts are arranged on parallel, in particular different, axes.Preferably, the planet carrier is rotatably mounted about a central axis, in particular is freely rotatably mounted. The central axis can correspond in particular to the axis of the sun gears.The planetary gear carrier can preferably be controlled with respect to its rotational movement, in particular in order to influence the rotational speeds of the rotary connections.The planet gear carrier preferably has a rotary connection, in particular an axial rotary connection. As a result, the planet wheel carrier can also serve as output.The planetary gears are preferably dimensioned depending on their tooth shape in such a way that a relative torque between those two rotary connections which are in meshing engagement via the respective sun or ring gears with the circumferential gear regions of the at least one planetary gear with the largest and the smallest radius, can move the planetary gears for rolling off even without further interventions and can thereby trigger the gear state "compensating movement". When the circumferential wheel regions approach, the manipulation device itself and the power requirement thereof can be reduced analogously thereto. By reducing the difference in the circumferential wheel areas, an approach can be achieved up to a complete locking between the outputs.Preferably, a positive connection only exists permanently between a driven rotary connection and a driving-off rotary connection. This allows a particularly compact construction of the transmission.Preferably, all planetary gears are made of a curved base body, preferably of a convexly or concavely curved base body, in particular of a convexly curved base body.Preferably, all planetary gears are straight or helical on their circumference. This allows particularly reliable and effective rolling of the teeth on one another.Preferably, the axes of all planetary gears run parallel to one another. This allows a particularly compact construction of the transmission.Preferably, the axes of all planetary gears are located on the lateral surface of a circular cylinder of radius e, at an eccentricity e to its central axis z.Seven exemplary embodiments of the invention are explained in more detail below with reference to the figures. Like reference numerals designate like components. They show schematically: FIG. 1 is a sectional view of a first embodiment of the differential gear according to the invention; FIG. 2 is a sectional view of a second embodiment of the differential gear according to the invention; FIG. 3 is a sectional view of a third embodiment of the differential gear according to the invention; FIG. 4 is a sectional view of a fourth embodiment of the differential gear according to the invention; FIG. 5 is a sectional view of a fifth embodiment of the differential gear according to the invention; FIG. 6 is a sectional view of a sixth embodiment of the differential gear according to the invention; and FIG. 7 is a sectional view of a seventh embodiment of the differential gear according to the invention.In FIG. 1, reference numeral 100 shows a first embodiment of the differential gear according to the invention. This embodiment relates in particular to a basic embodiment 1 of the invention. This means that the configuration shown in FIG. 1 shows the basic structure of the differential gear, on which all the configurations described below with extensions or additions are based.In the present case, this is a motor vehicle differential gear 100 for transmitting rotational energy between a first rotary connection 6, which can be coupled to a drive shaft connected to a drive, and two second rotary connections 2, 3, which can each be coupled via an output shaft to a wheel of the vehicle, in particular the wheels of the drive axle of the vehicle.The term "couplable" is to be understood in the present case as meaning a type of connection for force transmission, for example a rotary connection can be operatively connected to a shaft via a ring gear connection, as is the case in FIG. 1 with the rotary connection 6, or a rotary connection can be connected to a shaft in a rotationally fixed manner, as can be the case in FIG. 1 in each case, for example, with the rotary connections 2 and 3.The differential 100 shown in FIG. 1 is designed in particular as a so-called open differential, the mode of operation of which corresponds in principle to that of a conventional differential. Thus, in straight-ahead travel of the vehicle, the rotational speed of the planet carrier corresponds to the rotational speed of the drive and thus also of the outputs. When cornering, the planet carrier rotates in different directions to compensate for the differences in the curves.In contrast to conventional differentials, however, it is possible with the present differential gear 100 to scale the torque transmission by the constructive addition of further (cost-effective) planetary axles without the overall structural body becoming bulky. This would mean that a basic differential can