• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a method for controlling a hybrid driveline (3), comprising a gearbox (2) with an input shaft (8) and an output shaft (20); a first planetary shaft (10) coupled to the input shaft (8); a second planetary gear (12) coupled to the first planetary gear (10); a first electric machine (14) coupled to the first plane shaft (10); a second electrical machine (16) coupled to the second planetary gear (12); a first gear pair (60) and a third gear pair (72) disposed between the first plane shaft (10) and the output shaft (20); and a second gear pair (66) disposed between the second planetary shaft (12) and the output shaft (20), an internal combustion engine (4) being coupled to the first planetary shaft (10) via the input shaft (8). The method comprises the steps of: a) disengaging the first gear pair (60); b) connecting the first planetary shaft (10) to the output shaft (20) by means of a coupling mechanism (96); c) disengaging a fifth gear pair (21) connected to the output shaft (20) and a side shaft (18); d) transmitting a torque from the second planetary shaft (12) to the side shaft (18) via the second shaft pair (66); and e) transmitting a torque from the side shaft (18) to the output shaft (20) via the third pair of gears (72). The invention also relates to a computer program (P) for controlling a hybrid driveline (3) and a computer program product comprising program code for an electronic control unit (48) or other computer (53) for implementing the method according to the invention. (Fig. 2)
    公开号:SE1450314A1
    申请号:SE1450314
    申请日:2014-03-20
    公开日:2015-09-21
    发明作者:Johan Lindström；Mathias Björkman；Niklas Pettersson；Mikael Bergquist
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    BACKGROUND OF THE INVENTION AND TECHNICAL ART The present invention relates to a method for controlling a hybrid driveline according to the preamble of claim 1. The invention also relates to a vehicle, which comprises such a hybrid driveline according to the preamble of claim 11, a computer program for controlling such a hybrid driveline according to the preamble of claim 12, and a computer program product comprising program code according to the preamble of claim 13.
    Hybrid vehicles can be driven by a primal engine, which can be an internal combustion engine, and a secondary engine, which can be an electric machine. The electrical machine is equipped with at least one energy store, such as an electrochemical energy store for storing electrical energy and control equipment for regulating the flow of electrical energy between the energy store and the electrical machine. The electric machine can thus alternately work as a motor and generator depending on the operating condition of the vehicle. When the vehicle is braked, the electric machine generates electrical energy which is stored in the energy store. This is usually called regenerative braking, which means that the vehicle is braked with the help of the electric machine and the internal combustion engine. The stored electrical energy is later used for operation of the vehicle.
    A planetary gear usually comprises three components which are rotatably arranged in relation to each other, namely a sun gear, a planet gear holder and a ring gear. With knowledge of the number of teeth of the sun gear and the ring gear, the onboard speeds of the three components can be determined during operation. One of the components of the planetary shaft may be connected to an output shaft of an internal combustion engine. This component of the planetary shaft thus rotates at a speed corresponding to the speed of the output shaft of the internal combustion engine. A second component of the planetary gear may be connected by an input shaft to a gearbox. This component of the planetary shaft thus rotates at the same speed as the input shaft of the gearbox. A third component of the planetary gear is to provide hybrid operation connected to a rotor of an electric machine. This component of the planetary shaft thus rotates at the same speed as the rotor of the electric machine if they are directly connected 2 to each other. Alternatively, the electrical machine may be connected to the third component of the planetary gear via a transmission having a gear ratio. In this case, the electric machine and the third component of the planetary gear can rotate at different speeds. The speed and / or torque of electrical machines can be regulated steplessly. During operating cases when the input shaft to the gearbox is to be given a desired speed and / or torque, a control unit calculates, with knowledge of the combustion engine speed, the speed at which the third component must be driven in order for the input shaft to the gearbox to obtain the desired speed. . A control unit activates the electric machine, so that it gives the third component the calculated speed and thus the input shaft to the gearbox the desired speed.
    By coupling the output shaft of the internal combustion engine, the rotor of the electric machine and the input shaft of the gearbox to a planetary shaft, the conventional coupling mechanism can be avoided. When accelerating the vehicle, an increased torque must be delivered from the internal combustion engine and the electric machine to the gearbox and on to the vehicle's drive wheel. Since both the internal combustion engine and the electric machine are connected to the planetary gear, the greatest possible torque delivered by the internal combustion engine and the electric machine will be limited by any of these drives, the highest torque of which is lower than the other torque of the other drive. In the event that the maximum torque of the electric machine is lower than the maximum torque of the internal combustion engine, taking into account the gear ratio between them, the electric machine will not form a sufficiently large reaction torque to the planetary gear, which means that the internal combustion engine cannot transmit its highest torque to the gearbox. and on to the vehicle's drive wheel. Thus, the highest transferable torque to the gearbox is limited by the strength of the electric machine. This is also evident from the so-called planetary equation.
    Utilizing a conventional clutch that disengages the input shaft of the gearbox from the internal combustion engine during gearing processes in the gearbox entailed disadvantages, such as heating of the clutch slats, which results in wear of the clutch slats and also an increased fuel consumption. In addition, a conventional coupling mechanism is relatively heavy and expensive. It also occupies a relatively large space in the vehicle.
