Drive unit and operating procedure

Abstract

The invention relates to a drive unit (1) comprising at least two drives (15), at least one housing, therein comprising at least two drive input segments (3) arranged coaxially to the main axis (2), each drive input segment (3) having at least one torque transmitter (6), a multi-start planetary gear unit comprising at least one planetary gear unit arranged coaxially to the main axis (2), comprising at least one ring gear (10), a carrier gear (8), a sun gear (7) and an output shaft (11.5), and at least five mechanical switching elements, wherein the sun gear (7), the carrier gear (8) or the ring gear (10) is rotationally fixed to the output shaft (11.5), and a method for operating and changing the transmission ratio of the drive unit (1).

Description

[0001] The invention relates to a drive unit 1 of the type defined in more detail in the preamble of claim 1 and further to a method for operating this drive unit 1 according to claim 5.

[0002] According to the current state of the art, electrical machines such as electric motors and electric generators are known. The function of electric motors is to convert electrical energy into kinetic energy. They convert electrical power into mechanical power. This mechanical power is provided at the output shaft with a specific torque at a specific rotational speed. Electric generators, on the other hand, are used to convert mechanical power into electrical power. Electrical machines are known in various sizes and with different power outputs. According to the current state of the art, they usually comprise at least one stator and at least one rotor. The rotor is set into rotation by utilizing attractive and repulsive forces exerted on each other by several magnetic fields between the stator and rotor.The stator or rotor contains permanent magnets, and the other component contains electrical coils, or both the stator and rotor contain electrical coils. There are also designs in which the rotating magnetic field of the rotor is generated by magnetizable iron cores with poles. Such motors are called reluctance motors. Magnetizable iron cores with poles are also referred to as laminated cores in the literature.

[0003] It is known that there is a relationship between the power output of the electric machine, the rotational speed of its input or output shaft, and the torque at its input or output shaft. Mechanical transmissions are used to convert torques.

[0004] Mechanical transmissions are known that convert the rotational speed between their input shaft and their output shaft. In this process, a specific torque at a specific rotational speed of one shaft is converted into a different specific torque at a different specific rotational speed of the other shaft and made available for the corresponding application.

[0005] Mechanical transmissions in the form of multi-stage planetary gears are also known. Planetary gears are known that consist of a sun gear, a ring gear, and a planet carrier (also called a carrier gear) with one or more planet gears attached to it. Furthermore, compound planetary gears, which are composed of several planetary gears, are also known as multi-stage planetary gears. There are designs in which several planetary gears are rotationally fixed together. According to the current state of the art, the gear changes, i.e., the change in the transmission ratio, within multi-stage planetary gears are achieved by various types of mechanical switching elements.

[0006] Mechanical switching elements in transmission technology are composed of various friction-fit or positive-locking connecting elements. Positive-locking connecting elements can also be subjected to force.

[0007] Examples of mechanical switching elements based on frictional engagement include brakes, clutches (e.g., friction clutches), radially designed overrunning clutches (also functioning as backstops or freewheels), backstops whose locking direction is reversible with respect to the direction of rotation or which can be disengaged, and disengaged overrunning clutches. Form-fit versions of the aforementioned mechanical switching elements consist, for example, of connecting elements such as claws, teeth, pins, or bolts and recesses. Depending on the design, these can also be force-actuated. Mechanical switching elements, especially locking devices, constructed from such optionally force-actuated, form-fit connecting elements, hereinafter also referred to as locking elements in this patent specification, are disclosed, among others, in EP 1 820 251 B1, EP 3 744 998 A1, and EP 1 958 314 B1.

[0008] Mechanical switching elements can be switched pneumatically, hydraulically, mechanically, or electrically. This can also be achieved by an actuator. Electrically operated switching jaws are known, for example. An example of this is described in DE 10 2022 122 486 A1. Electromagnetic gear couplings or electromagnetic jaw couplings, based on similar principles, are also described in patent literature, specifically in EP 3 748 185 B1.

[0009] Furthermore, combinations of electric machines and multi-start planetary gears are known. Such combinations, in which the multi-start planetary gear is located wholly or partially within the rotor of the electric machine, are known, for example, from DE 10 2007 021 359 B4, DE 44 07 714 C1, DE 10 2012 210 242 A1 and DE 10 2020 106 248 A1.

[0010] Furthermore, combinations of electric machines with split stators, i.e. stator segments, and split rotors, i.e. rotor segments, in conjunction with planetary gearboxes are known, for example, from WO 2008 007125 A1 and from DE 10 2006 041 160 A1.

[0011] Furthermore, multi-stage planetary gears are also known, which are composed of several planetary gears whose drive is not by electric machines, but for example by heat engines, muscle power, wind power, other types of drives or a combination of different types of drives.

[0012] A drive unit comprising at least a housing, therein at least an electric machine consisting of a stator having at least two stator segments, and further comprising a rotor having at least two rotor segments, each with at least one brake or a backstop having a fixed connection to the housing, and a multi-start planetary gear consisting of at least one simple planetary gear arranged coaxially to the main shaft, comprising a ring gear, a carrier gear and a sun gear, is known from DE 10 2022 112 798 B4. The rotor segments, in conjunction with one of the stator segments, each constitute a drive. Thus, the drive unit from DE 10 2022 112 798 B4 has at least two separate drives.

[0013] The drive unit disclosed in DE 10 2022 112 798 B4 is characterized in that at least two stator segments of the stator of the electric machine are displaceable parallel to the main axis by means of at least one displacement device and the at least two rotor segments are each separately and rotationally fixed to the sun gear, the ring gear or the carrier gear.

[0014] Furthermore, it is known that the state of the art includes technical components that serve the delayed transmission of torques. An example of this is the torsion bar, also called a torsion spring.

[0015] Furthermore, it is known that, with regard to the force flow upstream and downstream of these technical components, the forces acting on them, in particular torques and rotational speeds, are determined and evaluated by means of sensor units in order to determine, for example, support torques in the field of electromechanical steering systems of motor vehicles and to optimize the steering control mechanism. Examples of such systems can be found in DE 601 09 531 T2 and further in DE 10 2014 208 926 A1 and also in WO 2010 124 884 A1.

[0016] The present invention is based on the objective of eliminating disadvantages of the drive unit from DE 10 2022 112 798 B4.

[0017] The disadvantages initially arise from the sliding device, which represents an increased design effort and means that the drive unit is designed for electric drives.

[0018] A further disadvantage is that without additional components, a reverse gear and therefore a reversal of the direction of rotation of the output shaft cannot be achieved.

[0019] Another disadvantage of the proposed drive unit is the availability of recuperation only in the highest gear.

[0020] The present invention aims to solve the problem of making the multi-start planetary gear of the drive unit capable of being driven by electric machines, heat engines, muscle power, wind power, or water power, or combinations thereof. Depending on the design of the drive unit, these drives can be located either on the main axis, i.e., the axis of rotation of the multi-start planetary gear and thus of the planetary gears encompassing it, or not on the main axis of the multi-start planetary gear.

[0021] If, as in DE 10 2022 112 798 B4, electric drives or a combination of electric and other types of drives are used, various mechanical switching elements according to the state of the art should be usable, depending on the design and area of ​​application.

[0022] Depending on the application, the use of backstops as mechanical switching elements in this drive unit can increase the technical complexity relative to the benefits. When using brakes as mechanical switching elements, the additional disadvantages include the thermal stress during switching operations, the complex design of the brakes, the technical effort required for controlling the brakes, and the increased maintenance requirements compared to backstops.

[0023] According to this, brakes and backstops in drive unit designs are to be partially or completely replaced by simpler and easier-to-switch, at least positive-locking, mechanical switching elements, whereby the positive locking of their connecting elements can also be force-actuated.

[0024] Furthermore, by using simple mechanical switching elements, whose function is based at least on the positive locking of their various connecting elements, for example conventional electrically operated jaw couplings, partially or exclusively depending on the area of ​​application, without necessarily using a sliding device known in the drive unit from DE 10 2022 112 798 B4, a rotationally fixed connection between rotatable and rotating shafts can be established in order to change the transmission ratio of the multi-start planetary gear, i.e. to perform gear changes.

[0025] These simple mechanical switching elements of the drive unit according to the invention, which are based at least on positive locking, are hereinafter referred to as locking devices. The connecting elements of the locking devices, with the aid of which rotationally fixed connections between rotatable or rotating shafts of the simple multi-start planetary gear can be established by means of a positive locking action, optionally subjected to force, are hereinafter referred to as locking elements.

[0026] The locking devices are to be monitored, controlled and regulated by the main electronic control unit or by conventional control units controlled and regulated by it.

[0027] Furthermore, the problem arising from this situation must be solved: to establish and release a positive locking mechanism, optionally force-applied, between the locking elements of the mechanical switching elements to be used for changing the transmission ratio of the drive unit according to the invention, while the output shaft of the multi-start planetary gear is rotating. This should be achieved without impairing the function of the drive unit according to the invention and, compared to mechanical switching elements based solely on force-fit, within an acceptable, and preferably short, timeframe.

[0028] Mechanical forces, especially torques, can also occur at any time via the rotating output shaft of the multi-start planetary gear unit, acting on the components of the planetary gear unit from outside the housing. These forces, possibly in interaction with the mechanical forces, especially torques, generated by the electric machine of the drive unit, which act outside the housing via the components of the planetary gear unit and the output shaft of the multi-start planetary gear unit, lead to changing rotational speeds of the components of the planetary gear unit, i.e., sun gear, ring gear, or carrier gear. This would regularly prevent the establishment of a positive or positive-locking connection of the locking elements of such a locking device.because the torques, through the existing non-rotatable connection between a component of the planetary gear and the output shaft of the multi-start planetary gear, act back on the component of the planetary gear connected to it, and thus also on the other components of the planetary gear and, if applicable, non-rotatably connected shafts of the multi-start planetary gear.

[0029] Thus, in the course of operation of the invention, locking devices as mechanical switching elements should enable rotationally fixed connections between rotating shafts to be established or released in order to change the transmission ratio of the multi-start planetary gear, even if a dynamic change occurs in the mechanical forces, in particular torques, acting from outside the housing on the output shaft of the multi-start planetary gear of the drive unit, and may be intensifying to the mechanical forces, in particular torques, generated by the electric drives of the drive unit, or in the opposite direction, i.e., weakening to the mechanical forces, in particular torques, generated by the electric drives of the drive unit.These mechanical forces, especially torques, acting on the drive unit from outside the housing can lead to changes in the rotational speeds of the components of the planetary gear.

[0030] These tasks should be solved with minimal additional design effort, a reduction in the size of the drive unit and a reduction in manufacturing costs compared to the state of the art.

[0031] Furthermore, the transmission ratio of the drive unit according to the invention should also be able to be changed without interrupting the train, so that a load-switching drive unit can be provided.

[0032] Furthermore, the present invention is based on the objective of providing embodiments of the drive unit which provide recuperation and a reverse gear in all gears, i.e., at all different switchable gear ratios, and which enable these changes in the gear ratio of the multi-gear planetary gear of the drive unit, controlled and regulated by an electronic main control unit.

[0033] Furthermore, the present invention is based on the objective of providing, for locking devices which serve to create a rotationally fixed connection between rotatable or rotating shafts and which require an amount of electrical energy for operation, this amount of electrical energy without wear and thus without friction losses.

[0034] A further object of the invention is to use the transmission path of the amount of energy transferred electrically or according to the principle of electromagnetic induction for the operation of the locking devices equally for the bidirectional communication between the main electronic control unit and at least the electronic control units of the locking devices.

[0035] This problem is solved by the drive unit 1 according to the invention according to claims 1, 2, 3 and 4 and a method for operating this drive unit 1 according to claims 5, 6, 7, 8, 9, 10 and 11.

[0036] Claim 12 specifies the advantageous fields of application of the invention.

[0037] A key aspect of the invention is that each torque transmitter 6 and each drive input segment 3 connected to the torque transmitter 6 is assigned at least one drive 15, the at least two drive input segments 3 can be coupled to each other by at least one mechanical switching element, Each of the at least two drive input segments 3 can be coupled separately to at least one component of at least one planetary gear set of the multi-start planetary gear set, namely ring gear 10, carrier gear 8 or sun gear 7, by means of a mechanical switching element in a rotationally fixed manner, wherein the at least two drive input segments 3 can be coupled to different components of at least one planetary gear set of the multi-start planetary gear set, namely either to sun gear 7 and carrier gear 8 or to sun gear 7 and ring gear 10 or to carrier gear 8 and ring gear 10, which are not connected to the output shaft 11.5 of the planetary gear set of the multi-start planetary gear set. the two components of at least one planetary gear of the multi-start planetary gear, which are not connected to the output shaft 11.5, namely either the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, each of which can be blocked in at least one direction of rotation by at least one mechanical switching element which has a fixed connection with the housing, where at least two drives 15 of the drive input segments 3 are electrically operable, the drive unit 1 comprises at least one electronic main control unit, and the electrically operable drives 15 of the drive input segments 3 can be used independently of one another both for driving the multi-start planetary gear and in conjunction with the mechanical switching elements and the electronic main control unit for changing the transmission ratio of the drive unit 1, the mechanical switching elements of the at least five mechanical switching elements, by which the at least two drive input segments 3 can be coupled in a rotationally fixed manner to the components of the planetary gear of the multi-start planetary gear that are not connected to the output shaft 11.5, namely either the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, are locking devices 12, wherein the at least two electrically operated drives 15 of the drive unit 1 in conjunction with the electronic main control unit can be used to position the positive locking elements 13b and 13c of the locking devices 12 and wherein the at least two electrically operated drives 15 of the drive unit 1 can be used in conjunction with the main electronic control unit to hold the switching position of the positive locking elements 13b and 13c of the locking devices 12.

[0038] The drive unit 1 according to the invention comprises at least - at least two drives 15, - at least a housing, at least arranged within it - at least two drive input segments 3 arranged coaxially to the main axis 2, - wherein each drive input segment 3 has at least one torque transmitter 6, - a multi-stage planetary gear system, comprising - at least one planetary gear set arranged coaxially to the main axis 2, comprising at least - a 10-inch ring gear - a carrier wheel 8, - a sun wheel 7 - and an output shaft 11.5, - and at least five mechanical switching elements, wherein the sun gear 7, the carrier gear 8 or the ring gear 10 is non-rotatably connected to the output shaft 11.5.

[0039] The drives 15 according to the invention, after converting the various forms of energy such as muscle energy, thermal energy or electrical energy, provide these in the form of kinetic energy for the torque transmitters 6.

[0040] The output shaft 11.5 of a planetary gear of the multi-start planetary gear also represents the output shaft of the multi-start planetary gear, provided that the multi-start planetary gear is made up of only one planetary gear.

[0041] A torque transmitter 6 according to the invention, exemplified in Fig. Figure 5 shows a typical mechanical component or assembly that transmits torques from its associated drive 15 to the drive input segment 3 connected to it. The transmission of the respective torque from the respective drive 15 to the associated torque transmitter 6 typically occurs via a shaft.

[0042] The at least two torque transmitters 6 can transmit the applied torques independently of one another to the respective drive input segment 3 of the drive unit 1 according to the invention. The transmission of the respective torque from each torque transmitter 6 to the respective drive input segment 3 also typically occurs via a shaft. Depending on the intended use and design of the drive unit 1 according to the invention, various types of torque transmitters 6 are possible. The torque transmitter 6 can be a rotationally fixed connection, for example, a rigidly connected shaft, or a chain or belt drive that enables the transmission of torque between differently arranged shafts.

[0043] Drive input segments 3 according to the invention serve to transmit the torques provided by the drives 15 via the torque transmitters 6 associated with them via at least one mechanical switching element to various components of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention, wherein each of these switching elements is connected via a shaft to at least one component of the planetary gear of the multi-start planetary gear that is not connected to the output shaft 11.5 of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention.

[0044] Through these mechanical switching elements, at least one drive 15 can be coupled via its associated torque transmitter 6 and the respective drive input segment 3 to a component of at least one planetary gear of the multi-start planetary gear, which is not connected to the output shaft 11.5 of the planetary gear.

[0045] The transmission of torque from the respective drive 15 to a component of a planetary gear set of the multi-start planetary gear set can also be effected directly via a shaft which can be coupled, via a mechanical switching element, in a rotationally fixed manner to the shaft of the component of the planetary gear set of the multi-start planetary gear set that is not connected to the output shaft 11.5 of the planetary gear set of the multi-start planetary gear set of the drive unit 1 according to the invention. In this case, the shaft connecting the respective drive 15 to the mechanical switching element in a rotationally fixed manner simultaneously constitutes a torque transmitter 6 and a drive input segment 3, including their respective shafts. Examples of this are shown in Fig. 1 with electric drives 15 as internal rotors and in Fig. 4 with electric drives 15 shown as external rotors.

[0046] According to the invention, the at least two drive input segments 3 can be coupled by at least one mechanical switching element. If the shaft connecting the respective drive to the mechanical switching element in a rotationally fixed manner is simultaneously a torque transmitter 6 and a drive input segment 3, including their respective shafts, they can be coupled in a rotationally fixed manner. If the transmission of torque from drive 15 to the drive input segment 3 takes place between differently arranged shafts, the coupling can be directly and rotationally fixed, as illustrated in Fig. 1 and Fig. 4, or also over several waves, as shown in Fig. 5.

[0047] The direct or indirect coupling of the drive input segments 3 by a mechanical switching element allows the total power of the at least two drives 15 to be distributed either to two components of a planetary gear set of the multi-start planetary gear set, namely ring gear 10, carrier gear 8, or sun gear 7, which are not connected to the output shaft 11.5 of the planetary gear set of the multi-start planetary gear set, or to drive only one component of a planetary gear set of the multi-start planetary gear set, namely ring gear 10, carrier gear 8, or sun gear 7, which is not connected to the output shaft 11.5 of the planetary gear set of the multi-start planetary gear set, by means of both drives 15. This serves to provide different gear ratios at the output shaft 11.5 of the planetary gear set of the multi-start planetary gear set of the drive unit 1 according to the invention.

[0048] If the torque transmitters 6 have a desired pre-reduction, for example by means of a belt drive, spur gears or chain gears, i.e., are to be used as a reduction gearbox, it is advantageous to arrange the position of the mechanical switching element, which serves to couple the drive input segments 3, at the point in the power flow where the lowest torque is present, in order to keep the manufacturing costs for this mechanical switching element as low as possible.

[0049] A planetary gear as a component of the multi-start planetary gear of the drive unit 1 according to the invention consists of at least one ring gear 10, a carrier gear 8 and a sun gear 7. One or more planet gears are attached to the carrier gear 8.

[0050] The components of a planetary gear system according to the invention are defined as the ring gear 10, the carrier gear 8 and the sun gear 7.

[0051] The planetary gear set can be arranged in a planetary gear housing rotatably mounted about the main axis 2 of the multi-start planetary gear set. This planetary gear housing can be a form of the shaft of the ring gear 10 of the respective planetary gear set. However, designs are also possible in which the planetary gear housing can be a form of other shafts from other components of the planetary gear set.

[0052] As principal axis 2 within the meaning of the invention, illustrated by way of example in Fig. 2, which represents the second embodiment, defines the axis of rotation of the sun gear 7 of the planetary gear of the multi-start planetary gear.