be equipped with a minimum of one planetary axle, in the high-load range, for example with eight or more planetary axles-with a constant basic construction.The differential gear 100 shown in FIG. 1 has in the present case a total of three sun gears or ring gears 21, 31, 61.The first sun gear 21 has, at a distal free end, in particular at an outwardly protruding free end, the rotary connection 2 and, at a proximal end, in particular at a free end located in the core of the differential gear 100, a circumferential gear region 21.1 with circumferential toothing.The second sun gear 31 has, at a distal free end, in particular at an outwardly protruding free end, the rotary connection 3 and, at a proximal end, in particular at a free end located in the core of the differential gear 100, a circumferential gear region 31.1 with circumferential toothing.The third sun gear 61, which is designed in the present case as a hollow shaft, has a radially protruding circumferential gear region at a distal free end, in particular at an outwardly protruding free end, with the third rotary connection 6 designed as a ring gear, and has a circumferential gear region 61.1 with a circumferential toothing at a proximal end, in particular at a free end located in the core of the differential gear 100. For a compact construction, the third sun gear 61 is arranged radially outside around the second sun gear 31.The circumferential wheel regions 21.1, 31.1 and 61.1 project radially to different extents from the respective shaft 21, 31, 61 or, in other words, they have different diameters in comparison with one another.A planet carrier 9 is arranged around at least all shafts of the sun gears 21, 31, 61. The planet carrier 9 is supported in the present case on the first sun gear 21 and the third sun gear 61 in a freely rotatable manner via a bearing in each case and is rotatably mounted about a central axis A. In the present case, the planet gear carrier 9 carries two planet gears 41, 42 arranged radially on the outside relative to the sun gears 21, 31, 61 and opposite one another.The planetary gears 41, 42 each have a planetary gear shaft 41.0, 42.0, in the axial longitudinal extent of which three individually formed and offset radially protruding circumferential gear regions 41.1, 41.2, 41.3, 42.1, 42.2, 42.3 are provided. At the radial ends of the circumferential wheel regions 41.1, 41.2, 41.3, 42.1, 42.2, 42.3, a circumferential toothing is arranged in each case, which toothing is operatively connected to in each case one of the toothings of the sun wheels 21, 31, 61. The peripheral gear areas 41.1, 41.2, 41.3, 42.1, 42.2, 42.3 project radially from the planetary gear shaft 41.0, 42.0 to different extents, or in other words they each have different diameters corresponding to the section of the respective sun gear.The planetary gears 41, 42 are each operatively connected with the toothing of the sun gears 21, 31, 61 by their toothing arranged on the circumferential gear areas 41.1, 41.2, 41.3, 42.1, 42.2, 42.3. In particular, each planetary gear 41, 42 meshes with the toothing of the sun gears 21, 31, 61 arranged on the respective circumferential gear region 21.1, 31.1, 61.1.In this case, it is provided that the planetary gears 41, 42 and sun gears 21, 31, 61 are operatively connected to one another via the respective toothing and the respective diameter of the circumferential gear regions 21.1, 31.1, 61.1, 41.1, 41.2, 41.3, 42.1, 42.2, 42.3 in such a way that the transmission of a rotational force between all sun gears 21, 31, 61 and the two planetary gears 41, 42 takes place without inhibition. In particular, it is provided that the transmission of a rotational force between the first sun gear 21, which is connected to the not-shown first output shaft, and the second sun gear 31, which is connected to the not-shown second output shaft, takes place without inhibition.This allows a particularly circumferential freewheel of the differential gear. In particular, a particularly exact synchronization and a particularly low-loss force transmission are made possible during straight travel and during blocking a force transmission to one of the two output shafts.The planetary gears 41, 42 are dimensioned in the present case depending on their tooth shape in such a way that a relative torque between those two rotary connections 2, 3 which are in meshing engagement with the circumferential gear areas 41.1, 41.2, 41.3, 42.1, 42.2, 42.3 of the planetary gear 41, 42 via the respective sun gears 21, 31 with the largest and the smallest radius, can move the planetary gears 41, 42 for rolling and thereby trigger the gear state "balancing movement" even without further interventions.In FIG. 2, reference numeral 101 shows a second embodiment of the differential gear according to the invention, in particular a so-called semi-locking differential. This involves the individual active braking of individual outputs of the differential transmission.This embodiment relates in particular to an embodiment of the invention with an adjustable