    In a vehicle, the available space for the drive device is often limited. If the drive device comprises a plurality of components, such as an internal combustion engine, an electric machine, a gearbox and a planetary gear, the construction must be compact. In the case of additional components, such as a regenerative braking device, there should be no requirement that the components included in the drive device have a compact construction. At the same time, the components included in the drive device must be designed with dimensions that can absorb the required forces and torques.
    For certain types of vehicles, especially heavy trucks and buses, a large number of gear steps are required. This increases the number of components in the gearbox, which must also be dimensioned to be able to absorb large hails and torques that occur in such heavy vehicles. This results in an increase in the size and weight of the wax lane.
    There are also requirements for high reliability and high operational reliability of the components that are in the drive device. In the event that the gearbox contains lamella couplings, wear occurs, which affects the gearbox's reliability and service life.
    In regenerative braking, kinetic energy is converted into electrical energy, which is stored in an energy store, such as accumulators. One factor that affects the service life of the energy storage is the number of cycles that the energy storage tiff & and absorbs power to and from the electrical machines. The more cycles, the shorter the lifespan of the energy store.
    Under certain operating conditions, it is undesirable to shut down the internal combustion engine in order to save fuel and to avoid cooling of the internal combustion engine exhaust after-treatment system. The vehicle is then propelled by the electric machine. If additional torque is added to the hybrid driveline or if the energy storage must be charged, the internal combustion engine must be started quickly and efficiently.
    The document EP-B 1-1126987 shows a gearbox with double planetary gearboxes. The sun gear of each planetary gear is connected to an electric machine and the ring wheels of the planetary gear are connected to each other. The planetary gear bearings of each planetary gear are connected to a number of pairs of gear shafts, in such a way that an infinite number of gear shaft steps are obtained. Another document, EP-B1-1280677, also shows how the planetary gears can be bridged with a gear step arranged on the output shaft of the internal combustion engine. 4 The document US-A1-20050227803 shows a vehicle transmission with two electric machines, which are connected to the respective sun wheels of two planetary shafts. The planetary shafts have a common planetary gear carrier, which is connected to the input shaft of the transmission.
    Document WO2008 / 046185-A 1 shows a hybrid transmission with two planetary shafts, in which an electric machine is connected to one planetary shaft and a double coupling cooperates with the other planetary shaft. The two planetary gears also cooperate with each other via a gear transmission.
    SUMMARY OF THE INVENTION Despite known solutions in the art, there is a need to further develop a method for controlling a hybrid driveline, to provide shifting without torque interruption and optimal brake regeneration.
    The object of the invention is to provide a new and advantageous method for controlling a hybrid driveline.
    Another object of the invention is to provide a new and advantageous computer program for controlling a hybrid driveline.
    These objects are achieved by the method stated in the introduction, which can be characterized by the features stated in the characterizing part of claim 1.
    These objects are also achieved with the vehicle stated in the introduction, which can be characterized by the features stated in the marking part of claim 11.
    These objects are also achieved with the computer program for controlling the hybrid driveline, which can be characterized by the features stated in the characterizing part of claim 12.
    These objects are also achieved with the computer program product for controlling the hybrid driveline, which can be characterized by the features stated in the characterizing part of claim 13.
    The method according to the invention provides an efficient and reliable method for controlling a hybrid driveline, comprising a gearbox with an input shaft and an output shaft; a first planetary shaft, which is coupled to the input shaft; a second planetary gear, which is coupled to the first planetary gear; a first electric machine coupled to the first planetary gear; a second electric machine coupled to the second planetary shaft; a first gear pair and a third gear pair arranged between the first planetary gear and the output shaft; and a second gear pair disposed between the second planetary shaft and the output shaft, an internal combustion engine being coupled to the first planetary shaft via the input shaft.
    According to one embodiment, the method comprises the steps of disengaging the first gear pair, connecting the first planetary gear to the output shaft by means of a clutch mechanism, disengaging a fifth gear pair connected to the output shaft and a side shaft, transmitting a torque from the second planetary gear shaft to the second gear shaft. , and to transmit a torque from the side shaft to the output shaft via the third gear pair. In this way, a shift is achieved from one shift to another without interruption of torque.
    The first gear pair suitably comprises a first gear gear and a first gear in engagement with each other, which first gear gear is fixedly arranged with the first planetary gear and which first gear wheel can be arranged on and off the side shaft. The third pair of gears suitably comprises a third gear gear and a third gear engaged in engagement with each other, which third gear drive is fixedly arranged with the first planetary gear and which third gear has a type of engagement and disengagement arranged on the side shaft.
    The second pair of gears suitably comprises a second gear gear and a second gear engaged in engagement with each other, which second gear drive is fixedly arranged with the second planetary gear and which second gear is arranged on and coupled to the side shaft.
    Preferably, the step of disengaging the first gear pair comprises controlling the internal combustion engine and the first electric machine so as to provide a torqueless state between the first gear pair and the side shaft, after which a first coupling element is displaced so that the first gear pair is disengaged from the side shaft. The internal combustion engine and the first electric machine are controlled by light, so that a torque-free condition is achieved between the first gear of the first gear pair and the side shaft, after which the first coupling element is displaced so that the first gear is disengaged from the side shaft.