[0053] The axis of rotation of the sun gear 7 of the planetary gear of the multi-start planetary gear corresponds simultaneously to the axis of rotation of the drive input segments 3 of the drive unit 1 according to the invention.

[0054] According to the invention, the multi-start planetary gear of the drive unit 1 according to the invention has at least five mechanical switching elements.

[0055] Mechanical switching elements according to the invention are, according to the prior art, constructed from various connecting elements based on frictional engagement, positive engagement, or force-applied positive engagement and serve to block shafts and / or components of the planetary gear of the multi-start planetary gear, or to couple the drive input segments to each other in a rotationally fixed manner, directly or indirectly via several shafts, or to couple the drive input segments of the drive unit according to the invention with components of the planetary gear of the multi-start planetary gear of the drive unit according to the invention. 1. Mechanical switching elements according to the invention are required to change the transmission ratio of the drive unit according to the invention.State-of-the-art mechanical switching elements include, for example, brakes, friction clutches, overrunning clutches, backstops, claw clutches, pull wedges, tapered pulls, shift sleeves, synchronizer rings or locking devices.

[0056] A locking device 12 used as a mechanical switching element in the drive unit 1 according to the invention consists of at least one actuator 13a and at least two positive-locking connecting elements, namely the locking element 13b and the locking element 13c, wherein the positive locking of the locking elements 13b and 13c can be established or released by the actuator 13a. The positive locking of the locking elements 13b and 13c of a locking device 12 according to the invention can also be force-actuated. An exemplary embodiment of a locking device according to the invention is shown in Fig. 3 shown.

[0057] At least one locking element 13b or 13c is fixedly connected to at least one component of the planetary gear set of the multi-start planetary gear set, or to a shaft connected to a component of the planetary gear set, or to a drive input segment 3. The other locking element 13c or 13b is connected either to at least one other component of the planetary gear set of the multi-start planetary gear set, or to a shaft connected to another component of the planetary gear set, or to another drive input segment 3. One of the locking elements 13b or 13c may also be fixedly connected to the housing instead.

[0058] The establishment or release of the positive locking mechanism according to the invention is referred to as switching the locking device 12. When the positive locking mechanism of the locking elements 13b and 13c is released, the locking device 12 is open according to the invention. When the positive locking mechanism of the locking elements 13b and 13c is established, the locking device 12 is closed according to the invention.

[0059] In a closed locking device 12 according to the invention, a sufficiently large, customary clearance exists between the locking elements 13b and 13c of the locking device 12 in the switching position to allow the positive locking of the locking elements 13b and 13c to be released. This clearance results from the sufficiently large, customary gap dimension between the locking elements 13b and 13c when the locking device 12 is closed in the switching position.

[0060] A switching position within the meaning of the invention is defined by the relative position of the at least two locking elements 13b and 13c of the locking device 12. In the switching position, the locking elements 13b and 13c are arranged relative to each other, i.e., positioned, such that a positive locking connection can be established or an existing positive locking connection can be released by means of the actuator 13a. For this purpose, a sufficiently large, customary clearance between the locking elements 13b and 13c of the locking device 12 must exist in the positive locking state or can be established during the process of establishing the positive locking connection. This clearance results from the sufficiently large, customary gap dimension between the locking elements 13b and 13c. The switching position of the locking elements 13b and 13c of a locking device 12 is a prerequisite for switching the respective locking device 12.

[0061] To change the transmission ratio of the drive unit 1 according to the invention, i.e., to change the gears of the multi-stage planetary gear, it is necessary to establish temporary rotationally fixed connections between various rotatable and rotating shafts, to block shafts to the housing, and to couple the drive input segments 3 directly or indirectly via several shafts using mechanical switching elements. The mechanical switching elements are switched in the usual manner.

[0062] The operation of the drive unit 1 according to the invention, and in particular the change in the transmission ratio of the drive unit 1 according to the invention, can be carried out in such a way that there is no interruption of the train at any time. Thus, the drive unit 1 according to the invention is capable of load shifting. This is ensured by the fact that during a shifting operation, i.e., gear change, the torque of at least one of the at least two drive input segments 3.1, 3.2 of the drive unit 1 according to the invention, provided via at least one of the at least two drives 15, is always available to drive a component of a planetary gear set of the multi-start planetary gear set.

[0063] The multi-stage planetary gearbox can be extended with additional gearboxes or planetary gearboxes for appropriate applications.

[0064] If the multi-start planetary gear unit has more than one planetary gear unit, the drive unit 1 according to the invention can be operated without increasing the number of drive input segments and the number of their drives 15. By extending the multi-start planetary gear unit with further planetary gear units, the number of different gear ratios of the multi-start planetary gear unit can also be increased.

[0065] By using additional mechanical switching elements and with increased design effort, the number of different gear ratios, i.e. gears, can be increased even when using only one planetary gear in a multi-gear planetary gearbox.

[0066] The invention relates to a drive unit 1 that can be used to drive vehicles or other technical devices or machines that convert supplied energy from various energy forms into kinetic energy and provide this as rotary motion at specific torques and speeds. According to the invention, the total power of the drive unit 1 is distributed to various drive input segments 3.1, 3.2, and thus to various components of a planetary gear set of the multi-start planetary gear set.

[0067] The invention comprises at least two drives 15, at least one housing in which at least two drive input segments 3 arranged coaxially to the main axis 2 are arranged, each drive input segment 3 having at least one torque transmitter 6, a multi-start planetary gear comprising at least one planetary gear arranged coaxially to the main axis 2, comprising at least one ring gear 10, a carrier gear 8, a sun gear 7 and an output shaft 11.5, and at least five mechanical switching elements, wherein the sun gear 7, the carrier gear 8 or the ring gear 10 is rotationally fixed to the output shaft 11.5.

[0068] In this arrangement, each torque transmitter 6 and the drive input segment 3 connected to the torque transmitter 6 is assigned at least one drive 15, the at least two drive input segments 3 can be coupled to each other by at least one mechanical switching element, each of the at least two drive input segments 3 can be coupled separately and without rotation to at least one component of at least one planetary gear set of the multi-start planetary gear set, namely ring gear 10, carrier gear 8 or sun gear 7, by a mechanical switching element, wherein the at least two drive input segments 3 can be coupled to different components of at least one planetary gear set of the multi-start planetary gear set, namely either to sun gear 7 and carrier gear 8 or to sun gear 7 and ring gear 10 or to carrier gear 8 and ring gear 10, which are not connected to the output shaft 11.5 of the planetary gear of the multi-start planetary gear, are connected, are couplingable, the two components of at least one planetary gear of the multi-start planetary gear, which are not connected to the output shaft 11.5, namely either the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, are each lockable in at least one direction of rotation by at least one mechanical switching element which has a fixed connection with the housing, and the drives 15 of the drive input segments 3 are independently usable both for driving the multi-start planetary gear and in conjunction with the mechanical switching elements for changing the transmission ratio of the drive unit 1.

[0069] The drive input segments 3, in conjunction with at least two drives 15, are used to drive the planetary gear of the multi-start planetary gear. Because the drive input segments 3 can be directly coupled to each other via their shafts in a rotationally fixed manner, or indirectly coupled via several shafts using a mechanical switching element, the power flow in the multi-start planetary gear can be branched during operation of the drive unit 1 according to the invention, using further existing mechanical switching elements. The power flow can be branched in at least three different ways.If the drive input segments 3 are coupled via their shafts by a mechanical switching element, they can, depending on the switching state of the mechanical switching elements downstream of their shafts, either jointly drive a component of a planetary gear set that is rotationally fixed to one drive input segment 3 via a mechanical switching element (namely, ring gear 10, carrier gear 8, or sun gear 7) of the multi-start planetary gear set, or drive a component of a planetary gear set of the multi-start planetary gear set that is rotationally fixed to the other drive input segment 3 via a mechanical switching element. If the drive input segments 3 are not coupled via their shafts by a mechanical switching element, they can drive different components of a planetary gear set of the multi-start planetary gear set independently of each other.Furthermore, in this state of branching of the power flow, i.e. in the course of the power branching in the drive unit according to the invention, it is also possible to use one drive input segment 3 to drive a component of a planetary gear of the multi-start planetary gear and the second drive input segment 3 to support the gear change, i.e. change of the transmission ratio of the drive unit 1 according to the invention.

[0070] Various possible embodiments of the drive unit 1 according to the invention, shown in columns 1 to 3 of Table 1, with respect to the number of planetary gears of the multi-start planetary gear, the number of drives 15 and the number of drive input segments 3, are represented with a spread as shown in column 5 of Table 1. Table 1 Number of planetary gears Number of drives Number of drive input segments Number of sensible aisles Spread 1 2 2 3 2,618 2 2 2 5 6,85

[0071] Furthermore, in embodiments of the drive unit 1 according to the invention, it is particularly advantageous that the ratio of the number of teeth of the sun gear 7 of a planetary gear set of the multi-start planetary gear set to the number of teeth of the ring gear 10 of the same planetary gear set of the multi-start planetary gear set is preferably determined to be 1 to 1.618. This is particularly advantageous because none of the step increments of the multi-start planetary gear set is greater than 1.618. In addition, gear sets of the planetary gear set with approximately equal step increments are provided, and the step increments are distributed approximately evenly across the range of the multi-start planetary gear set between the lowest and the highest gear.Since achieving an exact ratio of 1 to 1.618 between the number of teeth of sun gear 7 of a planetary gear set and the number of teeth of ring gear 10 of the same planetary gear set can only be accomplished with correspondingly high numbers of teeth for sun gear 7 and ring gear 10 of the planetary gear set, the design should aim for a ratio of teeth for sun gear 7 and ring gear 10 that comes as close as possible to this ratio with the lowest possible number of teeth.

[0072] The number of possible switchable gears, i.e., different transmission ratios available through the drive unit 1 according to the invention, for various possible embodiments of the invention are listed in column 4 of Table 1. The information regarding the number of switchable gears and the range of the different embodiments of the multi-start planetary gear set of the drive unit 1 according to the invention, shown in column 5 of Table 1, refers to a configuration of the multi-start planetary gear set consisting of planetary gear sets in which the ratio of the number of teeth of the sun gear 7 to the number of teeth of the ring gear 10 of the first simple planetary gear set is approximately 1 to 1.618.

[0073] Furthermore, in embodiments of the drive unit 1 according to the invention with a multi-start planetary gear, comprising a first planetary gear in which the ratio of the number of teeth of sun gear 7 to the number of teeth of ring gear 10 is preferably determined as 1 to 1.618, it is particularly advantageous in order to fully utilize the total power of the drive unit 1 according to the invention that the distribution of the drive power of the drives 15 to the drive input segments 3 of the drive unit 1 according to the invention, in an embodiment with two drives 15, takes place in a specific ratio, listed in Table 2. Table 2 first drive second drive calculated share of the total power output of the drives ~61,8% ~38,2%

[0074] One embodiment of the drive unit 1 according to the invention, as listed in Table 1, line 2, enables the transmission ratios and step jumps between the gears shown in Table 3.

[0075] The size of the step increments between the gears corresponds approximately to 1.618. Overall, this results in a spread for the multi-start planetary gear of the drive unit 1 according to the invention, as shown in Table 1, line 2, of approximately 6.85. Table 3 aisle Translation ratio Step jump to the next course 1 1 to ~0.146 ~1,618 2 1 to ~0.236 ~1,618 3 1 to ~0.382 ~1,618 4 1 to ~0.618 ~1,618 5 1 to 1

[0076] If higher torques of the drive unit 1 according to the invention are required with the same total power of the drives of the drive unit 1 according to the invention, the drive unit 1 according to the invention can be extended with further planetary gears or other gears according to the prior art.

[0077] In order to support the ring gear 10 of a planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention and at the same time to keep the necessary amount of lubricant low during the operation of the multi-start planetary gear, it is particularly advantageous to encapsulate the planetary gear within the housing of the drive unit 1 according to the invention in a lubricant-tight planetary gear housing.

[0078] Such a function can be implemented by adding state-of-the-art components that provide the functionality of a parking lock.

[0079] The application areas of the drive unit 1 according to the invention, in its various forms, are manifold. For example, the drive unit 1 according to the invention can be used economically in motor vehicles, rail vehicles, aircraft, and watercraft, as well as in machine tools or wind and hydroelectric power plants (in which case it uses electrically driven drives 15, functioning as a generator), or in other technical devices or machines that convert electrical energy into kinetic energy and provide it as rotary motion at specific torques and speeds. The invention also relates to a drive unit 1 which, if used as a planetary gear-supported generator according to the prior art, can convert kinetic energy into electrical energy.

[0080] According to the invention, the at least two drives 15 of the drive input segments 3 are electrically operable, the drive unit 1 comprises at least one electronic main control unit, and the electrically operable drives 15 of the drive input segments 3 can be used independently of one another both for driving the multi-start planetary gear and in conjunction with the mechanical switching elements and the electronic main control unit for changing the transmission ratio of the drive unit 1.

[0081] Advantageously, the drive unit 1 according to the invention can be operated by electrically powered drives 15. For this purpose, the use of an electronic main control unit is advantageous. This unit controls and regulates the electric drives 15, which can be used both to drive the components of a planetary gear set of the multi-start planetary gear set, namely with ring gear 10, carrier gear 8 or sun gear 7, and, in conjunction with the mechanical switching elements, to change the transmission ratio of the drive unit 1. The control of these at least two electric drives 15 is carried out independently of each other by the electronic main control unit. The main electronic control unit is connected to the stators of the electric drives 15.

[0082] An electric drive 15 or electrically operable drive 15 within the meaning of the invention is to be understood as a conventional electric motor consisting of at least one rotor 5 and at least one stator 4.

[0083] An electronic main control unit within the meaning of the invention is an electronic measuring and control unit comprising at least one central numerical electronic processing unit and conventional sensor units connected via communication links. It collects and evaluates information, in particular values ​​of physical quantities, from these sensor units and the conventional electronic control units, which serve to control and regulate the electrically generated magnetic fields between the stators 4 and their respective associated rotors 5 of the electric drives 15, and thereby monitors, controls, and regulates these electronic control units in a conventional, programmatically controlled manner. It also coordinates the control functions of the electronic control units, controls and regulates the electric current flowing to the stators 4 of the electric drives 15, and thus the speed of the output shaft 11.The electronic main control unit controls, regulates, and monitors both the output shaft 5 and the torques provided at the output shaft 11.5. Thus, according to the invention, the electronic main control unit controls, regulates, and monitors the drive of the multi-start planetary gear and, consequently, also the drive of the output shaft 11.5 of the multi-start planetary gear of the drive unit 1 according to the invention. Furthermore, the electronic main control unit also determines torques acting on the output shaft from the multi-start planetary gear, as well as torques acting in the opposite direction in the power flow, which act on the output shaft of the multi-start planetary gear from outside the housing.

[0084] The main electronic control unit may also integrate other common electronic control units.

[0085] An electronic main control unit according to the invention can have one or more conventional communication inputs for receiving control signals or control commands for the purpose of externally controlling the operation of the drive unit 1 according to the invention. An electronic main control unit according to the invention contains at least one conventional program code which, taking into account the available information, in particular values ​​of physical quantities, determines the rotational speed and direction of rotation of the output shaft 11 from sensor units.5 of the planetary gear of the multi-start planetary gear, the output shaft of the multi-start planetary gear and the output shaft of the drive unit 1 according to the invention in a conventional manner and, if the main electronic control unit has one or more communication inputs, evaluates incoming control signals or control commands via these communication inputs and uses them for the control and regulation of speed and direction of rotation of the output shaft 11.5 of the planetary gear of the multi-start planetary gear, the output shaft of the multi-start planetary gear and the output shaft of the drive unit 1 according to the invention.

[0086] A sensor unit according to the invention is a technical component that detects physical quantities such as rotational speed, direction of rotation, angular position, and torque of a component of the planetary gear or of a rotor 5 or the output shaft 11.5 of the planetary gear of the multi-start planetary gear or of a component non-rotatably connected to the output shaft 11.5 of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention using physical, chemical, or biological effects in a conventional manner and can transmit this information via a conventional communication link in the main electronic control unit to other electronic assemblies or devices or other connected control units for processing and evaluation. A sensor unit according to the invention can also serve to detect information, in particular values ​​of physical quantities, regarding the inclination, orientation, and position of the drive unit 1 according to the invention in space.

[0087] The sensor units of the main control unit are arranged in such a way that the speed, direction of rotation and angular position of the rotors 5 of the electric drives 15 and the drive input segments 3 and the components of the planetary gear of the multi-start planetary gear and the output shaft 11.5 of the planetary gear of the multi-start planetary gear, the output shaft of the multi-start planetary gear and the output shaft of the drive unit 1 according to the invention can be determined by the electronic main control unit in the usual manner.

[0088] For optimization purposes, it can also be advantageous for the electronic main control unit to additionally determine, evaluate, and use for controlling the operation and changing the transmission ratio of the drive unit 1 according to the invention by means of sensor units in the usual manner, the speed, direction of rotation and angular position and also the torque of further assemblies downstream of the drive unit 1 according to the invention with regard to the power flow.

[0089] In this patent application, speed, direction of rotation, angular position and torque always refer to the housing of the drive unit 1 according to the invention as a reference point, unless another reference point is expressly defined.

[0090] The control and regulation of the current flowing between the electrical energy source and the stators 4 of the electric drives 15 is carried out in the usual manner by electronic control units, in particular by the main electronic control unit, and serves in the usual manner to drive the planetary gear of the multi-start planetary gear and thus also to drive the output shaft 11.5.

[0091] The operation of the drive unit 1 according to the invention, and in particular the changing of the transmission ratio of the drive unit 1 according to the invention, can be carried out in such a way that there is no interruption of the train at any time. Thus, the drive unit 1 according to the invention is capable of load switching. This can be ensured by the electronic main control unit, which programmatically ensures that at least one rotor 5 of an electric drive is always connected via a detachable, rotationally fixed connection via a torque transmitter 6 and a drive input segment 3 to a component of the planetary gear unit or to a shaft which is non-rotatably connected to a component of the planetary gear and is driven by the electric drive 15.

[0092] The existing conventional mechanical switching elements of the drive unit 1 according to the invention can be controlled and / or regulated in the usual manner by the main electronic control unit and, if present, other conventional control units.

[0093] According to the invention, the mechanical switching elements of the at least five mechanical switching elements, by which the at least two drive input segments 3 can be coupled in a rotationally fixed manner to the components of the planetary gear of the multi-start planetary gear that are not connected to the output shaft 11.5, namely either to the sun gear 7 and the carrier gear 8 or to the sun gear 7 and the ring gear 10 or to the carrier gear 8 and the ring gear 10, are locking devices 12, wherein the at least two electrically operated drives 15 of the drive unit 1 in conjunction with the electronic main control unit can be used for positioning the positive locking elements 13b and 13c of the locking devices 12 and wherein the at least two electrically operated drives 15 of the drive unit 1 in conjunction with the electronic main control unit can be used to hold the switching position of the positive locking elements 13b and 13c of the locking devices 12.