inhibition of the first sun wheel 21, in particular via the planetary carrier 9. By means of a lock which can be controlled and regulated between the planet carrier 9 and the first sun gear 21, braking of the individual rotary connection 2 is made possible without the second output-side rotary connection 3 having to be simultaneously released, as is absolutely necessary, for example, in the case of conventional differentials of self-locking design. As a result, for example, a tractor can be turned substantially on the spot or a tracked vehicle can rotate about its own vertical axis.The construction is similar to the first embodiment shown in FIG. 1, differing only in that a manipulation device 90 for braking is additionally arranged between the planetary carrier 9, in particular on a side of the differential gear 101 opposite the rotary connection 6, and the first sun wheel 21.The manipulation device 90 serves to influence a force transmission, in particular a force transmission to at least one output shaft. In the embodiment shown in FIG. 2, the manipulation device 90 serves in particular as an inhibiting device for inhibiting a transmission of force, in particular a transmission of force to at least one output shaft, in the present case to the first sun gear 21 connected to the not-shown first output shaft. For this purpose, in the embodiment 101 according to FIG. 2, the manipulation device 90 serves in particular for generating an inhibition between the planet carrier 9 and the first sun gear 21, in order to bring about a lower torque relative to the second sun gear 31 and thus a braking of the first sun gear 21. For this purpose, the planet carrier 9 is operatively connected to the first sun gear 21 via the manipulation device 90. The manipulation device 90 is designed as a fluid coupling. It represents in particular a visco / converter / Fottinger coupling. The manipulation device 90 thus permits only a certain blocking effect.By relatively decelerating the rotation transmission from the planet carrier 9 to the first sun gear 21, the transmission of power to the first sun gear 21 can be inhibited. For this purpose, the manipulation device 90 in FIG. 2 is designed as a fluid coupling. The fluid coupling 90 may be provided in a conventional manner to achieve the desired effect.In the present case, the manipulation device 90 is additionally designed to be individually actuatable, so that the magnitude of the influence on the force transmission can be individually controlled and / or regulated. This is done in the present fluid coupling 90 in that the fluid can be introduced into or discharged from the fluid coupling 90. As a result, different braking effects and thus different degrees of inhibition can be achieved between the planet carrier 9 and the first sun wheel 21. In particular, the degree of inhibition can also be zero. Because of the non-self-locking construction, it is not necessary here to separately release the other sun wheel 31. As an alternative to a fluid coupling, other technological versions of couplings would also be conceivable.The differential 101,104,105 shown in FIG. 2 and also in FIGS. 5 and 6 relate to versions of the differential with which the planet carrier can be dynamically synchronized. This is a slip-controlled differential. The positioning of the manipulation devices is fundamentally irrelevant-they can be installed both on the drive side or output side or also in combination.Due to the transmission ratio within the transmission, however, much less braking energy is required in order to achieve the same effect as in conventional locking devices. This means less energy loss.FIG. 3 shows a third embodiment of the differential transmission according to the invention with the reference numeral 102, in particular again a so-called semi-locking differential. This again concerns the individual active manipulation, in particular braking of individual outputs of the differential gear. The design is similar to the first embodiment shown in FIG. 2, differing only in that in the present case two manipulation devices 91, 91' are provided and the manipulation devices 91, 91' are each designed as a mechanical brake system. Here, alternative technologies such as eddy current brakes or recuperation generators are likewise conceivable.This embodiment in turn relates in particular to an embodiment of the invention in which the planetary gear carrier 9 can be controlled with respect to its rotational movement, in particular in order to influence the rotational speeds of the output-side rotary connections 2 and 3. In this embodiment, in particular, an adjustable inhibition of the first sun gear 21 can take place via a targeted influencing, in particular braking, of the planetary carrier 9. In this case, the manipulation device 91' designed as a brake system is provided for braking the planet carrier 9. For this purpose, the planet carrier 9 has a protruding portion on a circumferential side, on which the manipulation device 91' embodied as a brake system acts, in