    Preferably, the step of connecting the first planetary shaft to the output shaft comprises providing a synchronous speed between a first main shaft connected to the first planetary shaft and the output shaft, after which the clutch mechanism is displaced so as to interconnect the first main shaft and the output shaft. Preferably, the internal combustion engine and / or the first electric machine are controlled so that a synchronous speed is achieved between the first main shaft and the output shaft.
    The step of disengaging the fifth gear pair from the side shaft comprises controlling the second electric machine, so that a torqueless state is created between the fifth gear pair and the side shaft, after which a fifth coupling element is displaced, so that the fifth gear pair is disengaged from the side shaft. The fifth pair of gears suitably comprises a fifth and sixth gear engaged with each other, which sixth gear is fixedly arranged at the output shaft and which fifth gear is coupled and disengaged on the side shaft by means of the fifth coupling element. Preferably, a torqueless state is created between the fifth gear and the side shaft, after which the fifth gear, and (with the fifth gear pair, the side shaft is disengaged.
    The method further comprises the step of, before transmitting a torque from the second planetary shaft to the side shaft, coupling the third gear pair to the side shaft. The connection is effected by controlling the second electric machine so that a synchronous speed is achieved between the side shaft and the third gear pair. a third coupling element is offset, so that it connects the third gear pair with the side shaft. Preferably, a synchronous speed is provided between the side shaft and the third gear of the third gear pair, after which the third clutch element is displaced so that the third gear is coupled to the side shaft.
    Preferably, the step of transmitting a torque from the second planetary shaft to the side shaft comprises controlling the first and / or the second electric machine so that torque balance is maintained in the first planetary shaft, after which a first coupling unit is displaced so as to disengage a first planetary shaft solar wheels and the first planet wheel holders apart. Then the internal combustion engine is controlled so that a synchronous speed is achieved 7 between a second sun gear arranged at the second planetary gear and a second planet gear holder, after which a second coupling unit is displaced so that it interconnects the second planet wheel holder and the second sun wheel.
    Torque balance refers to a condition in which a torque acts on a ring gear arranged at the planetary gear, corresponding to the product of the moment acting on the planetary gear bearing of the planetary gear and the gear ratio of the planetary gear while a torque acts on the planetary gear sun gear, corresponding to the torque shaft gear ratio). In the event that two of the planetary gear unit's integral parts, sun gear, ring gear or planet wheel holder, are connected by means of a coupling unit, no torque between the planetary gear unit parts is present opposite this torque balance. This allows the coupling unit on a single salt to be displaced and the integral parts of the planetary gear to be disengaged.
    The electrical machines, which are connected to the planetary shafts, can generate current and / or apply torque depending on the desired operating condition. The electrical machines can also supply each other with power during certain operating conditions.
    By connecting a first planet gear holder of the first planetary gear to a second sun gear of the second planetary gear, a first sun gear of the first planetary gear to the first major shaft and a second planetary gear holder of the second planetary gear to the second major shaft, a transmission is obtained which shifts without torque interruption.
    The gearbox is preferably provided with a number of pairs of gears, which include with a side shaft mechanically weldable and disengageable gears. This provides a number of fixed gear steps, which can be shifted without interruption of torque. The gears that can be loaded on the side axle also mean that a compact design with high reliability and high reliability is obtained. Alternatively, gears which are present in the gear pair can be arranged and disengaged on the first or second main shaft.
    The gear pairs each have a gear ratio, which is adapted to the vehicle's desired driving characteristics. The gear pair with the highest gear ratio, in relation to the other gear pairs, is suitably engaged when the lowest gear is engaged. With the gearbox according to the invention, conventional slip couplings between the internal combustion engine and the gearbox can be avoided.
    A welding mechanism is provided for firmly connecting the output shaft of the internal combustion engine to the housing of the gearbox. Thus, the first planetary gear housing will also be welded to the gearbox housing. By welding the output shaft of the internal combustion engine by means of the welding mechanism and the first planetary gear holder with the housing of the gearbox, the gearbox becomes and thus the vehicle is adapted for electric operation of the electric machines. The electric machines thus emit a torque to the output shaft of the gearbox.
    A first and second coupling unit are arranged between planetary gear carriers and sun gear at each planetary gear. The purpose of the coupling units is to load the respective planet wheel holders with the sun gear. When the planetary gear carrier and the sun gear are connected to each other, the power from the internal combustion engine will pass through the planetary gear carrier, the clutch unit, the sun gear and on to the gearbox, which means that the planetary gear does not absorb torque.
    This means that the dimension of the planet gears can only be adapted to the torque of the electric machine instead of the torque of the internal combustion engine, which in turn means that the planet gears can be made with smaller dimensions. Thus, a drive device according to the invention is obtained which has a compact construction, low weight and low manufacturing cost.
    The coupling units and the welding mechanisms preferably comprise an annular sleeve which is displaced axially between a coupled and uncoupled bearing. The sleeve essentially concentrically encloses the rotating components of the gearbox and is moved between the connected and disconnected layers by means of a force element. This results in a compact design with low weight and low manufacturing cost.
    BRIEF DESCRIPTION OF THE DRAWINGS In the following, as an example, preferred embodiments of the invention are described with reference to the accompanying drawings, in which: Fig. 1 schematically shows a vehicle in a side view with an internal combustion engine and a hybrid driveline controlled according to the present invention, 9 Fig. 2 shows a schematic side view of a hybrid driveline controlled according to the present invention, Fig. 3 shows a simplified schematic view of the hybrid driveline in Fig. 2, and Fig. 4 shows a flow chart of the method for guiding a hybrid driveline according to the present invention.
    DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION Fig. 1 schematically shows a side view of a vehicle 1, which comprises a gearbox.da 2 and an internal combustion engine 4, which engages in a hybrid driveline 3. The internal combustion engine 4 is connected to the gearbox 2 and the gearbox 2. is further coupled to the drive wheel 6 of the vehicle 1 via a propeller shaft 9.
    The drive wheels 6 are provided with braking devices 7 for braking the vehicle 1.
    Fig. 2 shows a schematic side view of a hybrid driveline 3 with a gearbox 2, which comprises an input shaft 8, a first and a second planetary shaft 10, respectively. 12, a first and second electric machine 14 resp. 16, a side shaft 18 and an output shaft 20. The first planetary shaft 10 has a first ring gear 22 to which a first rotor 24 of the first electric machine 14 is connected. The first planetary gear 10 also has a first sun gear 26. The second planetary gear 12 has a second ring gear 28 to which a second rotor 30 of the second electric machine 16 is connected. The second planetary gear 12 has a second sun gear 32. The first and second sun wheels 26 resp. 32 are arranged coaxially, which according to the embodiment shown means that a first main shaft 34 arranged on the first sun gear 26 extends inside a second main shaft 36 arranged on the second sun wheel 32, which is provided with a central bore 38. It is also possible to arrange the first and second sun wheels 26 resp. 32 and also the first main shaft 34 and the second main shaft 36 parallel to and adjacent to each other.
    The first electric machine 14 is provided with a first stator 40, which is connected to the vehicle 1, via a gear housing 42 surrounding the gearbox 2. The second electric machine 16 is provided with a second stator 44, which is connected to the vehicle 1, via the gear housing 42 surrounding the gearbox 2. The first and second electrical machines 16 are connected to an energy storage 46, such as a battery, which, depending on the operating condition of the vehicle 1, drives the electrical machines 14 and 14, respectively. 16. In other operating conditions, the electrical machines 14 resp. 16 operate as generators, whereby power is supplied to the energy storage 46. An electronic control unit 48 is connected to the energy storage 46 and controls the power supply to the electrical machines 14 resp. 16.
    Preferably, the energy storage 46 is connected to the electrical machines 14 and 14, respectively. 16 via a switch 49, which is connected to the control unit 48. In certain operating cases, the electrical machines 14 resp. 16 also drive each other. Electrical energy is then led from one electrical machine 14, 16 to the other electrical machine 14, 16 via the switch 49 connected to the electrical machines 14, 16. This makes it possible to achieve a power balance between the electrical machines 14, 16. Another computer 53 may also be connected to the control unit 48 and the gearbox 2.
    The first planetary gear 10 is provided with a first planet gear holder 50, on which a first set of planet gears 52 are mounted. The second planetary gear 12 is provided with a second planet gear holder 51, on which a second set of planet gears 54 are mounted. The first set of planet gears 52 cooperates with the first ring gear 22 and the first sun gear 26. The second set of planet gears 54 cooperates with the second ring gear 28 and the second sun gear 32. The input shaft 8 of the gearbox 2 is connected to the first planet gear holder 50.
    A first coupling unit 56 is arranged between the first sun gear 26 and the first planet gear holder 50. By employing the first coupling unit 56, said that the first sun gear 22 and the first planet wheel holder 50 are connected to each other and thus can not rotate in relation to each other. the first planet gear carrier 50 and the first sun gear 26 to rotate at equal speeds.
    A second coupling unit 58 is arranged between the second sun gear 32 and the second planet gear holder 51. By employing the second coupling unit 58, said that the second sun wheel 32 and the second planet wheel holder 51 are connected to each other and thus can not rotate in relation to each other, the second planet gear holder 51 and the second sun gear 32 will rotate at equal speeds.
    Preferably, the first and second coupling units 56, 58 comprise a first and second splined coupling sleeve 55 and 55, respectively. 57, which is axially displaceable on one with the first 11 resp. second planetary gear carrier 50 resp. 51 splines-intended part and on one with resp. sun wheel 26 resp. 32 splines intention party. By shifting resp. coupling sleeve 55, 57, so that the splined portions are connected via resp. coupling sleeve 55, 57 becomes the first planet gear holder 50 and the first sun gear 26 resp. the second planet gear holder 51 and the second sun gear 32 were embedded in load with each other and cannot rotate in relation to each other.
    The first and second clutch units 56, 58 according to the embodiment shown in Fig. 2 are arranged between the first sun gear 26 and the first planet gear holder 50 and 50, respectively. between the second sun gear 28 and the second planetary gear carrier 51. However, it is possible to arrange an additional or alternative coupling unit (not shown) between the first ring gear 22 and the first planetary gear carrier 50, and also to arrange an additional or alternative coupling unit (not shown). ) between the second ring gear 28 and the second planet gear holder 51.