[0094] In the drive unit 1 according to the invention, schematically in the first embodiment in Fig. 1, in the second embodiment as a partial view schematically in Fig. 2 shown, schematically in the third embodiment Fig. 4 and in the fourth embodiment schematically in Fig.As shown in Figure 5, the multi-start planetary gear unit is driven by electric drives 15. The main electronic control unit is connected to the stators 4 of the electric drives 15 and the locking devices 12. The total electrical power available for operating the drive unit 1 is distributed between the two electric drives 15. Stator 4.1 of one electric drive 15 drives rotor 5.1, and stator 4.2 of the other electric drive 15 drives rotor 5.2. The torque from rotor 5.1 and rotor 5.2 is transmitted via at least one torque transmitter 6 each to the at least two drive input segments 3, which in turn are each rotationally fixed via at least one mechanical switching element to a shaft with at least one component of a planetary gear unit of the multi-start planetary gear unit, which is not connected to the output shaft 11.5 of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention is connected, and each can be locked by a further mechanical switching element which has a fixed connection with the housing, and can be coupled in a rotationally fixed manner.

[0095] In the first, second and third embodiments, the shafts 11.2 and 11.3, which can be coupled in a rotationally fixed manner to the shafts of the respective components of the planetary gear of the multi-start planetary gear, which are not connected to the output shaft 11.5 of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention, via mechanical switching elements, namely the locking devices 12.2 and 12.4, are simultaneously torque transmitters 6 and drive input segments 3, thus equally assuming their function.

[0096] In the fourth embodiment, shown in Fig.5, the torque transmitters 6, the drive input segments 3 and the shafts 11.2 and 11.3 are designed as separate mechanical components, whereby the torque transmitters 6 can transmit the respective torques from the respective shafts 11.6 and 11.7 of the respective drive 15 to the shafts 11.2 and 11.3 of the drive input segments 3, since in the fourth embodiment the axes of rotation, namely the shafts 11.6 and 11.7, of the drives 15 do not lie on the main axis 2 of the drive unit 1 according to the invention.

[0097] The mechanical switching elements of the at least five mechanical switching elements of the drive unit 1 according to the invention, by which the at least two drive input segments 3 can be coupled in a rotationally fixed manner to the components of the planetary gear of the multi-start planetary gear that are not connected to the output shaft 11.5 of the planetary gear of the multi-start planetary gear, namely either to the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, are locking devices 12 in the sense of the invention.

[0098] To change the transmission ratio of the drive unit 1 according to the invention, i.e., to change the gears of the multi-start planetary gear, it is necessary to create temporary rotationally fixed connections between various rotatable and rotating shafts. Locking devices 12 according to the invention are suitable for this purpose.

[0099] The interaction of the electronic main control unit and the two electrically operated drives 15 establishes and holds the switching position of the locking elements 13b and 13c of the locking devices 12 according to the invention in preparation for switching the locking devices 12. The electronic main control unit, which in particular includes a central electronic computing unit and has conventional electrical connections or conventional control and communication connections to the locking devices 12, also controls, regulates, actuates and monitors the actuator 13a, which switches the respective locking device 12 according to the invention.

[0100] The remaining conventional mechanical switching elements of the drive unit 1 according to the invention, which are not locking devices 12 within the meaning of the invention, can be controlled and / or regulated in the usual manner by the main electronic control unit and, if present, other conventional control units.

[0101] The main electronic control unit is connected to the locking devices 12; it controls, regulates and monitors the modulation of the electric current flowing to the stators 4 of the electric drives 15 and thus both the change in the transmission ratios of the drive unit 1 according to the invention and its individual switching phases as well as the recuperation and the speed of the output shaft 11.5 of the planetary gear of the multi-start planetary gear as well as the torques provided at the output shaft 11.5.

[0102] Thus, the electronic main control unit according to the invention can control, regulate and monitor the process of changing the transmission ratio of the drive unit 1 according to the invention in a conventional manner using program control.

[0103] The modulation of the flowing electric current within the meaning of the invention is defined as the program-controlled modification of the flowing electric current to a stator 4 of an electric drive 15 of the drive unit 1 according to the invention, by the main electronic control unit or by other conventional electronic control units which are controlled and regulated by the main electronic control unit. Within the meaning of the invention, the modulation of the flowing electric current to a stator 4 refers exclusively to the modification of the flowing electric current to the stator 4 for the purpose of establishing and maintaining the switching position of the locking elements 13b and 13c of the locking devices 12 according to the invention in preparation for switching the locking devices 12, which in turn is a subprocess of changing the transmission ratio of the drive unit 1 according to the invention.

[0104] The modulation according to the invention is either pulse width modulation, frequency modulation, amplitude modulation, the application of direct currents or a mixture of these in the usual manner.

[0105] The modulation of the flowing electric current to a stator 4, controlled in the usual manner by the electronic main control unit, serves, in accordance with the invention, to control and regulate the associated rotor 5 of the respective electric drive 15.

[0106] The control and regulation of a rotor 5 is carried out by means of modulation in accordance with the invention and includes the change of speed, i.e. increasing or decreasing the speed, the positioning, holding the position and reversing the direction of rotation of the rotor 5 and thus at least one locking element 13b, 13c of a locking device 12 connected via a rotationally fixed connection.

[0107] Independently of the modulation of the flowing electric current in accordance with the invention, the control and regulation of the flowing electric current to the stators 4 of the electric drives 15 by the electronic main control unit also serves in the usual manner to drive the planetary gear of the multi-start planetary gear and thus also the drive of the output shaft 11.5 of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention.

[0108] The energy required for switching the locking devices 12 is supplied in the usual manner via electrical conductors and is controlled, regulated, and monitored by the main electronic control unit or by conventional electronic control units controlled, regulated, and monitored by the main electronic control unit. The transmission path for the energy required to switch the locking devices 12 is also used for bidirectional communication between the main electronic control unit or by conventional electronic control units controlled, regulated, and monitored by the main electronic control unit and the locking devices 12.

[0109] To establish and hold the switching position of the locking elements 13b and 13c of the locking devices 12 according to the invention in preparation for switching the locking devices 12, the at least two electric drives 15 of the drive unit 1 according to the invention are used, which are also used to drive the drive unit 1 according to the invention.These electric drives 15, each consisting of at least one stator 4 and one rotor 5, are controlled by the main electronic control unit according to the invention, which collects and evaluates information, in particular values ​​of physical quantities, from conventional sensor units and conventional electronic control units via communication links. This information is used to control and regulate the electrically generated magnetic fields between the stators 4 and their respective associated rotors 5. The main electronic control unit monitors, controls, and regulates these electronic control units in a program-controlled manner and coordinates, controls, and regulates the control functions of the electronic control units.

[0110] Using information, in particular values ​​of physical quantities, from the sensor units of the electronic main control unit and information, in particular values ​​of physical quantities, from control units optionally integrated into or connected to it, the electronic main control unit determines or derives information and data, in particular values ​​of physical quantities, on at least the rotational speed, direction of rotation and angular position of the rotors 5 of the electric drives 15 and the components of the planetary gear of the multi-start planetary gear, and determines or derives information, in particular values ​​of physical quantities, on the rotational speed, direction of rotation and applied torque at the output shaft 11.5 of the planetary gear of the multi-start planetary gear, the output shaft of the multi-start planetary gear and the output shaft of the drive unit 1 according to the invention.Using this information, in particular values ​​of physical quantities, the electronic main control unit can programmatically derive the relative positions of the at least two positive-locking locking elements 13b and 13c of the respective locking device 12. From this, the electronic main control unit, if necessary, controls and regulates the electric drives 15 of the drive unit 1 according to the invention such that, if the relative position of the components of the locking devices 12 does not correspond to the switching position and this switching position is required, the components of the respective locking device 12 are moved relative to each other so that they assume and maintain the switching position.

[0111] The at least two electric drives 15 of the drive unit 1 according to the invention can be used in conjunction with the electronic main control unit both for positioning the positive locking elements 13b and 13c of the locking devices 12 and for holding the switching position of the positive locking elements 13b and 13c of the locking devices 12 even when the output shaft 11.5 is rotating.

[0112] During the different phases of the gear changes of the drive unit 1 according to the invention, i.e., the change in the transmission ratio of the drive unit 1 according to the invention, states can occur in which both electric drives 15 are used simultaneously to establish and hold the switching position of the locking elements 13b and 13c of the locking devices 12 according to the invention in preparation for switching the locking devices 12, but at the same time one of the electric drives 15 is used to drive the multi-start planetary gear.

[0113] The transmission ratio of the drive unit 1 can be changed in the interaction of rotors 5 and stators of the electric drives 15, the locking devices 12 and the main electronic control unit.

[0114] Sensor units connected via communication links are integrated into the main electronic control unit.

[0115] The use and arrangement of the locking devices 12 according to the invention results in a reduction of the size compared to the prior art and a reduction in the manufacturing costs of the drive unit 1.

[0116] It is further preferred that the mechanical switching elements of the at least five mechanical switching elements, by which the two components of at least one planetary gear of the multi-start planetary gear, which are not connected to the output shaft 11.5, namely either the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, can be locked, are locking devices 12.

[0117] According to the invention, the drive unit 1 has at least five mechanical switching elements.

[0118] By using at least four locking devices 12 as mechanical switching elements, namely as those by which the at least two drive input segments 3 can be coupled in a rotationally fixed manner to the components of the planetary gear of the multi-start planetary gear that are not connected to the output shaft 11.5, namely either to the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, and as those by which the two components of at least one planetary gear of the multi-start planetary gear that are not connected to the output shaft 11.5 are connected, namely either the sun gear 7 and the carrier gear 8 or the sun gear 7 and the ring gear 10 or the carrier gear 8 and the ring gear 10, and can be locked, the overall efficiency of the drive unit 1 according to the invention is increased by reducing the friction losses, which are caused by drag losses when using exclusively force-fit mechanical switching elements.

[0119] The use of these at least four locking devices 12, as defined in the invention, with at least five required mechanical switching elements for changing the transmission ratio of the drive unit 1 according to the invention—i.e., for shifting gears—represents an advantageous compromise between short switching times, size, and thermal load of the drive unit 1 on the one hand, and longer switching times with lower thermal load and size of the drive unit 1 on the other. Furthermore, the use of locking devices 12 according to the invention reduces the manufacturing costs for the drive unit 1 according to the invention. The position of these at least four mechanical switching elements, designed as locking devices 12 according to the invention, is advantageous due to the design and leads to a further reduction in the manufacturing costs of the drive unit 1 according to the invention.

[0120] A distinction must be made between locking devices 12 according to the invention, which block components of the planetary gear of the multi-start planetary gear or shafts non-rotatably connected to them against the housing in the usual manner, and locking devices 12, which can establish a releasable non-rotatable connection between rotating or rotatable components of the planetary gear, namely ring gear (10), carrier gear (8) or sun gear (7), or the shafts of the rotors 5 of the electric drives 15. These locking devices 12 according to the invention differ essentially only in their function and not in their construction.

[0121] A locking element 13b, 13c of a locking device 12, in particular its alignment for the purpose of reaching and holding the switching position, which is the prerequisite for carrying out the switching of the locking device 12, is controlled and regulated via the rotors 5 of the electric drives 15 by means of an existing rotationally fixed connection, which may also be provided by means of further closed locking devices 12.

[0122] The use and arrangement of the locking devices 12 according to the invention further reduces the size of the drive unit 1 compared to the prior art. Moreover, the use of locking devices 12 according to the invention enables recuperation at all different transmission ratios provided by the drive unit 1. Furthermore, the use of the locking devices 12 also allows for a reversal of the direction of rotation of the output shaft 11.5, and thus of the output shaft of the multi-start planetary gear, and therefore also of the output shaft of the drive unit 1, at all transmission ratios available from the drive unit 1.

[0123] The use of locking devices 12 according to the invention reduces the thermal stress during switching operations. The more complex design of, for example, switching elements such as brakes, the technical effort required for their control, and the increased maintenance effort all increase manufacturing costs, lead to larger sizes, and result in higher production costs.

[0124] The fifth mechanical switching element, which serves to couple the at least two drive input segments 3 in a rotationally fixed manner, is a mechanical switching element according to the state of the art, for example a friction clutch 23, shown in Fig. 5.

[0125] It is further preferred that the at least five mechanical switching elements are locking devices 12.

[0126] By using at least five locking devices 12 according to the invention with at least five required mechanical switching elements, the thermal stress caused by the mechanical switching elements is reduced to the lowest possible level. Furthermore, locking devices 12 according to the invention can be implemented in a smaller size than conventional mechanical switching elements and exhibit a lower degree of wear. The switching times are slightly increased by using at least five locking devices 12 according to the invention. Depending on the application of the drive unit 1 according to the invention, this represents an advantageous compromise between higher thermal stress and shorter switching times of the drive unit 1 according to the invention.

[0127] Furthermore, the preferably use of locking devices 12 in accordance with the invention makes it possible to reduce the weight and size of the drive unit 1 according to the invention.

[0128] Various possible embodiments of the drive unit 1 according to the invention, shown in columns 1 to 3 of Table 4, with respect to the number of rotors and stators of the electric drives 15 and planetary gears, exhibit a spread as shown in column 5 of Table 4. Row 1 of Table 4 lists the first embodiment of the drive unit 1 according to the invention, which is described later in the explanation. Table 4 Number of planetary gears Number of stators Number of rotors Number of useful courses Spread 1 2 2 3 2,618 2 2 2 5 6,85

[0129] Furthermore, in embodiments of the drive unit 1 according to the invention, it is particularly advantageous that the ratio of the number of teeth of the sun gear 7 of a planetary gear set of the multi-start planetary gear set to the number of teeth of the ring gear 10 of the same planetary gear set of the multi-start planetary gear set is preferably determined to be 1 to 1.618. This is particularly advantageous because none of the step increments of the multi-start planetary gear set is greater than 1.618. In addition, gear sets of the planetary gear set with approximately equal step increments are provided, and the step increments are distributed approximately evenly across the range of the multi-start planetary gear set between the lowest and the highest gear.Since achieving an exact ratio of 1 to 1.618 between the number of teeth of sun gear 7 of a planetary gear set and the number of teeth of ring gear 10 of the same planetary gear set can only be accomplished with correspondingly high numbers of teeth for sun gear 7 and ring gear 10 of the planetary gear set, the design should aim for a ratio of teeth for sun gear 7 and ring gear 10 that comes as close as possible to this ratio with the lowest possible number of teeth.

[0130] The number of meaningfully switchable gears for various possible embodiments of the invention are listed in column 4 of Table 4. The information regarding the number of meaningfully switchable gears and the specification of the gear ratios of the various embodiments of the multi-start planetary gear of the drive unit 1 according to the invention, shown in column 5 of Table 4, refer here to a configuration of the multi-start planetary gear consisting of planetary gears in which the ratio of the number of teeth of the sun gear 7 to the number of teeth of the ring gear 10 of the first simple planetary gear is approximately 1 to 1.618.

[0131] Furthermore, in embodiments of the drive unit 1 according to the invention with a multi-start planetary gear, comprising a first planetary gear in which the ratio of the number of teeth of sun gear 7 to the number of teeth of ring gear 10 is preferably determined as 1 to 1.618, it is particularly advantageous in order to fully utilize the total installed electrical rated power of the electric drives 15 of the drive unit 1 according to the invention that the distribution of the electrical power of the drive unit 1 according to the invention, in an embodiment with two electric drives 15, to two stators 4 takes place in a specific division ratio, listed in Table 5. Table 5 First electric drive Second electric drive calculated share of the total power of the drives ~61,8% ~38,2%

[0132] One embodiment of the drive unit 1 according to the invention, as listed in Table 4, line 2, enables the transmission ratios and step jumps between the gears shown in Table 6.

[0133] The size of the step increments between the gears corresponds approximately to 1.618. Overall, this results in a spread for the multi-start planetary gear of the drive unit 1 according to the invention, as shown in Table 4, line 2, of approximately 6.85. Table 6 aisle Translation ratio Step jump to the next course 1 1 to ~0.146 ~1,618 2 1 to ~0.236 ~1,618 3 1 to ~0.382 ~1,618 4 1 to ~0.618 ~1,618 5 1 to 1

[0134] If the drive unit 1 according to the invention is to be used for operating a motor vehicle, it is economically advantageous to use only locking devices 12 as defined in the invention in the design of the drive unit 1 according to the invention, and not other conventional mechanical switching elements, in order to reduce the design effort. However, the functionality of a parking lock, if required, must then be implemented by extending the drive unit 1 according to the invention with components according to the prior art that provide the function of a parking lock.

[0135] Extending the clearance between the positive locking elements 13b, 13c of the locking devices 12 in a radial direction, i.e. in or against the direction of rotation of the positive locking elements 13b, 13c of the locking devices 12, beyond the sufficiently, customarily dimensioned dimension, can be advantageous for reducing the switching times of the locking devices 12 and thus with regard to reducing the time required for changing the transmission ratio.

[0136] If a reversal of the direction of rotation is required at the output shaft 11.5, the output shaft of the multi-start planetary gear and the output shaft of the drive unit 1, which is the case, for example, in motor vehicles with a reverse gear, this functionality can be provided with the drive unit 1 according to the invention by reversing the direction of rotation of the drive input segments 3 by means of the electric drives 15 via an electronic control unit.

[0137] If higher torques of the drive unit 1 according to the invention are required with the same total electrical power of the electric drives 15 of the drive unit 1 according to the invention, the drive unit 1 according to the invention can be extended with further planetary gears or other gears according to the prior art.

[0138] In order to support the ring gear 10 of a planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention and at the same time to keep the necessary amount of lubricant low during the operation of the multi-start planetary gear, it is particularly advantageous to encapsulate the planetary gear within the housing of the drive unit 1 according to the invention in a lubricant-tight planetary gear housing.

[0139] When using the drive unit 1 according to the invention, for example in motor vehicles, it is also advantageous to generate the electrical energy required for the operation of the electric drives 15 of an embodiment of the drive unit 1 according to the invention by means of a generator driven by an internal combustion engine and / or, if required, to temporarily store it in an energy storage device and then use it to drive the drive unit 1 according to the invention.

[0140] The application areas of the drive unit 1 according to the invention, in its various forms, are manifold. In particular, the drive unit 1 according to the invention can be used economically in versions with electrically driven drives 15 in motor vehicles, rail vehicles, aircraft, and watercraft, but also in machine tools or wind or hydroelectric power plants, in which case it functions as a generator, or in other technical devices or machines that convert electrical energy into kinetic energy and provide it as rotary motion at specific torques and speeds. The invention also relates to a drive unit 1 which, if used as a planetary gear-supported generator according to the prior art, can convert kinetic energy into electrical energy.

[0141] It is further preferred that a delay unit 26 is arranged on the output shaft of the multi-start planetary gear.

[0142] A delay unit 26 according to the invention is a mechanical component which is arranged in relation to the output shaft of the multi-start planetary gear of the drive unit 1 according to the invention in such a way that it transmits mechanical forces acting from outside the housing towards the output shaft 11.5 and thus towards the components of the planetary gear of the multi-start planetary gear to the output shaft 11.5 of the planetary gear of the multi-start planetary gear of the drive unit 1 according to the invention with a time delay and thereby compensates for or at least weakens torque fluctuations in the usual manner in order to ensure the controllability of the locking devices 12 for the purpose of switching the locking devices 12 and thus for the purpose of changing the transmission ratio of the drive unit 1 according to the invention.