particular by means of two individually controllable brake shoes. By relatively braking the rotation of the planet carrier 9, the transmission of force to the first sun gear 21 can be inhibited.By means of a lock which can be controlled and regulated between the planet carrier 9 and the first sun gear 21, braking of the individual rotary connection 2 is made possible without the second output-side rotary connection 3 having to be simultaneously released, as is absolutely necessary, for example, in the case of conventional differentials of self-locking design.Naturally, the manipulation device 91' designed as a brake system can be individually controlled by adjusting the contact pressure of the brake shoes.In addition, in this third embodiment of the differential gear 102 according to the invention, a second manipulation device 91 is provided which is operatively connected to both planetary gears 41, 42.To implement this braking possibility, a fourth sun gear 71 is provided as well as a further circumferential gear area 41.4, 42.4, which is arranged in the axial longitudinal extension of the planetary gear shaft 41.0, 42.0 and is provided with circumferential toothing, on each planetary gear 41, 42. This circumferential gear region 41.4, 42.4 is operatively connected in meshing fashion to the fourth sun gear 71. In this embodiment, both planetary gears 41, 42 can thereby be directly manipulated, in particular can be braked in the present case. The manipulation device 91 is substantially of the same construction as that of the manipulation device 91', namely as a mechanical brake system. This brake system 91 directly engages the fourth sun gear 71 so that the latter and thus ultimately also the respective planetary gear 41, 42 can be braked directly. Of course, the brake system 91 can be controlled individually by adjusting the contact pressure of the brake shoes.The controllable and regulable inhibition of the planetary gears 41, 42 enables a braking of the second sun gear 31 and thus of the second rotary connection 3 without the output-side first rotary connection 21 having to be simultaneously enabled, as is absolutely necessary, for example, in the case of conventional differentials of self-locking construction.The differential 102 shown in FIG. 3 thus relates to a construction in which, by braking either the planet carrier 9 or the braking of the additional sun gear 71, a propulsion of the drive wheel on the outside of the curve can be achieved with simultaneous braking of the drive wheel on the inside of the curve (torque vectoring). With the simultaneous use of both brakes, a parking brake can be realized. For this purpose, the arrangement of further sun gears and / or planetary gears would also be conceivable.It should be clear that this arrangement would also be conceivable for a differential gear in which, instead of the manipulation device 91 provided in the present case for braking the planetary gear shaft 41.0, 42.0, a manipulation device for accelerating the planetary gear shaft 41.0, 42.0 can be provided.In FIG. 4, reference numeral 103 shows a fourth embodiment of the differential gear according to the invention. In this case, it is provided that individual components of the differential gear 103 can be braked or accelerated. The design is similar to the first embodiment shown in FIG. 1, differing only in that in the present case there are additionally two manipulation devices 92, 92' as additional brakes and / or drives. For this purpose, the manipulation devices 92, 92' are each designed as an electric motor which can be operated selectively as a motor for driving or as a generator for braking.The differential gear 103 relates in particular to an embodiment of the invention with an indirectly adjustable deceleration or additional acceleration of the first sun gear 21-and thus also of the first rotary connection 2-via a targeted deceleration or acceleration of the planetary gear carrier 9 and / or an indirectly adjustable deceleration or additional acceleration of the second sun gear 31-and thus also of the second rotary connection 3-via a targeted deceleration or acceleration of the planetary gears 41, 42.The differential 103 according to FIG. 4 relates in particular to a construction in which, in the present case, propulsion of the respective drive wheel on the outside of the curve can be achieved by two electric motors (or generators) - the drive wheel on the inside of the curve is braked simultaneously (torque vectoring). In contrast to the version with brakes (as in FIG. 3 ), no (braking) energy is lost here, but the energy applied by the respective electric motor additionally flows into the drive.Here, a rotation of the vehicle about its own vertical axis is conceivable, as would be achievable, for example, in tracked vehicles or off-road vehicles. Due to the design, for example, in an off-road vehicle, it would also be necessary to use not four high-performance engines of equal size, but only two-or even only one in conjunction with a plurality of differentials.The