    Coupled to the first and second main shafts 34,36 is a transmission device 19 which includes a first gear pair 60 disposed between the first planetary gear shaft 10 and the output shaft 20. The first gear shaft pair 60 includes a first gear drive 62 and a first gear 64 , which are engaged with each other. A second pair of gears 66 is disposed between the second planetary gear 12 and the output shaft 20. The second pair of gears 66 includes a second gear gear 68 and a second gear 70, which are engaged with each other. A third gear pair 72 is disposed between the first planetary gear shaft 10 and the output shaft 20. The third gear pair 72 includes a third gear drive 74 and a third gear 76, which are engaged with each other. A fourth pair of gears 78 is disposed between the second planetary gear 12 and the output shaft 20. The fourth pair of gears 78 comprises a fourth gear 80 and a fourth gear 82, which are engaged with each other.
    On the first main shaft 34, the first and third gears 62 and 5, respectively. 74 arranged. The first and third gear gears 62, respectively. 74 are fixedly connected to the first main shaft 34 so that they cannot rotate in relation to the first main shaft 34. On the second main shaft 36, the second and fourth gear gears 68, respectively. 80 arranged. The second and fourth gear gears 68, respectively. 80 are fixedly connected to the second main shaft 36, so that they cannot rotate in relation to the second main shaft 36.
    The side shaft 18 extends substantially parallel to the first and second main shafts 34 and 34, respectively. 36. On the side shaft 18, the first, second, third and fourth gears 64, 70, 76 and 76, respectively. 82 stored 12 arranged. The first gear 62 engages the first gear 64, the second gear 68 engages the second gear 70, the third gear 74 engages the third gear 76 and the fourth gear 80 engages the fourth gear.
    The first, second, third and fourth gears 64, 70, 76 resp. 82 can be individually locked and disengaged on the side shaft 18 by means of first, second, third and fourth coupling elements 84, 86, 88 and 88, respectively. 90. Coupling elements 84, 86, 88 resp. 90 is preferably formed on the gears 64, 70, 76 resp. 82 and the side shaft 18 are formed with splined portions which cooperate with fifth and sixth coupling sleeves 83, 85 which mechanically engage with the splined portions of respective first to fourth gears 64, 70, 76 and 76, respectively. 82 and the side shaft 18. The first and third coupling elements 84, 88 are preferably provided with a common coupling sleeve 83 and the second and fourth coupling elements 86, 90 are preferably provided with a common coupling sleeve 85. In the disengaged joint a relative rotation may occur. and gears 64, 70, 76 resp. 82 and the side shaft 18. The coupling elements 84, 86, 88 resp. 90 can also consist of friction couplings. a fifth gear 92 is also arranged on the side shaft 18, which engages with a sixth gear 94, which is arranged on the output shaft 20 of the gearbox 2.
    The side shaft 18 is arranged between the respective first and second planetary shafts 10, 12 and the output shaft 20, so that the side shaft 18 is connected to the output shaft 20 via a fifth gear pair 21, which comprises the fifth and sixth gears 92, 94. The fifth the gear 92 can be coupled and disengaged on the side shaft 18 by means of a fifth coupling element 93.
    By disengaging the fifth gear 92 disengageable with the side shaft 18, it becomes possible to transmit torque from the second planetary shaft 12 to the side shaft 18 via, for example, the second gear pair 66 and to further transmit torque from the side shaft 18 to the output shaft 20 via the output shaft 20, for example. the gear pair 60. Thereby a number of gear stages are obtained, where torque from one planetary gear shaft 10, 12 can be transmitted to the side shaft 18 and further from the side shaft 18 to the main shaft 34, 36 connected to the other planetary shaft 10, 12 to finally transmit torque to the output shaft 20 of the gear shaft 2, however, this presupposes that a coupling mechanism 96 dr arranged between the first main shaft 34 and the output shaft 20 is connected, which will be described in more detail below. The fifth gear 92 can be locked and disengaged on the side shaft 18 by means of a fifth coupling element 93. The coupling element 93 is preferably constituted by spline-provided portions formed on the fifth gear 92 and the side shaft 18, which cooperate with a ninth coupling sleeve 87, with which they engage the splined portions of the fifth gear 92 and the side shaft 18. In the disengaged layer, a relative rotation may occur between the fifth gear 92 and the side shaft 18. The fifth coupling element 93 may also be formed by friction couplings.
    Torque transmission from the shaft 8 of the gear shaft 2 to the shaft 20 of the shaft shaft 2 can take place via the first or the second planetary shaft 10 resp. 12 and the side shaft 18. The torque transmission can also take place directly via the first planetary shaft 10, whose first sun gear 26 via the first main shaft 34 is connected to the output shaft 20 of the gearbox 2 via a coupling mechanism 96. The coupling mechanism 96 preferably comprises a splined seventh coupling sleeve 100, is axially displaceable on the first major shaft 34 and the output shaft splined portions. By displacing the seventh coupling sleeve 100, so that the splined portions are connected via the seventh coupling sleeve 100, the first main shaft 34 is fixed with the output shaft 20, which upon rotation will thus have the same speed. By disengaging the fifth gear 92 of the fifth gear pair 21 from the side shaft 18, torque from the second planetary shaft 12 can be transmitted to the side shaft 18 and further from the side shaft 18 to the first main shaft 34 connected to the first planetary shaft 10 to finally transmit torque to the gear shaft via the clutch mechanism 96 2 output shaft 20.