[0143] Dynamically changing torques on the output shaft 11.5 can be caused by mechanical forces acting on the output shaft 11.5 from outside the housing. This can prevent the positive locking of the two positive locking elements 13b and 13c of the locking device 12 from being established or released. This can occur particularly when the drive unit 1 according to the invention is used in motor vehicles employed in agriculture, especially when these vehicles are driven on very uneven terrain.

[0144] A further preferred method is for operating and changing the transmission ratio of a drive unit 1, in which the electrically operated drives 15 of the drive input segments 3 are used independently of one another both for driving the multi-start planetary gear and, in conjunction with the mechanical switching elements and the electronic main control unit, for changing the transmission ratio of the drive unit 1, wherein the at least two electrically operated drives 15 of the drive unit 1, in conjunction with the electronic main control unit, can be used for positioning the positive locking elements 13b and 13c of the locking devices 12, and wherein the at least two electrically operated drives 15 of the drive unit 1, in conjunction with the electronic main control unit, are used to hold the switching position of the positive locking elements 13b and 13c of the locking devices 12.

[0145] To change the transmission ratio of the drive unit 1 according to the invention, certain switching processes must be carried out, which consist of switching various mechanical switching elements and locking devices 12 in a specific sequence. An electronic main control unit according to the invention is used to control, regulate, and monitor the execution of these processes. The electronic main control unit collects and evaluates information, in particular values ​​of physical quantities, from sensor units via communication links and, based on this, controls, regulates, and monitors the switching processes.The main electronic control unit controls, regulates and monitors, with the aid of information from sensor units, in particular regarding values ​​of physical quantities, the interaction between the stators 4, the rotors 3 and the locking devices 12, in order to change the transmission ratio of the drive unit 1 according to the invention when the output shaft 11.5 is rotating.

[0146] The control, regulation and monitoring of the electrically operated drives 15 of the multi-start planetary gearbox is carried out using information from sensor units, in particular values ​​of physical quantities, which are collected and evaluated programmatically via communication links.

[0147] By reversing the direction of rotation of the rotors 3 by means of controlling the respective assigned stator 4 for the purpose of driving the multi-start planetary gear of the drive unit 1 according to the invention, the direction of rotation of the output shaft 11.5 can also be reversed and the transmission ratio of the drive unit 1 according to the invention can be changed when the direction of rotation of the output shaft 11.5 is reversed.

[0148] This method is necessary for operating a drive unit 1 according to the invention, since conventional methods cannot be used due to the mechanical design of the drive unit 1 according to the invention. The method is advantageous compared to the prior art because the electric drives are used both to drive the multi-start planetary gear and, in conjunction with the mechanical switching elements and the electronic main control unit, to change the transmission ratio of the drive unit 1. This renders a complex hydraulic or other conventional control system obsolete, at least with regard to the locking devices 12 according to the invention.

[0149] The at least two electrically operated drives 15 of the drive unit 1 are used in conjunction with the electronic main control unit to position the positive locking elements 13b and 13c of the locking devices 12 and, in conjunction with the electronic main control unit, to maintain the switching position of the positive locking elements 13b and 13c of the locking devices 12. The actuators 13a of the locking devices 12 according to the invention are actuated by the electronic main control unit.By controlling, regulating and monitoring these processes and simultaneously controlling, regulating and monitoring the electric drives 15, which simultaneously serve to drive the multi-start planetary gear of the drive unit according to the invention, by the electronic main control unit, at least partially exclusive electronic control, regulation and monitoring of individual mechanical switching elements, in particular locking devices 12 in accordance with the invention, can be carried out.

[0150] It is further preferred that, during the switching of a locking device 12 in the course of changing the transmission ratio of the drive unit 1, the output shaft of the multi-start planetary gear is driven by at least one of the electrically operable drives 15 of the drive unit 1.

[0151] The multi-stage planetary gear of the drive unit 1 according to the invention must be able to be driven by the electrically operated drives of the drive unit 1 even during the switching of a locking device 12 in the course of changing the transmission ratio of the drive unit 1, and thus with the output shaft 11.5 rotating. A particular challenge lies in switching locking devices 12 according to the invention, which do not require complex hydraulic or other conventional control, regulation, and monitoring systems according to the prior art. Switching individual locking devices 12 is a necessary subprocess of the gear change, i.e., the change in the transmission ratio of the drive unit according to the invention.The general mechanical design of locking devices 12 according to the invention requires positioning their locking elements 13b and 13c and thus bringing them into a switching position in order to open or close the respective locking device 12, controlled, regulated and monitored by the main electronic control unit, by means of actuator 13a and thus to releasably couple rotating shafts to other rotating or rotatable shafts in a rotationally fixed manner or to block rotating or rotatable shafts against the housing.

[0152] This is achieved by applying a method which includes driving the rotors 3 by the stators 4 while simultaneously modulating the flowing electric current to position the locking elements 13b and 13c of the respective locking device 12 and further describes the required sequence of switching the locking devices 12 in accordance with the invention and the other mechanical switching elements.

[0153] Furthermore, the method enables the drive unit 1 according to the invention to shift under load. Moreover, the described method makes it possible to achieve comparable shift times for gear changes, i.e., changes in the transmission ratio, as with conventional drive units with multi-speed transmissions according to the prior art.

[0154] It is further preferred that, during the switching of a locking device 12 in the course of changing the transmission ratio of the drive unit 1, the multi-start planetary gear is driven for recuperation by torques acting on the multi-start planetary gear from outside the housing via the output shaft of the multi-start planetary gear.

[0155] In the context of the invention, the term recuperation refers to the conversion of kinetic energy from mechanical forces, particularly torques, acting on the output shaft 11.5 from outside the housing over a certain period of time, via the multi-start planetary gear and the electric drives 15 of the drive unit 1 according to the invention, which now operate on the reverse principle, i.e., according to the generator principle, into an amount of electrical energy. This energy can be stored as required according to the prior art and used at a later time to provide torque at the output shaft 11.5 via the stators 4 and the rotors 3 of the electric drives 15 of the drive unit 1. This can increase the efficiency of the drive unit 1 according to the invention. Furthermore, recuperation can also occur simultaneously during a gear change, i.e., during the process of changing the transmission ratio of the drive unit 1.

[0156] It is further preferred that the torques determined at the output shaft of the multi-start planetary gear with respect to the power flow before and after the deceleration unit 26 by means of the sensor units of the electronic main control unit are used by the electronic main control unit to determine torque and speed differences and their time offset with respect to the power flow before and after the deceleration unit 26 and, with the aid of this information, to reduce the switching times of the locking devices 12 and thus also the time required for changing the transmission ratio of the drive unit 1 according to the invention.

[0157] When using a deceleration unit 26, it is advantageous to arrange sensor units upstream and downstream of the deceleration unit 26 with respect to the force flow. These sensor units are assigned to the main electronic control unit and transmit information, in particular on values ​​of physical quantities, rotational speed, direction of rotation and angular position, to the main electronic control unit via standard communication links. This allows the main electronic control unit to determine torque and speed differences and their time offset with respect to the force flow upstream and downstream of the deceleration unit 26.The additional determination of the torque at the output shaft of the multi-start planetary gear unit by sensor units of the electronic main control unit is advantageous for optimizing, i.e., reducing, the switching times of the locking devices 12 and thus also the time required for changing the gear ratio of the drive unit 1 according to the invention, i.e., for shifting gears. For optimization purposes, it can also be advantageous for the electronic main control unit to additionally determine, evaluate, and use sensor units in the usual manner the rotational speed, direction of rotation, angular position, and also the torque of further assemblies downstream of the drive unit 1 according to the invention with respect to the power flow, and to use this information for controlling the operation and the change in the gear ratio of the drive unit 1 according to the invention.

[0158] Depending on whether the drive unit 1 according to the invention drives or recuperates, the direction of the force flow of the mechanical forces, in particular torques, is different.

[0159] Since the main electronic control unit controls, regulates and monitors both the drive of the drive unit 1 and the establishment and maintenance of the switching position of the locking elements 13b and 13c of the locking devices 12 according to the invention for the preparation of switching the locking devices 12 via the stators 4 and rotors 5 of the electric drives 15, and furthermore controls, regulates and monitors the switching of the locking devices 12 by the respective actuators 13a for the purpose of changing the transmission ratio of the drive unit 1 according to the invention, it can, using the information, in particular on values ​​of physical quantities, which it determines by means of the sensor units with regard to the force flow before and after the deceleration unit, ensure trouble-free operation of the drive unit 1 according to the invention, even with dynamically changing torques on the output shaft 11.5.

[0160] Dynamically changing torques on the output shaft 11.5 can be caused by mechanical forces acting on the output shaft 11.5 from outside the housing. This can prevent the positive locking of the two positive locking elements 13b and 13c of the locking device 12 from being established or released. This can occur particularly when the drive unit 1 according to the invention is used in motor vehicles employed in agriculture, especially when these vehicles are driven on very uneven terrain.

[0161] It is further preferred that an amount of electrical energy is inductively transferred from an electrical conductor on the housing to an electrical conductor on a rotatable shaft of the drive unit (1), at least in order to electrically operate a locking device 12 on this rotatable shaft, by which a rotationally fixed connection between two rotatable shafts of the drive unit 1 can be established.

[0162] It is advantageous to electrically operate the locking devices 12, which serve to establish a rotationally fixed connection between two rotatable or rotating shafts, wherein a positive-locking locking element 13b, 13c of the locking device 12 is rigidly connected to each of the shafts to be connected. To avoid friction losses and wear, which occur, for example, when using sliding contacts, the energy required for the electrical supply of the locking devices 12 must be provided mechanically without contact. The principle of electromagnetic induction is used for this purpose.

[0163] For this purpose, one or more electrical conductors, for example in the form of electrical coils, are arranged on the housing and one or more electrical conductors, for example in the form of electrical coils, are arranged on a rotatable or rotating shaft in order to inductively transfer the amount of electrical energy required for the operation of the locking device 12 from the housing to this rotatable or rotating shaft.

[0164] It is further preferred that an amount of electrical energy is inductively transferred from an electrical conductor on a rotatable shaft of the drive unit 1, in which a voltage is inductively generated, via a further electrical conductor electrically connected to this electrical conductor, to an electrical conductor on a further rotatable shaft of the drive unit 1, at least in order to electrically operate a locking device 12 on this rotatable shaft, by which a rotationally fixed connection between two rotatable shafts of the drive unit 1 can be established.

[0165] It is advantageous to ensure the supply of electrically operated locking devices 12, which are difficult to access and can only be accessed via several shafts of the drive unit 1, and through which a rotationally fixed connection between two rotatable or rotating shafts of the drive unit 1 can be established, by using the principle of electromagnetic induction.

[0166] If, due to poor accessibility of the locking devices 12, the energy supply for the locking devices 12 is to be provided via several shafts, the amount of energy required for the operation of the electrically operated locking device 12 must also be transmitted via several rotatable or rotating shafts. The amount of energy required for the operation of the electrically operated locking devices 12 is first inductively transferred from an electrical conductor on the housing to an electrical conductor on a rotating or rotatable shaft of the drive unit 1.If a positive-locking locking element 13b, 13c of the locking device 12, which is electrically operable and through which a rotationally fixed connection between two rotatable or rotating shafts of the drive unit 1 can be established, is not rigidly connected to this shaft, the energy must first be transferred via this rotatable or rotating shaft of the drive unit 1 to another rotatable or rotating shaft of the drive unit 1. The principle of electromagnetic induction is used for this purpose.

[0167] This type of transmission of the amount of electrical energy required to operate the locking devices 12 reduces the design effort, which would otherwise be increased due to the poor accessibility of the locking devices 12 to be supplied with electrical energy.

[0168] If necessary, the amount of energy required for the operation of the electrically operated locking device 12 must also be transmitted via several rotatable or rotating shafts. This is also the case if the multi-start planetary gear is composed of more than one planetary gear arranged coaxially to the main axis 2.

[0169] The amount of energy required to operate the electrically operated locking device 12 is transmitted from rotatable or rotating shafts in the same way via further shafts which are connected via a detachable rotationally fixed connection, or directly to the respective electrically operated locking device 12.

[0170] It is further preferred that the transmission path for the amount of energy transmitted electrically or according to the principle of electromagnetic induction for the operation of the locking devices 12 is used equally for the bidirectional communication between the main electronic control unit and at least the electronic control units of the locking devices 12, which can establish a rotationally fixed connection between two rotatable or rotating shafts of the drive unit 1.

[0171] It is advantageous to use the same transmission path for supplying electrically operated locking devices 12, which are difficult to access and can only be accessed via several shafts of the drive unit 1, and which establish a rotationally fixed connection between two rotatable or rotating shafts of the drive unit 1, as well as for bidirectional communication between the electronic main control unit and conventional control units according to the prior art, which at least possess the locking devices 12 as defined in the invention and which can establish a rotationally fixed connection between two rotatable or rotating shafts of the drive unit 1. Using one and the same transmission path eliminates the need for an additional physical transmission path, leading to cost reductions in the manufacture of the drive unit 1 according to the invention.

[0172] The transmission of electrical energy to supply electrically operated locking devices 12, which can establish a rotationally fixed connection between rotatable or rotating shafts of the drive unit 1, is carried out in the usual way via electrical conductors and inductively via coils connected to these electrical conductors. These electrical coils and these electrical conductors can also be used in the usual way for bidirectional communication between the main electronic control unit or conventional control units controlled, regulated, and monitored by it. For example, this can be done using electromagnetic carrier waves.

[0173] It is also preferred to use the drive unit 1 according to the invention for driving motor vehicles, rail vehicles, aircraft and water vehicles, or as a generator for wind or hydropower plants.

[0174] Due to its small size compared to drive units with similar power or electrical output according to the prior art, the drive unit 1 according to the invention is advantageous for operating motor vehicles, rail vehicles, aircraft, and watercraft. In generator mode, the drive unit 1 according to the invention also offers economic advantages compared to drive units with similar electrical output according to the prior art due to its small size and is therefore advantageously suited for use as a generator in wind or hydropower plants.

[0175] Advantageous embodiments of the drive unit 1 according to the invention are described in dependent claims 2 to 4. The features of the claims can be combined in any technically meaningful way, whereby the following description as well as the features from the Fig. 1, Fig. 2, Fig. 3, Fig. 4 and Fig.5 as well as from Table 1, Table 2, Table 3, Table 4, Table 5 and Table 6 can serve as a basis.

[0176] Claim 5 relates to the method for operating a drive unit 1 according to the invention as defined in claims 1, 2, 3 or 4.

[0177] Claim 6 relates to the method for operating a drive unit 1 according to the invention as described in claim 5 while the output shaft of the multi-start planetary gear is driven by at least one of the electrically operable drives 15 of the drive unit 1.

[0178] Claim 7 relates to the method for operating a drive unit 1 according to the invention as per claim 5 during the switching of a locking device 12 in the course of changing the transmission ratio of the drive unit 1, the multi-start planetary gear is driven for recuperation by torques acting on the multi-start planetary gear from outside the housing via the output shaft of the multi-start planetary gear.

[0179] Claim 8 relates to the method for operating a drive unit 1 according to the invention as per claim 5, 6 or 7.

[0180] Claim 9 relates to a method for operating a drive unit 1 according to the invention according to one of claims 5, 6, 7 or 8, wherein the torques determined at the output shaft of the multi-start planetary gear with respect to the power flow before and after the deceleration unit 26 by means of the sensor units of the electronic main control unit are used by the electronic main control unit to determine torque and speed differences and their time offset with respect to the power flow before and after the deceleration unit 26 and, with the aid of this information, to reduce the switching times of the locking devices 12 and thus also the time required for changing the transmission ratio of the drive unit 1 according to the invention.

[0181] Claim 10 relates to the method for operating a drive unit 1 according to the invention as claimed in claim 9, wherein an electrical energy is inductively transferred from an electrical conductor on a rotatable shaft of the drive unit 1, in which a voltage is inductively generated, via a further electrical conductor electrically connected to this electrical conductor, to an electrical conductor on a further rotatable shaft of the drive unit 1, at least in order to electrically operate a locking device 12 on this rotatable shaft, by which a rotationally fixed connection between two rotatable shafts of the drive unit 1 can be established.

[0182] Claim 11 relates to the method for operating a drive unit 1 according to the invention according to one of claims 9 or 10, wherein the transmission path for the amount of energy transmitted electrically or according to the principle of electromagnetic induction for the operation of the locking devices 12 is used equally for the bidirectional communication between the main electronic control unit and at least the electronic control units of the locking devices 12, which can establish a rotationally fixed connection between two rotatable or rotating shafts of the drive unit 1.

[0183] Claim 12 names areas of application of the drive unit 1 according to the invention.

[0184] The invention is described below with reference to four exemplary embodiments with regard to the structure.

[0185] The procedure for operating and changing the gear ratio from the lowest to the highest gear is described for the first, second, and third embodiments with reference to the Fig. 1, Fig. 2, Fig. 3, Fig. 4 and Fig. Section 5 is described in more detail. Furthermore, the functionality of the fourth embodiment is explained.

[0186] Fig.Figure 1 schematically shows the drive unit 1 according to the invention in the first embodiment with two electric drives 15, each consisting of a stator 4.2 and rotor 5.2, and a stator 4.1 and rotor 5.1, in the form of internal rotors. Also shown are the shafts 11.1, 11.2, 11.3, 11.4 and the output shaft 11.5. Shaft 11.2 functions both as a torque transmitter 6.1 and as a drive input segment 3.1, and shaft 11.3 functions both as a torque transmitter 6.2 and as a drive input segment 3.2. The locking devices 12.1, 12.2, 12.3, 12.4 and 12.5, as well as the sun gear 7, the ring gear 10 and the carrier gear 8, are also shown. The main shaft 2 is not shown.

[0187] Fig.Figure 2 shows the delay unit 26 in the second embodiment. Also shown are the locking device 12.5 on the ring gear 10 and the locking device 12.1 on shaft 11.1, the components of the locking devices 12.5 and 12.1, namely the locking elements 13b, 13c and the actuator 13a, the output shaft 11.5, the carrier gear 8 and the main shaft 2 of the drive unit 1 according to the invention. Not shown are shaft 11.2, shaft 11.3, shaft 11.4, locking device 12.2, locking device 12.3, locking device 12.4, rotor 3.1, rotor 3.2, stator 4.1, stator 4.2, sun gear 7 and the drives 15.

[0188] Fig. Figure 3 shows an example of a locking device 12 according to the invention, consisting of locking element 13b, locking element 13c and actuator 13a.

[0189] Fig.Figure 4 schematically shows the drive unit 1 according to the invention in the third embodiment with two electric drives 15, each consisting of a stator 4.2 and rotor 5.2, and a stator 4.1 and rotor 5.1, in the form of external rotors. Also shown are the shafts 11.1, 11.2, 11.3, 11.4 and the output shaft 11.5. Shaft 11.2 functions both as a torque transmitter 6.1 and as a drive input segment 3.1, and shaft 11.3 functions both as a torque transmitter 6.2 and as a drive input segment 3.2. Furthermore, the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5, the sun gear 7, the ring gear 10, the carrier gear 8, and the stationary support shaft 14 are shown. The main shaft 2 is not shown.