differential control motors could be significantly smaller, which reduces costs. Optionally, a configuration of the motors as generators in order to be able to apply maximum manipulation forces-or in order to effect recuperation by braking action. Of course, a configuration of the motors as hydraulic motors or in another design is also conceivable.Next, the case of acceleration will be explained in detail.For accelerating the planet carrier 9, the manipulation device 92 acts as an electric motor. The manipulation device 92 engages in particular on the circumferential region of the planet carrier 9. For this purpose, the planet carrier 9 has a rotary connection, in particular an axial rotary connection, on a circumferential side. This rotary connection is in the present case exemplarily formed as a protruding portion on which the manipulation device 92 formed as an electric motor acts, in particular by means of an additional drive shaft. By relatively accelerating the rotation of the planet carrier 9, the power transmission from the third rotary connection 6 to the first sun gear 21 can be assisted and the rotation of the first sun gear 21 can be increased. The acceleration force of the electric motor can be individually adjustable.In order to enable the same effect also in the case of the second rotary connection 31, the differential gear 103 additionally comprises a second manipulation device 92' acting on the third sun wheel 61. This second manipulation device 92' can be, in particular, the main engine of the vehicle. This can operate, for example, electrically, hydraulically or as a burner. This second manipulation device 92' assists the acceleration of the third sun gear 61 on the drive side, which transfers its rotational energy directly to the planetary gears 41, 42.In addition, in this third embodiment of the differential gear 102 according to the invention, a second manipulation device 92' operatively connected to both planetary gears 41, 42 is provided. In this embodiment, both planetary gears 41, 42 can thereby be directly accelerated relatively. The controllable and regulable acceleration of the planetary gears 41, 42 enables an acceleration of the second sun gear 31 and thus of the second rotary connection 3 without the output-side first rotary connection 21 having to be simultaneously released, as is absolutely necessary, for example, in the case of conventional differentials of self-locking construction.Consequently, by directly supporting one of the outputs, a resulting braking, in particular a braking without energy destruction, of the other output--not energy-supported--is made possible, in particular with the lowest transmission ratio and the highest necessary support drive. By supporting the planet gear carrier by applying energy, a medium support drive is required at a medium transmission ratio. By supporting the planetary axle by applying energy, a smallest support drive is required at the highest transmission ratio.It should be clear that the electric motor provided for acceleration can also be used as a generator and consequently can correspondingly generate not an acceleration force but a braking force. The manipulation devices 92, 92' according to the embodiment 103 can thus correspondingly accelerate or decelerate the components explained above, in particular the planetary gear carrier 9 and / or the planetary gears 41, 42.Of course, an intensifying, opposite application of the manipulation devices 92, 92' is also possible, namely by using one of the manipulation devices 92, 92' as a drive motor and the other of the manipulation devices 92, 92' as a brake generator.The fourth embodiment of the differential transmission 103 thus enables, in particular, the so-called "torque vectoring" by an active drive and / or braking of individual components.In FIG. 5, a fifth embodiment of the differential transmission according to the invention is shown with the reference numeral 104, in particular again a so-called semi-locking differential, similar to the embodiment shown in FIG. 2. This involves the individual active braking of individual outputs of the differential transmission.This embodiment relates in particular to an embodiment of the invention with an adjustable inhibition of the first sun wheel 21, in particular via the planetary carrier 9. By means of a lock which can be controlled and regulated, in particular between the planet carrier 9 and the first sun gear 21, braking of the individual rotary connection 2 is made possible without the second rotary connection 3 on the output side having to be simultaneously released, as is absolutely necessary, for example, in the case of conventional differentials of self-locking design. The placement of the brake serving for inhibiting can in principle take effect at different areas: either directly at the drive or at the output 21 or 31, or at both. In this way, the blocking degree can be manipulated in particular.The construction is similar to the first embodiment shown in FIG. 2, differing only in that the manipulation