    During operation, the gearbox 2 can in certain operating cases work so that one of the sun wheels 26 resp. 32 is read against the first resp. second planetary gear carrier 50 resp. 51 with the help of the first resp. second coupling unit 56 resp. 58. The first resp. second main shaft 34 resp. 36 then receives the same speed as the input shaft 8 of the gearbox 2, depending on which sun gear 26 resp. 32, which is fixed with resp. planetary gear rack 50 resp. 51. One or both of the electric machines 14 resp. 16 can operate as a generator to generate electrical energy for the energy storage 46. Alternatively, the electrical machine 14 resp. 16 provide a torque supplement in order to increase the torque of the output shaft 20. During certain operating conditions, the electrical machines 14 resp. 16 to supply each other with electrical energy, independent of the energy storage 46.
    It is also possible to bathe the first and second electric machine 14 resp. 16 simultaneously generates power to the energy storage 46. During engine braking, the driver relaxes the vehicle's accelerator pedal 14 (not shown). The output shaft 20 of the gearbox 2 then drives one or both of the electric machines 14 resp. 16 at the same time as the internal combustion engine 4 and the electric machines 14 resp. 16 engine brakes. The electric machines 14 resp. 16 generates has electrical energy stored in the energy storage 46 in the vehicle 1. This operating condition is called regenerative braking. In order to enable more powerful braking action, the output shaft 97 of the internal combustion engine 4 can be locked and thus prevented from rotating. Thus, only one or the two electric machines 14 resp. 16 to act as a brake and 16 generate electrical energy, which is stored in the energy storage 46. The welding of the output shaft 97 of the internal combustion engine 4 can also be performed when the vehicle is to be accelerated by only one or both electric machines 14 resp. 16.
    If one or the other of the two electric machines 14 resp. 16 torques overcome the torques of the internal combustion engine 4 and with regard to the gear ratio between them, the internal combustion engine 4 will not be able to withstand the large torque that the electric machines 14 resp. 16, so that a welding of the output shaft 97 of the internal combustion engine 4 becomes necessary. The welding of the output shaft 97 of the internal combustion engine 4 is preferably performed with a welding device 102, which is arranged between the first planetary gear holder 50 and the gear housing 42. By welding the first planetary gear carrier 50 and the gear housing 42, the output shaft 97 of the internal combustion engine 4 97 is connected to the first planet gear carrier 50 via the input shaft 8 of the gearbox. The locking device 102 preferably comprises a splined eighth coupling sleeve 104, which is axially displaceable on a portion provided with the first planet gear carrier 50 and on a portion provided with the gear housing splines. By displacing the eighth clutch sleeve 104 so that the splined portions are connected via the clutch sleeve 104, the first planet gear carrier 50 and the output shaft 97 of the armed internal combustion engine 4 are prevented from rotating.
    The control unit 48 is connected to the electrical machines 14 resp. 16 and is adapted to control the electrical machines 14 resp. 16 said that in certain applicable operating conditions they use stored electrical energy to supply driving force to the output shaft 20 of the gearbox 2 and in other operating cases they use the kinetic energy of the output shaft 20 of the output shaft 2 to extract and store electrical energy. The control unit 48 thus senses the speed and / or torque of the output shaft 97 of the internal combustion engine 4 via sensors 98 arranged at the electrical machines 14 and 14, respectively. 16 and the shaft 20 emanating from the gearbox 2 to thereby obtain information and control the electrical machines 14 resp. 16 to work as electric motors or generators. The controller 48 may be a computer with appropriate software for this purpose. The control unit 48 also controls the flow of electrical energy between the energy storage 46 and resp. stator 40 resp. 44 of the electrical machines 14 resp. 16. In the event that the electrical machines 14 resp. 16 works as a motor supplied with stored electrical energy from the energy storage 46 to resp. stator 40 resp. 44. In cases where the electrical machines 14 resp. 16 works as a generator supplied with electrical energy frail resp. stator 40 resp. 44 to the energy storage 46. However, as mentioned above, the electric machines 14 resp. 16 in certain operating cases supply each other with electrical energy, independent of the energy storage 46.
    The first and the second coupling unit 56 resp. 58, the first, second, third, fourth and fifth coupling elements 84, 86, 88, 90, respectively. 93, the coupling mechanism 96 between the first main shaft 34 and the output shaft 20, and the locking device 102 between the first planetary gear holder 50 and the gear housing 42 are connected via their respective coupling sleeves to the control unit 48. These components are preferably activated and deactivated by electrical signals from the control unit 48. displacement is preferably by force means (not shown), such as hydraulically or pneumatically driven cylinders. It is also possible to displace the coupling sleeves with electrically driven power members.
    According to the exemplary embodiment in Fig. 2, four gear gears 62, 68, 74 and 80 and four gears 64, 70, 76 respectively. 82 and two planetary gears 10 resp. 12 with associated electrical machines 14 resp. 16. However, it is possible to design the gearbox 2 with more or fewer gear gears and gears and with more planetary gears with associated electrical machines.
    As described, torque is taken from the gearbox 2 from the output shaft 20. It is also possible to take torque directly from the first or second main shaft 34, 36 or directly from the side shaft 18. Torque can also be taken in parallel from two or all three shafts 18, 34 , 36 simultaneously.