[0190] Fig.Figure 5 schematically shows the drive unit 1 according to the invention in the fourth embodiment with two drives 15. Also shown are the shafts 11.1, 11.2, 11.3, 11.4 and the output shaft 11.5, the torque transmitters 6.1 and 6.2, the drive input segments 3.1 and 3.2, the backstops 21, 25, the disengageable overrunning clutches 22, 24 and the friction clutch 23 as mechanical switching elements, as well as the sun gear 7, the ring gear 10 and the carrier gear 8. The main shaft 2 is not shown.

[0191] A first embodiment of the drive unit 1 according to the invention, wherein the electrically operated drives 15 are designed as internal rotors, with three gears, is shown in Fig. 1 is shown and will be discussed below with reference to the Fig. 2 and Fig.3 explained and consists of an electronic main control unit, a housing containing two electrically operated drives 15, consisting of rotor 5.1 and stator 4.1 and rotor 5.2 and stator 4.2, a multi-start planetary gear consisting of a planetary gear and five locking devices 12, which for the purpose of differentiation are referred to in the further description of the exemplary embodiment as the locking devices 12.1, 12.2, 12.3, 12.4, 12.5 and which are described in Fig. Figure 1 shows the multi-start planetary gear set. This set consists of a planetary gear set arranged coaxially to the main shaft 2. In this exemplary embodiment, the planetary gear set comprises a ring gear 10, a carrier gear 8 with planet gears, and a sun gear 7.

[0192] The total rated power of the electrically operated drives 15 of the drive unit 1 according to the invention is distributed as shown in Table 2. The ratio of the number of teeth of sun gear 7 to the number of teeth of ring gear 10 is approximately 1 to 1.618.

[0193] The maximum achievable rotational speeds of rotor 5.1, rotor 5.2 and the rotational speed of the output shaft 11.5 are approximately the same.

[0194] In this embodiment of the drive unit 1 according to the invention, the planetary gear of the multi-start planetary gear is driven via rotor 5.1 and rotor 5.2.

[0195] Stator 4.1 and stator 4.2 of the electrically operated drives 15 of the drive unit 1 according to the invention are firmly connected to the housing.

[0196] Furthermore, the drive unit 1 includes shaft 11.1, shaft 11.2, shaft 11.3 and shaft 11.4, these shafts serving to connect the components of the planetary gear, the locking devices 12.1, 12.2, 12.3, 12.4, 12.5 and the rotors 5.1 and 5.2, and the output shaft 11.5. The axes of rotation of these shafts correspond to the main axis 2.

[0197] In this embodiment and in other possible embodiments with a multi-start planetary gear unit consisting of only one planetary gear unit, the output shaft 11.5 is, by design, also the output shaft of the multi-start planetary gear unit and also the output shaft of the drive unit 1 according to the invention.

[0198] Furthermore, the drive unit 1 includes torque transmitter 6.1 and drive input segment 3.1, as well as torque transmitter 6.2 and drive input segment 3.2. In this embodiment, these are not designed as separate components. In this embodiment, shaft 11.2 performs the function of torque transmitter 6.1 and drive input segment 3.1, and shaft 11.3 performs the function of torque transmitter 6.2 and drive input segment 3.2.

[0199] The shaft 11.1 is rotatably mounted in the housing and fixedly connected to the sun gear 7, the positive locking element 13b of the locking device 12.1 (the positive locking element 13c of the locking device 12.1 being fixedly connected to the housing), and the positive locking element 13b of the locking device 12.2 (the positive locking element 13c of the locking device 12.2 being fixedly connected to the shaft 11.2). The shaft 11.2 is designed as a hollow shaft and rotatably mounted on the shaft 11.1. The shaft 11.2 is fixedly connected to the rotor 5.1 and the positive locking element 13b of the locking device 12.3 (the positive locking element 13c of the locking device 12.3 being fixedly connected to the shaft 11.3). The shaft 11.3 is rigidly connected to the rotor 5.2 and the positive locking element 13b of the locking device 12.4, wherein the positive locking element 13c of the locking device 12.4 has a fixed connection with shaft 11.4. Shaft 11.3 is designed as a hollow shaft and is rotatably mounted on shaft 11.1.

[0200] The shaft 11.4 is a form of the ring gear 10 and is rotatably mounted on the shaft 11.1 and the output shaft 11.5 and is fixedly connected to the positive locking element 13b of the locking device 12.5, wherein the positive locking element 13c of the locking device 12.5 has a fixed connection to the housing. The shaft 11.4 is also fixedly connected to the positive locking element 13c of the locking device 12.4.

[0201] The output shaft 11.5 is rotatably mounted on the shaft 11.1 and is rigidly connected to the carrier wheel 8 of the planetary gear of the multi-start planetary gear.

[0202] The direction of rotation of rotor 5.1, rotor 5.2 and the output shaft 11.5 is the same when the planetary gear of the multi-start planetary gear is driven in the exemplary embodiment.

[0203] The locking devices 12.1, 12.2, 12.3, 12.4, 12.5 each comprise at least one actuator 13a, which is electromechanically operated, and at least two positive locking elements, namely the 1st positive locking element 13b and the 2nd positive locking element 13c, wherein the positive locking of the positive locking elements 13b and 13c can be established or released by the actuator 13a.

[0204] In the closed locking devices 12, there is a sufficiently large, customary clearance between the positive locking elements 13b and 13c of the locking devices 12 to enable the positive locking of the positive locking elements 13b and 13c to be released or restored.

[0205] The locking devices 12.2, 12.3 and 12.4 each have electronic control units.

[0206] In this embodiment, the locking devices 12.1, 12.2, 12.3, 12.4, and 12.5 are electrically operated. The energy required to operate the locking devices 12.1, 12.2, 12.3, 12.4, and 12.5 is supplied by an electrical power source and transmitted to the locking devices 12.1 and 12.5, which are permanently connected to the housing, via electrical conductors. The energy required to operate the locking devices 12.2, 12.3, and 12.4 is transmitted by means of electrical conductors and using the principle of electromagnetic induction. The locking devices 12.2, 12.3, and 12.4 each have electronic control units.

[0207] The energy required for the operation of the locking device 12.2 is first inductively transferred from an electrical coil on the housing to an electrical coil on the shaft 11.1. This energy is then transferred from this electrical coil on shaft 11.1 to the locking device 12.2 via an electrical conductor located on shaft 11.1.

[0208] The energy required for the operation of the locking device 12.3 is electrically transmitted from the electrical conductor located on shaft 11.1 to another electrical coil on shaft 11.1 and then inductively from this second electrical coil to an electrical coil on shaft 11.2. The energy is then transferred from this electrical coil on shaft 11.2 to the locking device 12.3 via an electrical conductor located on shaft 11.2.

[0209] The energy required for the operation of the locking device 12.4 is electrically transmitted from the electrical conductor located on shaft 11.2 to another electrical coil on shaft 11.2 and then inductively transmitted from this second electrical coil on shaft 11.2 to an electrical coil on shaft 11.3. The energy is then transmitted from this electrical coil on shaft 11.3, via an electrical conductor located on shaft 11.3, to the locking device 12.4.

[0210] The locking devices 12.1 and 12.5 are controlled by the main electronic control unit, which is connected to them via electrical conductors.

[0211] The locking devices 12.2, 12.3, and 12.4 are controlled by the main electronic control unit. The transmission path for the energy transferred electrically and, in some sections, via electromagnetic induction for the operation of the locking devices 12.2, 12.3, and 12.4 is used equally for bidirectional communication between the main electronic control unit and the electronic control units of the locking devices 12.2, 12.3, and 12.4. The electronic control units of the locking devices 12.2, 12.3, and 12.4 are conventional, state-of-the-art control units.

[0212] The method for operating and changing the transmission ratio of the drive unit 1 according to the invention in the first embodiment is explained below with reference to the various switching states and their transitions. The description proceeds from the first gear with the highest torque relative to the total power of the two electric drives 15 on the output shaft 11.5 to the third gear with the lowest torque relative to the total power of the two electric drives 15 on the output shaft 11.5. The main electronic control unit continuously and programmatically detects and evaluates the speed, direction of rotation, and angular position of shaft 11.2, with the additional function of torque transmitter 6.1 and drive input segment 3.1, and thus also the speed, direction of rotation, and angular position of rotor 5.1 and shaft 11.3, with the additional function of torque transmitter 6.2 and drive input segment 3.2, and thus also speed, direction of rotation and angular position of rotor 5.2, and furthermore speed, direction of rotation and angular position of sun gear 7, carrier gear 8 and ring gear 10 and the torque of the output shaft 11.5.

[0213] The method serves to operate the drive unit 1 according to the invention and to change the transmission ratio, i.e. to switch gears, of the drive unit 1 according to the invention.

[0214] If, for the duration of the switching of a locking device 12 in the course of changing the transmission ratio of the drive unit 1 according to the invention, either the multi-start planetary gear and the output shaft 11.5 are driven by at least one of the two electrically operated drives 15 of the drive unit 1 according to the invention, or the multi-start planetary gear is driven by mechanical forces, in particular torques, acting from outside the housing via the output shaft 11.5 on the carrier wheel 8 for the purpose of recuperation, i.e., if a vehicle driven by the drive unit 1 according to the invention is to be accelerated or recuperation is to take place, the process is as follows.Insofar as the following explanations refer to the drive of the planetary gear of the multi-gear planetary gear by one or both electric drives 15 in the individual phases of the gear changes, the drive of the planetary gear of the multi-gear planetary gear can, in the case of recuperation, also be effected by torques acting on the output shaft 11.5 from outside the housing. During the gear changes, their phases, and also during the establishment and holding of the switching position of the locking elements 13b and 13c of the respective locking device 12 in preparation for switching the respective locking devices 12, the drive can be switched arbitrarily between the respective electric drive 15 of the multi-gear planetary gear and the drive of the multi-gear planetary gear by torques acting on the output shaft 11.5 from outside the housing.The main electronic control unit controls, regulates and monitors the electrical current flowing to stators 4.1 and 4.2 in such a way as to compensate for speed fluctuations.

[0215] For the sake of simplicity, however, the following explanations will refer exclusively to the drive by the relevant electric drive 15 or the drive by the relevant electric drives 15.

[0216] Stator 4.1 and stator 4.2 of the electric drives 15, in conjunction with rotor 5.1 and rotor 5.2, serve both to establish and maintain the switching position of the locking elements 13b and 13c of the locking devices 12.1, 12.2, 12.1, 12.4 and 12.5 in preparation for switching the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 in order to change the transmission ratio of the drive unit 1 according to the invention, and to drive the output shaft of the multi-start planetary gear of the drive unit 1 according to the invention via the planetary gear of the multi-start planetary gear.

[0217] In the first gear, locking devices 12.2, 12.3, and 12.5 are closed, while locking devices 12.1 and 12.4 are open. The electric current flowing from an electrical power source is switched to stator 4.1 and stator 4.2 by the main electronic control unit. When the electric current is applied, stators 4.1 and 4.2 set rotor 5.1 and rotor 5.2, which is rotationally fixed to it due to the closed locking device 12.3, into rotational motion. This continues up to the maximum speed that can be achieved by the two electric drives 15.

[0218] Rotor 5.1 and rotor 5.2 drive the sun gear 7 via shaft 11.1. The locking device 12.1 located on shaft 11.1 is open. The ring gear 10 is blocked by the closed locking device 12.5.

[0219] Thus, in this switching state, the sun gear 7 drives the carrier gear 8 and therefore the output shaft 11.5 via the planet gears.

[0220] This switching state of the drive unit 1 provides the maximum torque at the output shaft 11.5 in relation to the total power of the two electric drives 15 in first gear.

[0221] If necessary, recuperation is possible in this switching state by switching stator 4.1 and stator 4.2 via the electronic main control unit.

[0222] The change from first gear to second gear, i.e., this change in the transmission ratio of the drive unit 1, is effected by switching the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 and the modulation of the electric current flowing from an electrical energy source to stator 4.1 and stator 4.2 by the main electronic control unit and takes place in different phases, whereby during these phases the output shaft 11.5 continues to be in a rotary motion and is driven via the multi-start planetary gear or by torques acting on the output shaft 11.5 from outside the housing.

[0223] In the first phase of the gear change, the planetary gear set of the multi-stage planetary gear set in this embodiment continues to be driven by the stator 4.1 via the rotor 5.1. The electrical current flowing to the stator 4.2 is now modulated by the main electronic control unit. In this phase, the stator 4.2 no longer serves to drive the multi-stage planetary gear set, but is used to: establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.3 in preparation for switching the locking devices 12.3. To switch the locking device 12.3, its positive-locking locking elements 13b and 13c must be positioned in the switching position. The main electronic control unit modulates the electric current flowing to stator 4.2 such that the positive-locking locking elements 13b and 13c of the locking device 12.3 are moved into the switching position relative to each other and are held in this switching position once this position is reached. To maintain this switching position during fluctuations in the rotational speed of rotor 5.1, the main electronic control unit modulates the electric current flowing to stator 4.2 accordingly. When the positive-locking locking elements 13b and 13c of the locking device 12.3 are in the switching position, the main electronic control unit actuates the actuator 13a of the locking device 12.3, thereby releasing the positive locking of the positive-locking locking elements 13b and 13c of the locking device 12.3.

[0224] In the second phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven by the stator 4.1 via the rotor 5.1. The electrical current flowing to the stator 4.2 is now modulated by the main electronic control unit. In this phase, the stator 4.2 does not drive the multi-start planetary gear set, but is used to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.4 in preparation for switching the locking devices 12.4. To switch the locking device 12.4, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0225] The main electronic control unit modulates the electric current flowing to stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.4 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0226] Since the ring gear 10 is blocked by the closed locking device 12.5, the rotational speed of rotor 5.2 is zero when the switching position of components 13b and 13c of the locking device 12.4 is reached.

[0227] When the positive locking elements 13b and 13c of the locking device 12.4 are in the switching position, the actuator 13a of the locking device 12.4 is actuated by the electronic main control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.4.

[0228] In the third phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven by the stator 4.1 via the rotor 5.1. The electrical current flowing to the stator 4.2 is now modulated by the main electronic control unit. In this phase, the stator 4.2 does not drive the multi-start planetary gear set, but is used to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.5 in preparation for switching the locking devices 12.5. To switch the locking device 12.5, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0229] The main electronic control unit modulates the electric current flowing to stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.5 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0230] Since the ring gear 10 is blocked by the closed locking device 12.5, the rotational speed of rotor 5.2 is zero when the switching position of components 13b and 13c of the locking device 12.5 is reached.

[0231] Modulating the electric current flowing to stator 4.2 is necessary to balance the torques acting on the ring gear 10 via the planet gears from both the carrier gear 8 and the sun gear 7, so that the zero rotational speed of rotor 5.2 remains unchanged. At this point, the planetary gear set of the multi-start planetary gear set continues to be driven by stator 4.1 via rotor 5.1.

[0232] When the positive locking elements 13b and 13c of the locking device 12.5 are in the switching position, the actuator 13a of the locking device 12.5 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.5.

[0233] In the fourth phase of the switching process, the planetary gear of the multi-start planetary gear is initially driven by the stator 4.1 via the rotor 5.1 and by the stator 4.2 via the rotor 5.2.

[0234] The electronic control unit switches the electric current flowing to stator 4.2 and increases its current intensity. Simultaneously, the electronic control unit decreases the current flowing to stator 4.1. Stator 4.1 and stator 4.2 then jointly drive the multi-start planetary gear until the rotational speed of rotor 5.1 is zero; from this point on, only stator 4.2 drives the multi-start planetary gear via rotor 5.2.

[0235] Immediately upon reaching zero rotational speed of rotor 5.1, the main electronic control unit modulates the electrical current flowing to stator 3.1 to maintain the zero rotational speed of rotor 5.1. This modulation is necessary to balance the torques acting on the sun gear 7 via the planet gears from both the carrier gear 8 and the ring gear 10, ensuring that the zero rotational speed of rotor 5.1 remains unchanged. At this point, the planetary gear set of the multi-start planetary gear set continues to be driven by stator 4.2 via rotor 5.2.

[0236] The electric current flowing to stator 4.1 is now modulated by the main electronic control unit so that stator 4.1 can be used to establish and hold the switching position of the locking elements 13b and 13c of the locking device 12.1 in preparation for switching the locking device 12.1, and simultaneously to counteract the torques acting on the sun gear 7 via the planet gears from both the carrier gear 8 and the ring gear 10. To switch the locking device 12.1, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0237] The main electronic control unit now modulates the electric current flowing to stator 4.1 so that the positive locking elements 13b and 13c of the locking device 12.1 are moved into switching position relative to each other and are held in this switching position once this switching position is reached.

[0238] When the positive locking elements 13b and 13c of the locking device 12.1 are in the switching position, the actuator 13a of the locking device 12.1 is actuated by the main electronic control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.1.

[0239] In the fifth phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven by the stator 4.2 via the rotor 5.2. The electrical current flowing to the stator 4.1 is modulated by the main electronic control unit. In this phase, the stator 4.1 does not drive the multi-start planetary gear set, but is used to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.2 in preparation for switching the locking devices 12.2. To switch the locking device 12.2, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0240] The main electronic control unit modulates the electric current flowing to stator 4.1 so that the positive locking elements 13b and 13c of the locking device 12.2 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0241] When the positive locking elements 13b and 13c of the locking device 12.2 are in the switching position, the actuator 13a of the locking device 12.2 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.2.

[0242] In the sixth phase of the switching process, the planetary gear set of the multi-stage planetary gearbox continues to be driven by the stator 4.2 via the rotor 5.2. The electrical current flowing to the stator 4.1 is switched by the main electronic control unit, and its current intensity is increased by the main electronic control unit. This continues until rotor 5.1 and rotor 5.2 reach the same rotational speed.

[0243] Stator 4.1 does not serve to drive the multi-start planetary gear in this phase, but is used to establish and hold the switching position of the locking elements 13b and 13c of the locking device 12.3 in preparation for switching the locking devices 12.3. To switch the locking device 12.3, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0244] From the moment the rotational speeds of rotor 5.1 and rotor 5.2 are synchronized, the main electronic control unit modulates the electric current flowing to stator 4.1 so that the positive locking elements 13b and 13c of the locking device 12.3 are moved into the switching position relative to each other and are held in this switching position once this switching position is reached.

[0245] When the positive locking elements 13b and 13c of the locking device 12.3 are in the switching position, the actuator 13a of the locking device 12.3 is actuated by the main electronic control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.3.

[0246] This completes the shifting process from first gear to second gear.

[0247] In the second gear, stator 4.1 drives rotor 5.1 and stator 4.2 drives rotor 5.2. Rotors 5.1 and 5.2, which are rotationally locked together by locking device 12.3, drive the ring gear 10, which is rotationally locked together by locking device 12.4. The sun gear 7 is blocked by locking device 12.1, and locking devices 12.2 and 12.5 are open.

[0248] The electronic control unit now increases the current flowing to stator 4.1 and stator 4.2. This increases the rotational speed of rotor 5.1 and rotor 5.2, and consequently the rotational speed of the ring gear 10, which is rigidly coupled to rotor 5.2. This also increases the rotational speed of the carrier gear 8 and the output shaft 11.5 rigidly connected to it, up to the maximum speed achievable by the electric drives 15.