device 91" is not designed as a fluid coupling, but as a mechanical brake between the planetary carrier 9 and the first sun wheel 21.In the embodiment shown in FIG. 5, manipulation device 91" thus serves in turn to inhibit a transmission of force to first sun gear 21, which is connected to the not-shown first output shaft. To this end, manipulation device 91" in embodiment 104 effects an inhibition between planet carrier 9 and first sun gear 21, in order to effect a lower torque relative to second sun gear 31 and thus a braking of first sun gear 21. For this purpose, the planet carrier 9 is operatively connected to the first sun gear 21 via the manipulation device 91". By relatively decelerating the rotation transmission from the planet carrier 9 to the first sun gear 21, the transmission of power to the first sun gear 21 can be inhibited. For this purpose, the manipulation device 91" in FIG. 5 is designed as a mechanical brake. The brake 91" can be provided in a conventional manner by means of jaws and disks to achieve the desired effect. The brake disk is formed in the present case by a radially protruding section of the first sun wheel 21. The first sun gear 21 can thus be braked relative to the planet carrier 9 in a relatively simple manner up to a complete standstill or to a relative speed of zero.In FIG. 6, reference numeral 105 shows a sixth embodiment of the differential gear according to the invention. In this case, it is provided that individual components of the differential transmission 103 can be actively accelerated. The construction is similar to the first embodiment shown in FIG. 1, differing only in that a manipulation device 90' is provided in the present case as an additional drive means between the third sun gear 61 and the planet carrier 9.This embodiment relates in particular to an embodiment of the invention with an adjustable additional acceleration of the first sun gear 21 via a targeted acceleration of the planetary carrier 9.In this case, for accelerating the planet carrier 9, the manipulation device 90' is again arranged as a fluid clutch, in particular as an electromechanical clutch, this time between the third sun gear 61 and the planet carrier 9. The rotational force transmitted from a not-shown drive shaft to the third sun gear 61 can thus also be transmitted at least partially directly to the planet carrier 9 by the controllable fluid clutch 90'.By synchronizing the rotation of the planet carrier 9 relative to each other, the force transmission can be transmitted from the third rotary connection 6 to the planet carrier, which in turn manipulates the degree of locking.The fluid coupling 90' is designed to be individually controllable, so that the magnitude of the influence on the locking effect can be individually controlled and / or regulated. This is done in the present fluid coupling 90' by allowing the fluid to be introduced into or discharged from the fluid coupling 90'. As a result, different driver effects and thus different degrees of inhibition between the third sun gear 61 and the planetary carrier 9 can be achieved. In particular, the degree of inhibition can also be zero. Because of the non-self-locking construction, it is not necessary here to separately release the other sun wheel 31.In FIG. 7, reference numeral 106 shows a seventh embodiment of the differential gear according to the invention, which is very similar to the embodiment 105 shown in FIG. 6. In particular, the only difference here is that the fluid clutch 90'' cannot be actuated, but is provided as a continuous clutch between the third sun gear 61 and the planet carrier 9.This is thus in particular a differential that is pre-locked by the manipulation device and has a firmly defined locking effect. The differential 106 thus shown in FIG. 7 relates to a construction in which a preset locking effect can be achieved with a pre-filled viscous clutch.It should be understood that the scope of the present invention is not limited to the described embodiments. In particular, the structure and the arrangement of the components of the differential gear can be completely modified with the same mode of operation, without changing the core of the invention.List of reference numbers:1 Basic configuration 2 Rotary connection 3 Rotary connection 4 Rotary connection 6 Rotary connection 8 Clutch 9 Planet carrier 21 Sun or ring gear 31 Sun or ring gear 41 Planet gear 41.0 Planet gear shaft 41.1 Circumferential gear region 41.2 Circumferential gear region 41.3 Circumferential gear region 41.4 Circumferential gear region 42 Planet gear 42.0 Planet gear shaft 42.1 Circumferential gear region 42.2 Circumferential gear region 42.3 Circumferential gear region 42.4 Circumferential gear region 61 Sun or ring gear 61.1 Circumferential gear region 71 Sun or ring gear 90 Manipulation device, fluid clutch 91, 91' Manipulation device, mechanical brake 92, 92' Manipulation device, electric motor 100 Differential gear 101 Differential gear 102 Differential gear 103 Differential gear 104 Differential gear 105 Differential gear 106 Differential gear A Axle