    In the following, an upshift from a first to a seventh gear will be described when the gearbox 2 is arranged in a vehicle 1 and propulsion of the vehicle takes place by means of the internal combustion engine 4.
    The input shaft 8 of the gearbox 2 is connected to the output shaft 97 of the internal combustion engine 4 of the vehicle 1. The output shaft 20 of the gearbox 2 is connected to a drive shaft 99 of the vehicle 1. When the internal combustion engine 4 is idling and the vehicle 1 is stationary, the input shaft 8 rotates at the same time as the output shaft 20 of the alternating shaft 2 is stationary. The welding device 102 is deactivated so that the output shaft 97 of the internal combustion engine 4 can rotate freely. As the input shaft 8 of the gearbox 2 rotates, the first planet gear holder 50 will also rotate, which means that the first set of planet wheels 52 will rotate. Since the first planet wheel holder 50 is connected to the second sun wheel 32, the second sun wheel 32 and thus also the second set of planet wheels 54 will rotate. By not supplying power to the first and second electrical machines 14 resp. 16, the first and second ring wheels 22 and 28, which are connected with resp. first and second rotor 24 resp. 30 at resp. electric machine 14 resp. 16 to rotate freely, whereby no torque is absorbed by the ring wheels 22 resp. 28. The first and the second coupling unit 56 resp. 58 are disconnected and thus not employed. Thus, no torque will be transmitted from the internal combustion engine 4 to the sun gear 26 of the first planetary gear 10, nor to the planetary gear holder 51 of the second planetary gear 12. The coupling mechanism 96 between the first major shaft 34 and the output shaft 20 is disengaged, so that the first major shaft 34 and the the output shaft 20 can rotate freely in relation to each other. Since the sun gear 26 of the first planetary gear, the planetary gear holder 51 of the second planetary gear 12 and the output shaft 20 of the gearbox 2 are stationary at this stage, the side shaft 18 is also stationary. In a first step, the fourth gear 82 and the third gear 76 are coupled to the side shaft 18 by means of the fourth and third coupling elements 88 and 88, respectively. 90. The first gear 64 and the second gear 70 are disengaged from the side shaft 18. This allows the first gear 64 and the second gear 70 to rotate freely in relation to and the side shaft 18. The fifth gear 92 of the fifth gear pair 21 is fixed the side shaft 18 by means of the fifth coupling element 93.
    In order to initiate the rotation of the output shaft 20 output shaft 2 for the purpose of driving the vehicle 1, the fourth gear gear 80 and the fourth gear 82 on the side shaft 18 shall be caused to rotate.
    This is accomplished by rotating the second planet gear holder 51. When the second planet gear holder 51 rotates, the second main shaft 36 will also rotate and thus the fourth gear gear 80, which is arranged on the second main shaft 36, is also rotated. The second planet gear holder 51 is caused to rotate by the second ring wheel 28 being controlled by the second electric the machine 16. By activating the second electric machine 16 and controlling the internal combustion engine 4 to the optimum speed, the vehicle 1 begins to move by the second main shaft 36 starting to rotate. When the second planet gear holder 51 and the second sun gear 32 reach the same speed, the second sun gear 32 is fixed to the second planet wheel holder 51 by means of the second clutch unit 58. As mentioned above, the second clutch unit 58 is preferably designed so that the second sun wheel 32 and the the second planet gear holder 51 mechanically engages with each other. Alternatively, the second clutch unit 58 may be formed as a slip brake or a disc clutch which softly connects the second sun gear 32 to the second planet wheel holder 51. When the second sun wheel 32 is connected to the second planet wheel holder 51, the second planet wheel holder 51 will rotate at the same speed as the output shaft 9 of the internal combustion engine 4. Thereby the torque generated by the internal combustion engine 4 is transmitted to the gear shaft. The output shaft 20 of the output gear 2 via the fourth gear 80, the fourth gear 82 on the side shaft 18, the fifth gear 18 and the side gear 92 on the side sixth gear 94 on gear shaft 2 output shaft 20.
    The vehicle 1 will thus start to be moved and propelled by a first gear.
    The first, second, third and fourth gear pairs 60, 66, 72, 78 each have a gear ratio which is adapted to the desired driving characteristics of the vehicle 1. According to the embodiment shown in Fig. 2, the fourth gear pair 78 has the highest gear ratio compared to the first, second and third gear pairs 60, 66, 72, which means that the fourth gear pair 78 is engaged when the lowest gear is engaged. The second gear pair 66 opposite, like the fourth gear pair 78, torque between the second main shaft 36 and the side shaft 18, and could instead be made with the highest gear ratio in comparison with other gear pairs 60, 72, 78, whereby in such an embodiment the second gear pair 66 would be engaged when the lowest gear is engaged.