[0249] If necessary, recuperation is possible in this switching state by switching stator 4.1 and stator 4.2 to generator operation by the electronic main control unit.

[0250] In this switching state of the drive unit 1 according to the invention in second gear, a lower torque is provided at the output shaft 11.5 in relation to the total power of the electric drives 15, but at a higher speed at the output shaft 11.5, than in first gear.

[0251] The change from second gear to third gear, i.e., this change in the gear ratio of the drive unit 1, is effected by switching the locking devices 12.1, 12.2 and 12.3 and the modulation of the electric current flowing from an electrical energy source to stator 4.1 by the electronic main control unit and takes place in different phases, during which the output shaft 11.5 continues to be in a rotary motion and is driven via the multi-stage planetary gear.

[0252] In the first phase of the switching process, the planetary gear set of the multi-start planetary gear set in this embodiment continues to be driven by the stator 4.2 via the rotor 5.2. The electrical current flowing to the stator 4.1 is now modulated by the main electronic control unit. Stator 4.1 no longer serves to drive the multi-start planetary gear set, but is used to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.3 in preparation for switching the locking device 12.3. To switch the locking device 12.3, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0253] The main electronic control unit modulates the electric current flowing to stator 4.1 such that the positive-locking locking elements 13b and 13c of the locking device 12.3 are moved into the switching position relative to each other and are held in this switching position once this position is reached. To maintain this switching position during fluctuations in the rotational speed of rotor 5.2, the main electronic control unit modulates the electric current flowing to stator 4.1 accordingly. When the positive-locking locking elements 13b and 13c of the locking device 12.3 are in the switching position, the main electronic control unit actuates the actuator 13a of the locking device 12.3, thereby releasing the positive locking of the positive-locking locking elements 13b and 13c of the locking device 12.3.

[0254] In the second phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven by the stator 4.2 via the rotor 5.2. The electrical current flowing to the stator 4.1 is now modulated by the main electronic control unit. In this phase, the stator 4.1 does not drive the multi-start planetary gear set, but is used to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.2 in preparation for switching the locking device 12.2. To switch the locking device 12.2, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0255] Since the sun wheel 7 is blocked by the closed locking device 12.1, the rotational speed of rotor 5.1 is zero when the switching position of components 13b and 13c of the locking device 12.2 is reached.

[0256] The main electronic control unit now modulates the electric current flowing to stator 4.1 so that the positive locking elements 13b and 13c of the locking device 12.2 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0257] When the positive locking elements 13b and 13c of the locking device 12.2 are in the switching position, the actuator 13a of the locking device 12.2 is actuated by the electronic main control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.2.

[0258] In the third phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven by the stator 4.2 via the rotor 5.2. The electrical current flowing to the stator 4.1 is now modulated by the main electronic control unit. In this phase, the stator 4.1 does not drive the multi-start planetary gear set, but is used to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.1 in preparation for switching the locking device 12.1. To switch the locking device 12.1, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0259] Since the sun gear 7 is blocked by the closed locking device 12.1, the rotational speed of rotor 5.1 is zero when the switching position of the locking elements 13b and 13c of the locking device 12.1 is reached.

[0260] The main electronic control unit now modulates the electric current flowing to stator 4.1 so that the positive locking elements 13b and 13c of the locking device 12.1 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0261] Modulating the electric current flowing to stator 4.1 is necessary to balance the torques acting on the sun gear 7 via the planet gears from both the carrier gear 8 and the ring gear 10, so that the zero rotational speed of rotor 5.1 remains unchanged. At this point, the planetary gear set of the multi-start planetary gear set continues to be driven by stator 4.2 via rotor 5.2.

[0262] When the positive locking elements 13b and 13c of the locking device 12.1 are in the switching position, the actuator 13a of the locking device 12.1 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.1.

[0263] In the fourth phase of the switching process, the planetary gear set of the multi-stage planetary gearbox continues to be driven by stator 4.2 via rotor 5.2. The electric current flowing to stator 4.1 is now switched by the electronic control unit, and its current intensity is increased by the electronic control unit. Simultaneously, the current intensity of the electric current flowing to stator 4.2 is decreased by the electronic control unit. This continues until rotor 5.1 and rotor 5.2 reach the same rotational speed.

[0264] This completes the shifting process from second gear to third gear.

[0265] In the third gear, stator 4.1 drives rotor 5.1 and stator 4.2 drives rotor 5.2. Rotor 5.1 drives the sun gear 7, which is rotationally fixed to rotor 5.1 by the locking device 12.2. Rotor 5.2 drives the ring gear 10, which is rotationally fixed to rotor 5.2 by the locking device 12.4. Locking devices 12.1, 12.3, and 12.5 are open; locking devices 12.2 and 12.4 are closed.

[0266] The electronic main control unit now increases the current flowing to stator 4.1 and stator 4.2. This increases the rotational speed of rotor 5.1 and rotor 5.2, and consequently the rotational speed of sun gear 7 and ring gear 10, and thus also the rotational speed of carrier gear 8 and the output shaft 11.5 rigidly connected to it, up to the maximum speed achievable by the electric drives 15.

[0267] If necessary, recuperation is possible in this switching state by switching stator 4.1 and stator 4.2 to generator operation by the electronic main control unit.

[0268] This switching state of the drive unit 1 according to the invention in third gear provides a lower torque at the output shaft 11.5 than in second gear with respect to the total power of the electric drives 15, but at a higher speed at the output shaft 11.5.

[0269] If, during the switching of a locking device in the course of changing the transmission ratio of the drive unit 1 according to the invention, neither the multi-start planetary gear and, through it, the output shaft 11.5 are driven by the electrically operated drives 15 of the drive unit 1 according to the invention, nor are mechanical forces acting on the output shaft 11.5 from outside the housing used for recuperation, but fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 occur due to mechanical forces, in particular torques, acting on the output shaft 11.5 from outside the housing, which can occur when a vehicle driven by the drive unit 1 according to the invention is accelerated by externally acting forces, the process is as follows.

[0270] Stator 4.1 and stator 4.2, in conjunction with rotor 5.1 and rotor 5.2, are required to establish and maintain the switching position of the locking elements 13b and 13c of the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 in preparation for switching the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 in order to change the transmission ratio of the drive unit 1 according to the invention.

[0271] In this case, it is necessary, unlike when, for the duration of switching a locking device 12.1, 12.2, 12.3, 12.4 and 12.5, in the course of changing the transmission ratio of the drive unit 1 according to the invention, either the multi-start planetary gear and through this also the output shaft 11.5 . is driven or the multi-stage planetary gear is used for recuperation by mechanical forces acting on the output shaft 11.5 from outside the housing - i.e., when a vehicle driven by the drive unit 1 according to the invention is to be accelerated or recuperation is to take place, the electrical current flowing to stator 4.1 and stator 4.2 is modulated simultaneously in accordance with the invention for establishing and maintaining the switching position of the locking elements 13b and 13c of the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 in preparation for switching the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5.

[0272] This simultaneous modulation of the electric current flowing to stator 4.1 and stator 4.2 is necessary because fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 are caused by forces, especially torques, acting on the output shaft 11.5 from outside the housing. These fluctuations result in forces of varying magnitudes acting on the positive-locking locking elements 13b and 13c of the locking devices 12.1, 12.2, 12.3, 12.4, and 12.5. These forces can also occur in opposite directions of rotation. These fluctuations are compensated for by simultaneous modulation of the electric current flowing to stator 4.1 and stator 4.2. This modulation is program-controlled by the main electronic control unit or by conventional electronic control units controlled by the main electronic control unit. switching locking devices 12.1, 12.2, 12.3, 12.4 or 12.The rotors 5.1 and 5.2 are moved into the switching position and held there. The rotors 5.1 and 5.2 are controlled by modulating the electric current flowing to stator 4.1 and stator 4.2, so that their speed is increased or decreased, their direction of rotation is reversed, the positioning of the positive-locking locking elements 13b and 13c of the locking devices 12, which are directly or via further closed locking devices 12, is carried out, and the holding of the switching position of the respective locking elements 13b and 13c of the respective locking device 12 can be ensured. Furthermore, the modulation of the electric current flowing to stator 4.1 and stator 4.2 compensates for the cumulative gap dimensions between the positive-locking locking elements 13b and 13c in the case of multiple locking devices 12 in the power flow.

[0273] The modulation of the electric current flowing to stator 4.1 and stator 4.2 by the electronic main control unit is carried out independently of each other and is determined programmatically by the electronic main control unit with the aid of information from its sensor units, in particular values ​​of physical quantities, and information derived therefrom.

[0274] In first gear, locking devices 12.2, 12.3, and 12.5 are closed, while locking devices 12.1 and 12.4 are open. Due to the closed locking device 12.3, rotor 5.1 is rotationally locked to rotor 5.2. Due to the closed locking device 12.2, rotor 5.1 is rotationally locked to sun gear 7. Ring gear 10 is blocked by the closed locking device 12.5.

[0275] The change from first gear to second gear, i.e., this change in the transmission ratio of the drive unit 1, is effected by switching the locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 and the modulation of the electric current flowing from an electrical energy source to stator 4.1 and stator 4.2 by the main electronic control unit and takes place in different phases, during which the output shaft 11.5 continues to be in a rotary motion.

[0276] In the first phase of the switching process, the planetary gear set of the multi-start planetary gear set in this embodiment is no longer driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, particularly torques, acting on the output shaft 11.5 from outside the housing. The electrical current flowing to the stator 4.1 and stator 4.2 is now modulated by the main electronic control unit. In this phase, the stator 4.1 and stator 4.2 serve to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.3 in preparation for switching the locking device 12.3. To switch the locking device 12.3, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0277] The main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 such that the positive-locking locking elements 13b and 13c of the locking device 12.3 are moved into the switching position relative to each other and are held in this switching position once this switching position is reached. To achieve and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 accordingly.

[0278] When the positive locking elements 13b and 13c of the locking device 12.3 are in the switching position, the actuator 13a of the locking device 12.3 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.3.

[0279] In the second phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven neither by the stator 4.1 via the rotor 5.1 nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0280] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit.

[0281] Stator 4.1 and stator 4.2 serve in this phase to establish and hold the switching position of the locking elements 13b and 13c of the locking devices 12.4 in preparation for switching the locking device 12.4. To switch the locking device 12.4, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0282] The main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.4 are moved into switching position relative to each other and are held in this switching position once this switching position is reached.

[0283] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0284] Since the ring gear 10 is blocked by the closed locking device 12.5, the rotational speed of rotor 5.2 is zero when the switching position of components 13b and 13c of the locking device 12.4 is reached.

[0285] When the positive locking elements 13b and 13c of the locking device 12.4 are in the switching position, the actuator 13a of the locking device 12.4 is actuated by the electronic main control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.4.

[0286] In the third phase of the switching process, the planetary gear set of the multi-stage planetary gear set is still not driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0287] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit.

[0288] Stator 4.1 and stator 4.2 serve in this phase to establish and hold the switching position of the locking elements 13b and 13c of the locking device 12.5 in preparation for switching the locking device 12.5. To switch the locking device 12.5, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0289] The main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.5 are moved into switching position relative to each other and are held in this switching position upon reaching this switching position.

[0290] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0291] Since the ring gear 10 is blocked by the closed locking device 12.5, the rotational speed of rotor 5.2 is zero when the switching position of components 13b and 13c of the locking device 12.5 is reached.

[0292] When the positive locking elements 13b and 13c of the locking device 12.5 are in the switching position, the actuator 13a of the locking device 12.5 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.5.

[0293] In the fourth phase of the switching process, the planetary gear set of the multi-stage planetary gear set is still not driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0294] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit. In this phase, stator 4.1 and stator 4.2 serve to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.1 in preparation for switching the locking device 12.1. To switch the locking device 12.1, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0295] The main electronic control unit now modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.1 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0296] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0297] When the positive locking elements 13b and 13c of the locking device 12.1 are in the switching position, the actuator 13a of the locking device 12.1 is actuated by the main electronic control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.1.

[0298] In the fifth phase of the switching process, the planetary gear set of the multi-stage planetary gear set is still not driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0299] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit.

[0300] Stator 4.1 and stator 4.2 serve in this phase to establish and hold the switching position of the locking elements 13b and 13c of the locking devices 12.2 in preparation for switching the locking device 12.2. To switch the locking device 12.2, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0301] The main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.2 are moved into switching position relative to each other and are held in this switching position upon reaching this switching position.

[0302] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0303] When the positive locking elements 13b and 13c of the locking device 12.2 are in the switching position, the actuator 13a of the locking device 12.2 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.2.

[0304] In the sixth phase of the switching process, the planetary gear set of the multi-stage planetary gear set is still not driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0305] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit.

[0306] Stator 4.1 and stator 4.2 serve in this phase to establish and hold the switching position of the locking elements 13b and 13c of the locking device 12.3 in preparation for switching the locking device 12.3. To switch the locking device 12.3, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0307] The electric current flowing to stator 4.1 and stator 4.2 is modulated by the main electronic control unit. This continues until rotor 5.1 and rotor 5.2 reach the same rotational speed.

[0308] From the moment the rotational speeds of rotor 5.1 and rotor 5.2 are synchronized, the main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.3 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0309] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0310] When the positive locking elements 13b and 13c of the locking device 12.3 are in the switching position, the actuator 13a of the locking device 12.3 is actuated by the main electronic control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.3.

[0311] This completes the shifting process from first gear to second gear.

[0312] In the second gear, rotor 5.1 and rotor 5.2 are rotationally locked together by the locking device 12.3. Rotor 5.2 is rotationally locked to the ring gear 10 via the locking device 12.4. The sun gear 7 is blocked by the locking device 12.1, and the locking devices 12.2 and 12.5 are open.

[0313] The change from second gear to third gear, i.e., this change in the gear ratio of the drive unit 1, is effected by switching the locking devices 12.1, 12.2 and 12.3 and the modulation of the electric current flowing from an electrical energy source to stator 4.1 and stator 4.2 by the main electronic control unit and takes place in different phases, during which the output shaft 11.5 continues to be in a rotary motion.

[0314] In the first phase of the switching process, the planetary gear set of the multi-stage planetary gear set is still not driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0315] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit. In this phase, stator 4.1 and stator 4.2 serve to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.3 in preparation for switching the locking device 12.3. To switch the locking device 12.3, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0316] The main electronic control unit modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.3 are moved into switching position relative to each other and are held in this switching position upon reaching it.

[0317] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0318] When the positive locking elements 13b and 13c of the locking device 12.3 are in the switching position, the actuator 13a of the locking device 12.3 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.3.

[0319] In the second phase of the switching process, the planetary gear set of the multi-start planetary gear set continues to be driven neither by the stator 4.1 via the rotor 5.1 nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, particularly torques, acting on the output shaft 11.5 from outside the housing.

[0320] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit. In this phase, stator 4.1 and stator 4.2 serve to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.2 in preparation for switching the locking device 12.2. To switch the locking device 12.2, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0321] Since the sun wheel 7 is blocked by the closed locking device 12.1, the rotational speed of rotor 5.1 is zero when the switching position of components 13b and 13c of the locking device 12.2 is reached.

[0322] The main electronic control unit now modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.2 are moved into switching position relative to each other and are held in this switching position once this switching position is reached.

[0323] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0324] When the positive locking elements 13b and 13c of the locking device 12.2 are in the switching position, the actuator 13a of the locking device 12.2 is actuated by the electronic main control unit, thereby establishing the positive locking of the positive locking elements 13b and 13c of the locking device 12.2.

[0325] In the third phase of the switching process, the planetary gear set of the multi-stage planetary gear set is still not driven by the stator 4.1 via the rotor 5.1, nor by the stator 4.2 via the rotor 5.2. The speed of the output shaft 11.5 increases due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing.

[0326] The electric current flowing to stator 4.1 and stator 4.2 is now modulated by the main electronic control unit. In this phase, stator 4.1 and stator 4.2 serve to establish and maintain the switching position of the locking elements 13b and 13c of the locking device 12.1 in preparation for switching the locking device 12.1. To switch the locking device 12.1, its positive-locking locking elements 13b and 13c must be positioned in the switching position.

[0327] Since the sun wheel 7 is blocked by the closed locking device 12.1, the rotational speed of rotor 5.1 is zero when the switching position of components 13b and 13c of the locking device 12.1 is reached.

[0328] The main electronic control unit now modulates the electric current flowing to stator 4.1 and stator 4.2 so that the positive locking elements 13b and 13c of the locking device 12.1 are moved into the switching position relative to each other and are held in this switching position once this switching position is reached.

[0329] In order to reach and maintain this switching position in the event of fluctuations in the rotational speed of the output shaft 11.5 and the carrier wheel 8 connected to the output shaft 11.5 due to forces, in particular torques, acting on the output shaft 11.5 from outside the housing, the main electronic control unit modulates the electrical current flowing to stator 4.1 and stator 4.2 accordingly.

[0330] When the positive locking elements 13b and 13c of the locking device 12.1 are in the switching position, the actuator 13a of the locking device 12.1 is actuated by the electronic main control unit, thereby releasing the positive locking of the positive locking elements 13b and 13c of the locking device 12.1.

[0331] This completes the shifting process from second gear to third gear.

[0332] During the described phases of the individual gear changes of the drive unit 1 according to the invention, the electronic main control unit can switch at any time, if necessary, to the first described method, i.e., to driving the planetary gear of the multi-start planetary gear by the stators 4.1 and / or 4.2, or to generator operation and thus to using forces, in particular torques, acting on the output shaft of the multi-start planetary gear from outside the housing for recuperation.

[0333] A second embodiment of the drive unit 1 according to the invention, wherein the electrically operated drives 15 are designed as internal rotors, with three gears, is shown in Fig. 2, will be explained below using the Fig. 1, Fig. 2 and Fig. 3 explains and consists of an electronic main control unit, a housing containing two electrically operated drives 15, each consisting of rotor 5.1 and stator 4.1 and rotor 5.2 and stator 4.2, a multi-start planetary gear set, and five locking devices 12, which, for the purpose of differentiation, are referred to in the further description of the exemplary embodiment as the locking devices 12.1, 12.2, 12.3, 12.4, and 12.5. The multi-start planetary gear set consists of a planetary gear set arranged coaxially to the main shaft 2. The planetary gear set is constructed from a ring gear 10, a carrier gear 8 with planet gears, and a sun gear 7.

[0334] The total rated power of the electrically operated drives 15 of the drive unit 1 according to the invention is distributed as shown in Table 5. The ratio of the number of teeth of sun gear 7 to the number of teeth of ring gear 10 is approximately 1 to 1.618.

[0335] The maximum achievable rotational speeds of rotor 5.1, rotor 5.2 and the rotational speed of the output shaft 11.5 are approximately the same.

[0336] In this embodiment of the drive unit 1 according to the invention, the planetary gear of the multi-start planetary gear is driven via rotor 5.1 and rotor 5.2.

[0337] Stator 4.1 and stator 4.2 of the electrically operated drives 15 of the drive unit 1 according to the invention are firmly connected to the housing.