Claims

Differential gear (100, 101, 102, 103, 104, 105, 106), in particular a motor vehicle differential gear, for transmitting rotational energy between at least two rotary connections (2, 3, 6), which can each be coupled to a drive or output shaft, having at least one planetary gear (41, 42) and at least one sun or ring gear (21, 31, 61, 71) which meshes therewith, wherein at least one planetary gear (41, 42) is designed as a planetary gear shaft (41.0, 42.0), and the planetary gear shaft (41.0, 42.0) is preferably mounted in or on a planetary gear carrier (9) and has, in its axial longitudinal extent, at least three circumferential gear regions (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4) with different diameters, which are arranged offset from one another and are each provided with an all-round toothing, and having each toothed circumferential gear region (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4) a sun gear (21, 31, 61, 71) meshes, and at least two of the sun gears (21, 31) are coupled rotationally fixedly to one of the rotary connections (2, 3) or are directly connected, characterized in that a transmission state is provided in which at least two of the sun gears (21, 31, 61, 71) and the at least one planetary gear (41, 42) are operatively connected to one another in such a way that the transmission of a rotational force between at least one first rotary connection (2) to at least one second rotary connection (3) takes place without inhibition.Differential gear (100, 101, 102, 103, 104, 105, 106) according to Claim 1, characterized in that, in the first transmission state, the at least two sun gears (21, 31) and the at least one planetary gear (41, 42) are operatively connected to one another in such a way that a rotation between all sun gears (21, 31, 61, 71) and the at least one planetary gear (41, 42) takes place without inhibition.Differential gear (101, 102, 103, 104, 105, 106), in particular a motor vehicle differential gear, for transmitting rotational energy between at least three rotary connections (2, 3, 6) which can each be coupled to a drive or output shaft, in particular a differential gear according to one of Claims 1 or 2, having at least one planetary gear (41, 42) and at least one sun or ring gear (21, 31, 61, 71) which meshes therewith, wherein at least one planetary gear (41, 42) is designed as a planetary gear shaft (41.0, 42.0), and the planetary gear shaft (41.0, 42.0) is preferably mounted in or on a planetary gear carrier (9) and has, in its axial longitudinal extent, at least three circumferential gear regions (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4) which are arranged offset from one another and are each provided with an all-round toothing, with different diameters, and a sun wheel (21, 31, 61, 71) meshes with each toothed circumferential wheel region (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4), and at least two of the sun wheels (21, 31) are coupled rotationally fixedly to one of the rotary connections (2, 3) or are directly connected, characterized in that a manipulation device (90, 91, 92) is provided for influencing a force transmission, in particular a force transmission to at least one output shaft, wherein the manipulation device (90, 91, 92) is designed to be individually controllable, such that the magnitude of the influence on the force transmission can be individually controlled and / or regulated.Differential gear (101, 102, 103, 104, 105, 106) according to Claim 3, characterized in that the manipulation device (90, 91, 92) is designed as an inhibiting device for inhibiting a transmission of force, in particular a transmission of force to at least one output shaft, wherein the inhibiting device is designed to be individually controllable, such that the magnitude of the reduction in the transmission of force can be controlled and / or regulated individually.Differential gear (101, 102, 103, 104, 105, 106) according to either of Claims 3 and 4, characterized in that the manipulation device (92) is designed as a drive device for amplifying a force transmission, in particular a force transmission to at least one output shaft, wherein the drive device is designed to be individually controllable, such that the magnitude of the amplification of the force transmission can be individually controlled and / or regulated.Differential gear (101, 102, 103, 104, 105, 106) according to one of Claims 3 to 5, characterized in that the manipulation device (90, 91, 92) is directly operatively connected to the at least one sun wheel (21, 31, 61, 71), to the at least one planetary wheel (41, 42) and / or to the at least one planetary wheel carrier (9).Differential gear (101, 102, 103, 104, 105, 106) according to one of Claims 3 to 6, characterized in that the manipulation device (90, 91, 92) is designed as a braking device, as a motor, in particular as an electric motor, and / or as a generator.Differential gear (101, 102, 103, 104, 105, 106) according to one of