[0338] Furthermore, the drive unit 1 includes shaft 11.1, shaft 11.2, shaft 11.3 and shaft 11.4, these shafts serving to connect the components of the planetary gear, the locking devices 12.1, 12.2, 12.3, 12.4, 12.5 and the rotors 5.1 and 5.2, and the output shaft 11.5. The axes of rotation of these shafts correspond to the main axis 2.

[0339] In this embodiment and in other possible embodiments with a multi-start planetary gear unit consisting of only one planetary gear unit, the output shaft 11.5 is, by design, also the output shaft of the multi-start planetary gear unit and also the output shaft of the drive unit 1 according to the invention.

[0340] Furthermore, the drive unit 1 includes torque transmitter 6.1 and drive input segment 3.1, as well as torque transmitter 6.2 and drive input segment 3.2. In this embodiment, these are not designed as separate components. In this embodiment, shaft 11.2 performs the function of torque transmitter 6.1 and drive input segment 3.1, and shaft 11.3 performs the function of torque transmitter 6.2 and drive input segment 3.2.

[0341] The shaft 11.1 is rotatably mounted in the housing and fixedly connected to the sun gear 7, the positive locking element 13b of the locking device 12.1 (the positive locking element 13c of the locking device 12.1 being fixedly connected to the housing), and the positive locking element 13b of the locking device 12.2 (the positive locking element 13c of the locking device 12.2 being fixedly connected to the shaft 11.2). The shaft 11.2 is designed as a hollow shaft and rotatably mounted on the shaft 11.1. The shaft 11.2 is fixedly connected to the rotor 5.1 and the positive locking element 13b of the locking device 12.3 (the positive locking element 13c of the locking device 12.3 being fixedly connected to the shaft 11.3). The shaft 11.3 is rigidly connected to the rotor 5.2 and the positive locking element 13b of the locking device 12.4, wherein the positive locking element 13c of the locking device 12.4 has a fixed connection with shaft 11.4. Shaft 11.3 is designed as a hollow shaft and is rotatably mounted on shaft 11.1.

[0342] The shaft 11.4 represents a form of the ring gear 10 and is rotatably mounted on the shaft 11.1 and the output shaft 11.5 and is firmly connected to the positive locking element 13b of the locking device 12.5, wherein the positive locking element 13c of the locking device 12.5 has a fixed connection with the housing.

[0343] The output shaft 11.5 is rotatably mounted on the shaft 11.1 and is rigidly connected to the carrier wheel 8 of the planetary gear of the multi-start planetary gear.

[0344] The direction of rotation of rotor 5.1, rotor 5.2 and the output shaft 11.5 is the same when the planetary gear of the multi-start planetary gear is driven in the exemplary embodiment.

[0345] In the second embodiment, a delay unit 26 is arranged on the output shaft 11.5. In this embodiment and in other possible embodiments with a multi-start planetary gear unit consisting of only one planetary gear unit, the output shaft 11.5 is, by design, also the output shaft of the multi-start planetary gear unit and the output shaft of the drive unit 1 according to the invention. In this embodiment, the delay unit 26 is a torsion bar spring.

[0346] With regard to the force flow, sensor units belonging to the main control unit are arranged in front of and behind the deceleration unit 26, which record information, in particular values ​​of physical quantities, with the help of which the electronic main control unit determines torque and speed differences and their time offset with regard to the force flow in front of and behind the deceleration unit 26.

[0347] The locking devices 12.1, 12.2, 12.3, 12.4, 12.5 each comprise at least one actuator 13a, which is electromechanically operated, and at least two positive locking elements, namely the 1st positive locking element 13b and the 2nd positive locking element 13c, wherein the positive locking of the positive locking elements 13b and 13c can be established or released by the actuator 13a.

[0348] In the closed locking devices 12, a sufficiently and customarily dimensioned clearance exists between the positive-locking locking elements 13b and 13c of the locking devices 12 to allow the positive locking of the positive-locking locking elements 13b and 13c to be released or restored. This clearance results from the sufficiently and customarily dimensioned gap between the locking elements 13b and 13c.

[0349] The locking devices 12.2, 12.3 and 12.4 each have standard electronic control units.

[0350] In the second embodiment, the locking devices 12.1, 12.2, 12.3, 12.4, and 12.5 are electrically operated in the usual manner. The energy required to operate the locking devices is supplied by an electrical power source and transmitted to the locking devices 12.1 and 12.5, which are permanently connected to the housing, via electrical conductors. The energy required to operate the locking devices 12.2, 12.3, and 12.4 is transmitted by means of electrical conductors and using the principle of electromagnetic induction. The locking devices 12.2, 12.3, and 12.4 each have electronic control units.

[0351] The energy required for the operation of the locking device 12.2 is first inductively transferred from an electrical coil on the housing to an electrical coil on the shaft 11.1. This energy is then transferred from this electrical coil on shaft 11.1 to the locking device 12.2 via an electrical conductor located on shaft 11.1.

[0352] The energy required for the operation of the locking device 12.3 is electrically transmitted from the electrical conductor located on shaft 11.1 to another electrical coil on shaft 11.1 and then inductively from this second electrical coil to an electrical coil on shaft 11.2. The energy is then transferred from this electrical coil on shaft 11.2 to the locking device 12.3 via an electrical conductor located on shaft 11.2.

[0353] The energy required for the operation of the locking device 12.4 is electrically transmitted from the electrical conductor located on shaft 11.2 to another electrical coil on shaft 11.2 and then inductively transmitted from this second electrical coil on shaft 11.2 to an electrical coil on shaft 11.3. The energy is then transmitted from this electrical coil on shaft 11.3, via an electrical conductor located on shaft 11.3, to the locking device 12.4.

[0354] The locking devices 12.1 and 12.5 are controlled by the main electronic control unit, which is connected to them via electrical conductors.

[0355] The locking devices 12.2, 12.3, and 12.4 are controlled by the main electronic control unit. The transmission path for the energy transferred electrically and, in some sections, via electromagnetic induction for the operation of the locking devices is used equally for bidirectional communication between the main electronic control unit and the electronic control units of the locking devices 12.2, 12.3, and 12.4. The electronic control units of the locking devices 12.2, 12.3, and 12.4 are standard, state-of-the-art control units.

[0356] The method for operating and changing the transmission ratio, i.e., for shifting gears, of the drive unit 1 according to the invention in the second embodiment, is shown in Fig. 2, comprises the method for operating and changing the transmission ratio of the drive unit 1 according to the invention in the first embodiment, as illustrated in Fig. 1, and additionally incorporates the information, in particular values ​​of physical quantities, obtained using the delay unit 26 and the electronic main control unit by the sensor units associated therewith. The method thus enables the operation and modification of the transmission ratio of the drive unit 1 according to the invention in vehicles despite strong fluctuations of forces, in particular torques, acting on the output shaft 11.5 from outside the housing due to very uneven surfaces.

[0357] Such strong fluctuations can lead to the switching position of locking devices 12 not being able to be maintained, and thus the establishment or release of the positive locking of the two positive locking elements 13b and 13c of the locking device 12 to be switched cannot take place, and thus the switching of locking devices 12 for the purpose of changing the transmission ratio of the drive unit 1 according to the invention is prevented.

[0358] It can also lead to an increase in the time required to switch all the locking devices 12 that are to be switched for changing the transmission ratio of the drive unit 1 according to the invention.

[0359] On both sides of the deceleration unit 26, sensor units are arranged with respect to the force flow on the output shaft of the multi-start planetary gear unit. These sensor units are assigned to the electronic main control unit and transmit information, in particular values ​​of physical quantities, to the electronic main control unit via communication links. From this information, the electronic main control unit can derive speed and torque differences with respect to the speeds present on both sides of the deceleration unit 26 and the forces acting on both sides of the deceleration unit 26, in particular torques, and their time offset, also taking into account the characteristic data of the deceleration unit 26 stored in the electronic main control unit.Taking into account the technical characteristics of the deceleration unit 26 stored in the electronic main control unit in the usual manner, the rotational speeds with respect to the force flow on both sides of the deceleration unit 26 are determined in the exemplary embodiment, and from this the torques with respect to the force flow on both sides of the deceleration unit 26 and the transmission period of the torque between both sides of the deceleration unit 26 with respect to the force flow are derived.

[0360] This gives the electronic main control unit more time for calculations required in connection with the regulation, control and monitoring of the switching of locking devices 12 when torque fluctuations occur on the output shaft of the multi-start planetary gear due to forces, in particular torques, acting on the output shaft of the multi-start planetary gear from outside the housing.This time advantage in the program-controlled regulation and monitoring of the switching of the locking devices 12, the establishment and maintenance of the switching position of the locking elements 13b and 13c of the locking devices 12 in preparation for switching as a sub-process of a gear change, i.e., the change of the transmission ratio of the drive unit 1 according to the invention, ensures trouble-free operation and trouble-free change of the transmission ratio of the drive unit 1 according to the invention despite forces, in particular torques, acting dynamically from outside the housing on the output shaft of the multi-start planetary gear.

[0361] Furthermore, the delay unit 26 averages the amplitude of fluctuating torques acting from the multi-start planetary gear via the output shaft of the multi-start planetary gear to outside the housing, and thus fluctuating speeds at the output shaft of the multi-start planetary gear, as well as the amplitude of torques acting in the opposite direction to the power flow from outside the housing via the delay unit 26 to the output shaft 11.5, and thus fluctuating speeds.

[0362] A third embodiment of the drive unit 1 according to the invention, wherein the electrically operated drives 15 are designed as external rotors, with three gears, is described in Fig. 4 is shown and will be discussed below with reference to the Fig. 3 explained.

[0363] Due to the electrically operated drives 15 being designed as external rotors, this design differs in part from the design of the second embodiment and is described below.

[0364] The third embodiment consists of an electronic main control unit, a housing containing two electrically operated drives 15, each consisting of rotor 5.1 and stator 4.1 and rotor 5.2 and stator 4.2, a multi-start planetary gear consisting of a planetary gear set and five locking devices 12, which, for the purpose of differentiation, are referred to in the further description of the embodiment as the locking devices 12.1, 12.2, 12.3, 12.4, 12.5 and which are Fig. Figure 4 shows the multi-start planetary gear set. This set consists of a planetary gear set arranged coaxially to the main shaft 2. In this exemplary embodiment, the planetary gear set comprises a ring gear 10, a carrier gear 8 with planet gears, and a sun gear 7.

[0365] The total rated power of the electrically operated drives 15 of the drive unit 1 according to the invention is distributed as shown in Table 2. The ratio of the number of teeth of sun gear 7 to the number of teeth of ring gear 10 is approximately 1 to 1.618.

[0366] The maximum achievable rotational speeds of rotor 5.1, rotor 5.2 and the rotational speed of the output shaft 11.5 are approximately the same.

[0367] In this embodiment of the drive unit 1 according to the invention, the planetary gear of the multi-start planetary gear is driven via rotor 5.1 and rotor 5.2.

[0368] Stator 4.1 and stator 4.2 of the electrically operated drives 15 of the drive unit 1 according to the invention are rigidly connected to the stationary support shaft 14. The stationary support shaft 14 is rigidly connected to the housing. The stationary support shaft 14 lies on the main shaft 2, which in Fig.4 is not shown.

[0369] Furthermore, the drive unit 1 includes shaft 11.1, shaft 11.2, shaft 11.3 and shaft 11.4, these shafts serving to connect the components of the planetary gear, the locking devices 12.1, 12.2, 12.3, 12.4, 12.5 and the rotors 5.1 and 5.2, and the output shaft 11.5. The axes of rotation of these shafts correspond to the main axis 2.

[0370] In this embodiment and in other possible embodiments with a multi-start planetary gear unit consisting of only one planetary gear unit, the output shaft 11.5 is, by design, also the output shaft of the multi-start planetary gear unit and also the output shaft of the drive unit 1 according to the invention.

[0371] Furthermore, the drive unit 1 includes torque transmitter 6.1 and drive input segment 3.1, as well as torque transmitter 6.2 and drive input segment 3.2. In this embodiment, these are not designed as separate components. In this embodiment, shaft 11.2 performs the function of torque transmitter 6.1 and drive input segment 3.1, and shaft 11.3 performs the function of torque transmitter 6.2 and drive input segment 3.2.

[0372] The fixed support axis 14 is rigidly connected to the housing and lies on the main axis 2, which is in Fig. 4 is not shown.

[0373] The shaft 11.1 is rotatably mounted as a hollow shaft on the stationary support axis 14 and is rigidly connected to the sun gear 7, the positive locking element 13b of the locking device 12.1 (the positive locking element 13c of the locking device 12.1 having a fixed connection to the stationary support axis 14), and the positive locking element 13b of the locking device 12.2 (the positive locking element 13c of the locking device 12.2 having a fixed connection to the shaft 11.2). The shaft 11.2 is designed as a hollow shaft and rotatably mounted on the stationary support axis 14. The shaft 11.2 is rigidly connected to the rotor 5.1 and the positive locking element 13b of the locking device 12.3 (the positive locking element 13c of the locking device 12.3 having a fixed connection to the shaft 11.3). The shaft 11.3 is fixed to the rotor 5.2 and the positive locking element 13b of the locking device 12.4 connected, wherein the positive locking element 13c of the locking device 12.4 has a fixed connection with the shaft 11.4. The shaft 11.3 is designed as a hollow shaft and rotatably mounted on the stationary support axis 14.

[0374] The shaft 11.4 represents a form of the ring gear 10 and is rotatably mounted on the stationary support axis 14 and the output shaft 11.5 and is firmly connected to the positive locking element 13b of the locking device 12.5, wherein the positive locking element 13c of the locking device 12.5 has a fixed connection with the housing.

[0375] The output shaft 11.5 is rotatably mounted in the housing and is rigidly connected to the carrier wheel 8 of the planetary gear of the multi-start planetary gear.

[0376] The direction of rotation of rotor 5.1, rotor 5.2 and the output shaft 11.5 is the same when the planetary gear of the multi-start planetary gear is driven in the exemplary embodiment.

[0377] The locking devices 12.1, 12.2, 12.3, 12.4, 12.5 each comprise at least one actuator 13a, which is electromechanically operated, and at least two positive locking elements, namely the 1st positive locking element 13b and the 2nd positive locking element 13c, wherein the positive locking of the positive locking elements 13b and 13c can be established or released by the actuator 13a.

[0378] In the closed locking devices 12, there is a sufficiently large, customary clearance between the positive locking elements 13b and 13c of the locking devices 12 to enable the positive locking of the positive locking elements 13b and 13c to be released or restored.

[0379] The locking devices 12.2, 12.3 and 12.4 each have electronic control units.

[0380] In the third embodiment, the locking devices 12.1, 12.2, 12.3, 12.4, 12.5 are electrically operated in the usual manner. This is done as described in the second embodiment.

[0381] The locking devices 12.1, 12.2, 12.3, 12.4 and 12.5 are controlled by the main electronic control unit. This is done as described in the second embodiment.

[0382] The operating principle and thus the method for operating and changing the transmission ratio, i.e., for shifting gears, of the drive unit 1 according to the invention in the third embodiment corresponds to the operating principle and thus the method for operating and changing the transmission ratio, i.e., for shifting gears, of the drive unit 1 according to the invention in the second embodiment.

[0383] A fourth embodiment of the drive unit 1 according to the invention, with three gears, is shown in Fig. Figure 5 shows the assembly and it consists of a housing containing two drives 15, a multi-stage planetary gear unit, and five mechanical switching elements. In the fourth embodiment, these five mechanical switching elements are the backstops 21, 25, the disengageable overrunning clutches 22, 24, and the friction clutch 23.

[0384] The torque of the drives 15 is provided by muscle power, whereby the torque provided by each drive 15 and their speed are subject to fluctuations. The two drives 15 are also operated independently of each other.

[0385] Disengageable overrunning clutches 22, 24 according to the invention are overrunning clutches according to the prior art which can be brought into a state in which neither torques can be transmitted in the clockwise nor the counterclockwise direction of rotation between the shafts or components that can be coupled by the disengageable overrunning clutch, i.e., the power flow there can be interrupted regardless of the direction of rotation. If a disengageable overrunning clutch according to the invention is engaged, it can transmit torques in one direction of rotation between the shafts or components that can be coupled by the disengageable overrunning clutch.

[0386] The multi-stage planetary gear consists of a planetary gear arranged coaxially to the main shaft 2. In the exemplary embodiment, the planetary gear is composed of a ring gear 10, a carrier gear 8 with planet gears, and a sun gear 7.

[0387] In this embodiment of the drive unit 1 according to the invention, the planetary gear of the multi-start planetary gear is driven via the drives 15.

[0388] Furthermore, the drive unit 1 includes shaft 11.1, shaft 11.2, shaft 11.3, and shaft 11.4, which serve to connect the components of the planetary gear set, the mechanical switching elements (i.e., the backstops 21, 25, the disengageable overrunning clutches 22, 24, and the drive input segments 3.1, 3.2), and the output shaft 11.5. The axes of rotation of these shafts lie on the main axis 2 (not shown in Figure 1). Fig. 5. Furthermore, the drive unit 1 includes the shaft 11.6 and the shaft 11.7, these shafts serving to connect the drives 15 with torque transmitter 6.1, torque transmitter 6.2 and the friction clutch 23.

[0389] In this embodiment and in other possible embodiments with a multi-start planetary gear unit consisting of only one planetary gear unit, the output shaft 11.5 is, by design, also the output shaft of the multi-start planetary gear unit and also the output shaft of the drive unit 1 according to the invention.

[0390] The backstop 21 has a fixed connection with the housing and is arranged on shaft 11.1 and on the housing in such a way that it can block the shaft 11.1 in one direction of rotation against the housing.

[0391] The switchable overrunning clutch 22 is arranged on shaft 11.1 and shaft 11.2 such that power transmission between shaft 11.1 and shaft 11.2 can be established via it. It is arranged such that when it is engaged and drive input segment 3.1 rotates in the direction of rotation of output shaft 11.5 and shaft 11.2 has the same rotational speed as shaft 11.1, shafts 11.1 and 11.2 are coupled.

[0392] The friction clutch 23 is arranged on torque transmitter 6.1 and torque transmitter 6.2 in such a way that the power flow between drive input segment 3.1 and drive input segment 3.2 can be established via torque transmitter 6.1 and torque transmitter 6.2.

[0393] Once this power flow is established, it is referred to as activated within the meaning of the invention. If this power flow is interrupted by the friction clutch 23, the friction clutch 23 is referred to as deactivated within the meaning of the invention.

[0394] The switchable overrunning clutch 24 is arranged on shaft 11.3 and shaft 11.4 such that power transmission between shaft 11.3 and shaft 11.4 can be established via it. It is arranged such that when it is engaged and drive input segment 3.2 rotates in the direction of rotation of the output shaft 11.5 and shaft 11.3 has the rotational speed of shaft 11.4, shafts 11.3 and 11.4 are coupled.

[0395] The backstop 25 has a fixed connection with the housing and is arranged on shaft 11.4 and on the housing in such a way that it can block the shaft 11.4 in one direction of rotation against the housing.

[0396] The switchable overtaking clutch 22, the friction clutch 23 and the switchable overtaking clutch 24 are operated in the usual manner.

[0397] The drive unit 1 comprises a torque transmitter 6.1 and a torque transmitter 6.2, wherein the torque transmitter 6.1 serves to connect the shaft 11.2 to the shaft 11.6 and the torque transmitter 6.2 serves to connect the shaft 11.3 to the shaft 11.7.

[0398] In the fourth embodiment, torque transmitters 6.1 and 6.2 are designed as belt drives according to the state of the art.

[0399] The shaft 11.1 is rotatably mounted in the housing and rigidly connected to the sun gear 7, the backstop 21, and the disengageable overrunning clutch 22, the disengageable overrunning clutch 22 also having a rigid connection to the shaft 11.2. The shaft 11.2 is designed as a hollow shaft and rotatably mounted on the shaft 11.1.

[0400] Shaft 11.2 remains rigidly connected to the drive input segment 3.1 and the torque transmitter 6.1. The torque transmitter 6.1 remains rigidly connected to the friction clutch 23 and shaft 11.6. Shaft 11.6 remains rigidly connected to a drive 15.

[0401] Shaft 11.3 is rigidly connected to the drive input segment 3.2 and the torque transmitter 6.2. The torque transmitter 6.2 is further connected to the friction clutch 23 and shaft 11.7. Shaft 11.7 is also rigidly connected to a drive 15. Shaft 11.3 is designed as a hollow shaft and is rotatably mounted on shaft 11.1.

[0402] The shaft 11.4 represents a form of the ring gear 10 and is rotatably mounted on the shaft 11.1 and the output shaft 11.5 and is rigidly connected to the backstop 25, which has a fixed connection to the housing, and the disengageable overrunning clutch 24.

[0403] The output shaft 11.5 is designed as a hollow shaft and is rotatably mounted on the shaft 11.1 and is firmly connected to the carrier wheel 8 of the planetary gear of the multi-start planetary gear.

[0404] The direction of rotation of drive input segment 3.1, drive input segment 3.2 and output shaft 11.5 is the same when the planetary gear of the multi-start planetary gear is driven by the drives 15 in the exemplary embodiment.

[0405] The operation and the changing of the transmission ratio, i.e., the shifting of gears, of the drive unit 1 according to the invention in the fourth embodiment is explained below with reference to the various shifting states and their transitions. The description proceeds from the first gear with the highest torque in relation to the total power of the two drives 15 on the output shaft of the multi-start planetary gear to the third gear with the lowest torque in relation to the total power of the drives 15 on the output shaft of the multi-start planetary gear.

[0406] If a vehicle driven by the drive unit 1 according to the invention in the fourth embodiment is to be accelerated, the process is as follows.

[0407] For the sake of simplicity, the following explanations will refer exclusively to the drive by the relevant drive 15 or the drive by the relevant drives 15.

[0408] The friction clutch 23 and the switchable overtaking clutches 22 and 24 are actuated and controlled according to the state of the art.

[0409] The backstop 21 blocks the sun gear 7 and the backstop 25 blocks the ring gear 10, each against the housing and opposite to the direction of rotation of the drive input segments 3.1 and 3.2, and thus of the output shaft 11.5 ( Fig. 5).

[0410] The two drives 15 serve individually or jointly to drive the output shaft of the multi-start planetary gear of the drive unit 1 according to the invention via the planetary gear of the multi-start planetary gear.

[0411] The two drives 15, in conjunction with torque transmitter 6.1, torque transmitter 6.2, drive input segment 3.1 and drive input segment 3.2, serve to prepare the switching of the switchable overtaking clutch 22 and the switchable overtaking clutch 24, and further, in conjunction with the switchable overtaking clutch 22, the switchable overtaking clutch 24, the friction clutch 23, the backstop 21 and the backstop 25, to change the transmission ratio of the drive unit 1 according to the invention.

[0412] In first gear, the switchable overtaking clutch 22 is engaged, the friction clutch 23 is activated, and the switchable overtaking clutch 24 is disengaged.

[0413] The drives 15 drive the torque transmitters 6.1 and 6.2 in the direction of rotation of the output shaft 11.5. The drive is alternating between uniform and uneven torque application. The two drives 15, drive input segment 3.1, drive input segment 3.2, torque transmitter 6.1 and torque transmitter 6.2 are coupled via the activated friction clutch 23.

[0414] Thus, the drives 15, via the engaged, disengageable overrunning clutch 22, drive the sun gear 7 in the direction of rotation of the output shaft 11.5. A reverse rotation of the ring gear 10 against the direction of rotation of the output shaft 11.5 is prevented by the backstop 25.

[0415] Thus, the sun gear 7 drives the carrier gear 8 and therefore the output shaft 11.5 via the planet gears.

[0416] The rotational speed of the sun gear 7 is now increased by the muscle forces acting on the drives 15. This continues until the maximum rotational speed that can be achieved by the two drives 15 is reached.

[0417] The change from first gear to second gear, i.e., this change in the gear ratio of the drive unit 1, is effected by switching off the switchable overtaking clutch 22, deactivating and activating the friction clutch 23 and switching on the switchable overtaking clutch 24 and takes place in different phases, during which the output shaft 11.5 continues to be in a rotary motion and is driven via the multi-gear planetary gear.

[0418] In the first phase of the gear change, the planetary gear of the multi-stage planetary gear – in this embodiment – ​​continues to be driven by the two drives 15.

[0419] The friction clutch 23 is now actuated according to the state of the art and thus deactivated. As a result, the drive input segments 3.1 and 3.2 are no longer coupled via the friction clutch 23.

[0420] The drive 15, to which torque transmitter 6.2 is attached, no longer serves to drive the multi-start planetary gear. The sun gear 7, and thus the multi-start planetary gear, continues to be driven via the drive 15, to which torque transmitter 6.1 is attached.

[0421] In the second phase, the drive 15, to which the torque transmitter 6.2 is attached, no longer serves to drive the multi-stage planetary gear, but is used to prepare for engaging the disengageable overrunning clutch 24. For this purpose, the rotational speed provided by the drive 15, which is associated with the drive input segment 3.2, must be lower in the direction of rotation of the output shaft 11.5 than the rotational speed of the ring gear 10 in the direction of rotation of the output shaft 11.5. In this embodiment, this is achieved by muscle forces acting on the drive 15, which acts on the drive input segment 3.2 via the torque transmitter 6.2, providing the required rotational speed. Since the ring gear 10 is blocked by the backstop 25, its rotational speed is zero. The muscle forces acting on the drive 15, which is associated with the torque transmitter 6.2 and thus also with the drive input segment 3.2, ensure that the required rotational speed is reached.2, the rotational speed of the drive input segment 3.2 is reduced to engage the disengageable overrunning clutch 24 until the direction of rotation of the drive input segment 3.2 is reversed relative to the direction of rotation of the output shaft 11.5. The overrunning clutch 24 is then engaged according to the state of the art.

[0422] In the third phase, as soon as the overrunning clutch 24 is engaged, the ring gear 10 is driven by muscle power via the drive 15, the torque transmitter 6.2, and the drive input segment 3.2. The ring gear 10 is set into a rotary motion in the direction of rotation of the output shaft 11.5. Simultaneously, the muscle power applied to the drive 15, which is assigned to the torque transmitter 6.1, is reduced until the rotational speed of the drive 15, which is assigned to the torque transmitter 6.1, is zero. This also reduces the rotational speed of the sun gear 7 to zero. Reverse rotation of the sun gear 7 against the direction of rotation of the output shaft 11.5 is prevented by the backstop 21. Now, a lower torque than required to drive the drive unit 1 is applied by muscle power to the drive 15, which is assigned to the torque transmitter 6.1, in the opposite direction of rotation of the output shaft 11.5.5 is provided so that the disengageable overrunning clutch 22 is no longer jammed and can now be disengaged. The disengageable overrunning clutch 22 is now disengaged in the usual manner according to the state of the art. The ring gear 10, and thus the multi-stage planetary gear, continues to be driven at this point by the muscle force acting on the drive 15, which is assigned to the torque transmitter 6.2.

[0423] In the fourth phase, the multi-stage planetary gear continues to be driven via the drive 15, the associated torque transmitter 6.2, the drive input segment 3.2, and thus via the ring gear 10. Now, the friction clutch 23 is activated in the usual manner according to the state of the art. As soon as the friction clutch 23 is activated, the ring gear 10 is further driven by the forces acting simultaneously on the two drives 15. The ring gear 10 drives the carrier gear 8 and thus the output shaft 11.5 via the planet gears.

[0424] This completes the shifting process from first gear to second gear.

[0425] The rotational speed of the ring gear 10 is now increased by the muscle forces acting on the drives 15. This continues until the maximum rotational speed that can be achieved by the two drives 15 is reached.

[0426] The change from second gear to third gear, i.e., this change in the gear ratio of drive unit 1, is achieved by The switching on of the switchable overrunning clutch 22 and the deactivation and activation of the friction clutch 23 takes place in different phases, during which the output shaft 11.5 continues to be in a rotary motion and is driven via the multi-gear planetary gear.

[0427] In the first phase of the gear change, in this embodiment, the two drives 15 continue to drive the ring gear 10 and thus the multi-start planetary gear via the torque transmitter 6.2 and the drive input segment 3.2.

[0428] The friction clutch 23 is now actuated according to the state of the art and thus deactivated. Therefore, the drive input segments 3.1 and 3.2 are no longer coupled via the friction clutch 23.

[0429] The drive 15, to which torque transmitter 6.1 is attached, no longer serves to drive the multi-start planetary gear. The ring gear 10, and thus the multi-start planetary gear, continues to be driven via the drive 15, to which torque transmitter 6.2 is attached.

[0430] In the second phase, the drive 15, to which the torque transmitter 6.1 is attached, no longer serves to drive the multi-stage planetary gear, but is used to prepare for engaging the disengageable overrunning clutch 22. For this purpose, the rotational speed provided by the drive 15, which is associated with the drive input segment 3.1, must be lower in the direction of rotation of the output shaft 11.5 than the rotational speed of the ring gear 10 in the direction of rotation of the output shaft 11.5. In this embodiment, this is achieved by muscle forces acting on the drive 15, which acts on the drive input segment 3.1 via the torque transmitter 6.1, providing the required rotational speed. Since the sun gear 7 is blocked by the backstop 21, its rotational speed is zero. The muscle forces acting on the drive 15, which is associated with the torque transmitter 6.1 and thus also with the drive input segment 3.1, ensure that the required rotational speed is reached.When the drive input segment 3.1 is assigned to the output shaft 11.5, the rotational speed of the drive input segment 3.1 is reduced to engage the disengageable overrunning clutch 22 until the direction of rotation of the drive input segment 3.1 is reversed relative to the direction of rotation of the output shaft 11.5. The overrunning clutch 22 is then engaged according to the state of the art.

[0431] In the third phase, once the overrunning clutch 22 is engaged, muscle power is transmitted via the drive 15, the torque transmitter 6.1, and the drive input segment 3.1 to drive the sun gear 7. The sun gear 7 is set into a rotary motion in the direction of rotation of the output shaft 11.5. Simultaneously, the muscle power applied to the drive 15, which is assigned to the torque transmitter 6.2, is reduced until the rotational speeds of the two drives 15 are approximately equal, in order to synchronize them.

[0432] As soon as the rotational speeds of the two drives 15 and thus also the rotational speeds of sun gear 7 and ring gear 10 are approximately equal, the friction clutch 23 is activated in the usual way according to the state of the art.

[0433] This completes the shifting process from second gear to third gear.

[0434] The rotational speed of the ring gear 10 and the sun gear 7 is now increased by the muscle forces acting on the drives 15. This continues until the maximum rotational speed that can be achieved by the two drives 15 is reached.

[0435] In third gear, the ring gear 10 and the sun gear 7 jointly drive the carrier gear 8 and thus the output shaft 11.5 via the planet gears. The drive to these two components of the planetary gear set, i.e., the sun gear 7 and the ring gear 10, of the multi-stage planetary gear set, is effected by both drives 15. However, due to the activated friction clutch 23, the drive can also be effected by only one of the two drives 15, or, depending on the available muscle power at the two drives 15, by both drives 15 together, with different torques provided by different muscle power and thus different torques at the drives 15. List of reference symbols 1 drive unit 2 Main axis 3.1 Drive input segment 3.2 Drive input segment 4.1 Stator 4.2 Stator 5.1 Rotor 5.2 Rotor 6.1 Torque Transducer 6.2 Torque Transducer 7 Sun wheel 8 Carrier wheel 10 Ring gear 11.1 Wave 11.2 Wave 11.3 Wave 11.4 Wave 11.5 Output shaft 11.6 wave 11.7 Wave 12 Locking device 12.1 Locking device 12.2 Locking device 12.3 Locking device 12.4 Locking device 12.5 Locking device 13a Actuator 13b 1. positive locking element 13c 2. positive locking element 14 fixed support axis 15 Drive 21 Backstop 22 Disengageable overtaking clutch 23 Friction clutch 24 switchable overtaking clutches 25 Backstop 26 Delay unit

Claims

[1] Drive unit (1) at least comprising - at least two drives (15), - at least a housing, at least arranged within it - at least two drive input segments (3) arranged coaxially to the main axis (2), - wherein each drive input segment (3) has at least one torque transmitter (6), - a multi-stage planetary gear system, comprising - at least one planetary gear set arranged coaxially to the main axis (2), comprising at least - a ring gear (10), - a carrier wheel (8), - a sun wheel (7) - and an output shaft (11.5), - and at least five mechanical switching elements, wherein the sun gear (7), the carrier gear (8) or the ring gear (10) is non-rotatably connected to the output shaft (11.5), characterized by , that Each torque transmitter (6) and the drive input segment (3) connected to the torque transmitter (6) is assigned at least one drive (15), the at least two drive input segments (3) can be coupled to each other by at least one mechanical switching element, Each of the at least two drive input segments (3) can be coupled separately to at least one component of at least one planetary gear set of the multi-start planetary gear set, namely ring gear (10), carrier gear (8) or sun gear (7), by means of a mechanical switching element in a rotationally fixed manner, wherein the at least two drive input segments (3) can be coupled to different components of at least one planetary gear set of the multi-start planetary gear set, namely either sun gear (7) and carrier gear (8) or sun gear (7) and ring gear (10) or carrier gear (8) and ring gear (10), which are not connected to the output shaft (11.5) of the planetary gear set of the multi-start planetary gear set. the two components of at least one planetary gear of the multi-start planetary gear which are not connected to the output shaft (11.5), namely either the sun gear (7) and the carrier gear (8) or the sun gear (7) and the ring gear (10) or the carrier gear (8) and the ring gear (10), each of which can be locked in at least one direction of rotation by at least one mechanical switching element which has a fixed connection with the housing, the at least two drives (15) of the drive input segments (3) are electrically operable, the drive unit (1) comprises at least one electronic main control unit, and the electrically operable drives (15) of the drive input segments (3) can be used independently of one another both to drive the multi-start planetary gear set and in conjunction with the mechanical switching elements and the electronic main control unit to change the transmission ratio of the drive unit (1), the mechanical switching elements of the at least five mechanical switching elements, by which the at least two drive input segments (3) can be coupled in a rotationally fixed manner to the components of the planetary gear of the multi-start planetary gear that are not connected to the output shaft (11.5), namely either the sun gear (7) and the carrier gear (8) or the sun gear (7) and the ring gear (10) or the carrier gear (8) and the ring gear (10), are locking devices (12), wherein the at least two electrically operated drives (15) of the drive unit (1) can be used in conjunction with the main electronic control unit for positioning the positive locking elements (13b) and (13c) of the locking devices (12). and wherein the at least two electrically operated drives (15) of the drive unit (1) can be used in conjunction with the main electronic control unit to hold the switching position of the positive locking elements (13b) and (13c) of the locking devices (12). [2] Drive unit (1) according to claim 1 characterized by , that the mechanical switching elements of the at least five mechanical switching elements, by which the two components of at least one planetary gear of the multi-start planetary gear, which are not connected to the output shaft (11.5), can be blocked, are locking devices (12). [3] Drive unit (1) according to claim 2 characterized by that the at least five mechanical switching elements are locking devices (12). [4] Drive unit (1) according to one of claims 1, 2 or 3, characterized by , that a delay unit (26) is arranged on the output shaft of the multi-start planetary gear. [5] Method for operating and changing the transmission ratio of a drive unit (1) according to one of claims 1, 2, 3 or 4, characterized by, that the electrically operated drives (15) of the drive input segments (3) are used independently of each other both to drive the multi-start planetary gear and in conjunction with the mechanical switching elements and the electronic main control unit to change the transmission ratio of the drive unit (1), wherein the at least two electrically operated drives (15) of the drive unit (1) are usable in conjunction with the electronic main control unit for positioning the positive locking elements (13b) and (13c) of the locking devices (12) and wherein the at least two electrically operated drives (15) of the drive unit (1) are used in conjunction with the electronic main control unit to hold the switching position of the positive locking elements (13b) and (13c) of the locking devices (12). [6] Method according to claim 5, characterized by, that during the switching of a locking device (12) in the course of changing the transmission ratio of the drive unit (1) the output shaft of the multi-start planetary gear is driven by at least one of the electrically operated drives (15) of the drive unit (1). [7] Method according to claim 5, characterized in that during the switching of a locking device (12) in the course of changing the transmission ratio of the drive unit (1), the multi-start planetary gear is driven for recuperation by torques acting on the multi-start planetary gear from outside the housing via the output shaft of the multi-start planetary gear. [8] Method according to claim 5, 6 or 7, characterized by, that the torques determined at the output shaft of the multi-start planetary gear with respect to the power flow before and after the deceleration unit (26) by means of the sensor units of the electronic main control unit are used by the electronic main control unit to determine torque and speed differences and their time offset with respect to the power flow before and after the deceleration unit (26) and, with the aid of this information, to reduce the switching times of the locking devices (12) and thus also the time required for changing the transmission ratio of the drive unit (1) according to the invention. [9] Method according to any one of claims 5, 6, 7 or 8, characterized by, that an amount of electrical energy is inductively transferred from an electrical conductor on the housing to an electrical conductor on a rotatable shaft of the drive unit (1), at least in order to electrically operate a locking device (12) on this rotatable shaft, by which a rotationally fixed connection between two rotatable shafts of the drive unit (1) can be established. [10] Method according to claim 9, characterized by, that an electrical energy is inductively transferred from an electrical conductor on a rotatable shaft of the drive unit (1), in which a voltage is inductively generated, via a further electrical conductor electrically connected to this electrical conductor, to an electrical conductor on a further rotatable shaft of the drive unit (1), at least in order to electrically operate a locking device (12) on this rotatable shaft, by which a rotationally fixed connection between two rotatable shafts of the drive unit (1) can be established. [11] Method according to claim 9 or 10, characterized by, that the transmission path for the amount of energy transmitted electrically or according to the principle of electromagnetic induction for the operation of the locking devices (12) is used equally for the bidirectional communication between the main electronic control unit and at least the electronic control units of the locking devices (12), which can establish a rotationally fixed connection between two rotatable or rotating shafts of the drive unit (1). [12] Use of the drive unit (1) according to one of claims 1, 2, 3 or 4 for driving motor vehicles, rail vehicles, aircraft and watercraft, or as a generator for wind or hydropower plants.

Images