Claims 3 to 7, characterized in that a transmission state is provided in which, for the transmission of force, the at least one planetary gear (41, 42) is operatively connected to at least one sun gear (61) connected to an input shaft and to at least two sun gears (21, 31) each connected to an output shaft, wherein the transmission of force to at least one of the sun gears (21, 31) connected to an output shaft or to a component connected to this sun gear (21, 31) in a rotationally fixed manner can be actively influenced, in particular actively reduced or enlarged, by means of the manipulation device (90, 91, 92).Differential gear (101, 102, 103, 104, 105, 106) according to one of Claims 3 to 8, characterized in that a transmission state is provided in which, for the transmission of force, the at least one planetary gear (41, 42) is operatively connected to at least one sun gear (61) connected to an input shaft, to at least two sun gears (21, 31) each connected to an output shaft and to at least one sun gear (71) operatively connected directly to a manipulation device (90, 91, 92), wherein the transmission of force to the at least one planetary gear (41, 42) or the planetary gear carrier (9) or to a component connected to the planetary gear (41, 42) or the planetary gear carrier (9) in a rotationally fixed manner can be actively influenced, in particular actively reduced or enlarged, by means of the manipulation device (90, 91, 92).Differential gear (101, 102, 103, 104, 105, 106) according to one of Claims 3 to 9, characterized in that the manipulation device (90, 91, 92) is connected to the sun wheel (21, 31, 61), the planet wheel (41, 42) and / or the planet wheel carrier (9) via a separable clutch, such that the connection between the manipulation device (90, 91, 92) and the sun wheel (21, 31), the planet wheel (41, 42) and / or the planet wheel carrier (9) can be established or released as required.Differential gear (101, 102, 103, 104, 105, 106) according to Claim 10, characterized in that the clutch is designed as a hydraulic, mechanical or electromechanical clutch.Differential gear (101, 102, 103, 104, 105, 106) according to one of Claims 3 to 11, characterized in that at least one planetary gear shaft (41.0, 42.0) has, in its axial longitudinal extent, at least four circumferential gear regions (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4) which are arranged offset from one another and are each provided with circumferential toothing, and a sun gear (21, 31, 61, 71) meshes with each toothed circumferential gear region (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4), wherein the fourth sun gear (71) is connected directly or via a clutch to the manipulation device (90, 91, 92).Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that at least two planetary gears (41, 42) each have a planetary gear shaft (41.0, 42.0), which are arranged on axes aligned parallel to one another.Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that the planet carrier (9) is mounted rotatably about a central axis (A).Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that the planetary gear carrier (9) can be actuated with respect to its rotational movement, in particular in order to influence the rotational speeds of the rotary connections (2, 3, 6).Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that the planet carrier (9) has a rotary connection, in particular an axial rotary connection.Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that planet gears (41, 42) are dimensioned as a function of their gear diameter and / or tooth shape in such a way that a relative torque between those two rotary connections (2, 3, 6) which are in meshing engagement via the relevant sun or ring gears (21, 31, 61, 71) with the circumferential gear regions (41.1, 41.2, 41.3, 41.4, 42.1, 42.2, 42.3, 42.4) of the at least one planet gear (41, 42) having the largest and the smallest radius can move the planet gears (41, 42) for rolling and can thereby trigger the gear state "compensating movement" even without further interventions.Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that a positive connection is permanently provided between only one single driven rotary connection (6) and only one single driving-off rotary connection (2, 3).Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that all planetary gears (41, 42) are produced from a curved base body, preferably from a convexly or concavely curved base body, in particular from a convexly curved base body.Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that all the planetary gears (41, 42) are straight or helical on their circumference.Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that the axes of all the planet gears (41, 42) run parallel to one another.Differential gear (100, 101, 102, 103, 104, 105, 106) according to one of the preceding claims, characterized in that the axes of all the planet gears (41, 42) are on the lateral surface of a circular cylinder.

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