    When the side shaft 18 is caused to rotate by the fourth gear 82 on the side shaft 18, the third gear 76 on the side shaft 18 will also rotate. Thereby, the side shaft 18 drives the third gear 76, which in turn drives the third gear 74 on the first main shaft 34. When the first main shaft 34 rotates, the first sun gear 26 will also rotate, as a result, depending on the speed of the internal combustion engine 4 output shaft 97 and thus the speed of the first planet gear holder 50, will cause the first ring gear 22 and the first rotor 24 of the first electric machine 14 to rotate. In this case, it is possible to allow the first electrical machine 14 to operate as a generator in order to supply power to the energy storage 46 and / or to supply power to the second electrical machine 16. It is also possible for the second electrical machine 16 to be operated as a generator. Alternatively, the first electrical machine 14 may deliver a torque supplement by the control unit 48 controlling the first electric machine 14 to provide propulsive torque. To shift from a first gear to a second gear, the loading between the second sun gear 32 and the second planet gear holder 51 must cease, which is accomplished by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved in the second planetary gear 12. Then, the second clutch assembly 58 is controlled so as to release the second sun gear 32 and the second planet gear holder 51 apart. The second gear is engaged by the control unit 48 controlling the internal combustion engine 4, so that a synchronous speed occurs between the first planet gear carrier 50 and the first sun gear 26, in order to effect a loading between the first planet wheel carrier 50 and the first sun gear 26. This This is accomplished by controlling the first clutch assembly 56 so that the first planet gear holder 50 and the first sun gear 26 are mechanically connected to each other. Alternatively, the first clutch unit 56 may be formed as a slip brake or a disc clutch which softly connects the first sun gear 26 to the first planet gear carrier 50. By synchronizing the control of the internal combustion engine 4 and the second and first electric machines 14 and 14, respectively. 16, a smooth and uninterrupted transition from a first to a second gear can be performed.
    The first main shaft 34 now rotates and is driven by the output shaft 97 of the internal combustion engine 4 and the first main shaft 34 now drives the third gear gear 74. The first planet gear carrier 50 thus drives the third gear gear 74 via the first sun gear 26 and the first main shaft 34. Since the third the gear 76 engages the third gear gear 74 and is engaged with the side shaft 18, the third gear 76 will drive the side shaft 18, which in turn drives the fifth gear 92 on the side shaft 18. The fifth gear 92 in turn drives the output shaft 2 axle 20 via the sixth gear 94, which is arranged on the output shaft 20 of the gearbox 2, the vehicle 1 is now propelled by a second gear.
    When the side shaft 18 is caused to rotate by the third gear 76, the fourth gear 82 will also rotate. Thus, the side shaft 18 drives the fourth gear 82, which in turn drives the fourth gear 80 on the second main shaft 36. As the second main shaft 36 rotates, the second planet gear holder 51 will also rotate, as a result, depending on the speed of the internal combustion engine 4. output shaft 97 and then the speed of the first planetary gear carrier 50, will cause the second ring gear 28 and the second rotor 30 of the second electric machine 16 to rotate. In this case, it is possible to allow the second electrical machine 16 to operate as a generator in order to supply electricity to the energy storage 46 and / or to supply the first electrical machine 14 with electricity. The second electric machine 16 19 can also deliver a torque supplement by the control unit 48 controlling the second electric machine 16 to provide propulsive torque.
    To shift from a second gear to a third gear, the fourth gear 82 on the side shaft 18 must be disengaged from the side shaft 18 with the fourth coupling element 90, so that the fourth gear 82 can rotate freely in relation to the side shaft 18. Then the side shaft 18 is coupled with the second gear 70 on the side shaft 18 through the second coupling element 86. In order to effect a coupling of the side shaft 18 and the second gear 70 on the side shaft 18, the second electric machine 16 is preferably controlled so that a synchronous speed occurs between the side shaft 18 and the the second gear 70 on the side shaft 18. A synchronous speed can be determined by measuring the speed of the second rotor 30 of the second electric machine 16 and measuring the speed of the output shaft 20. Thus, the speed of the second main shaft 36 and the speed of the side shaft 18 can be determined by given gear ratios. The speed of the respective shafts 18, 36 is controlled and when a synchronous speed has arisen between the side shaft 18 and the second gear 70, the side shaft 18 and the second gear 70 are connected by means of the second coupling element 86.
    To carry out the shift from a second gear to a third gear, the loading between the first sun gear 26 and the first planet gear holder 50 must cease, which is achieved by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved. in the first planetary gear 10, after which the first clutch unit 56 is controlled so as to release the first sun gear 26 and the first planet gear holder 50 from each other. Thereafter, the internal combustion engine 4 is controlled so that a synchronous speed occurs between the second sun gear 32 and the second planet gear holder 51, so that the second coupling unit 58 can be engaged so as to thereby connect the coupling sleeve 57 to the second sun wheel 32 with the second planter wheel holder 51. synchronize the control of the internal combustion engine 4 and the second and first electric machine 14 resp. 16, a smooth and uninterrupted transition from a second to a third gear can be performed.
    The third gear 76 is released by controlling the first electric machine 14 so that a torqueless state arises between the side shaft 18 and the third gear 76. When a torqueless state arises, the third gear 76 is released from the side shaft 18 by controlling the third clutch member 88. so that it releases the third gear 76 from the side shaft 18. Thereafter, the first electric machine 14 is controlled so that a synchronous speed occurs between the side shaft 18 and the first gear 64. When a synchronous speed occurs, the first gear 64 on the side shaft 18 is connected through that the first coupling element 84 is controlled so that it engages the first gear 64 on the side shaft 18. A synchronous speed can be determined by measuring the speed of the first rotor 24 of the first electric machine 14 and measuring the speed of the output shaft 20, after which the speeds of the shafts 18, 34 are controlled so that a synchronous speed arises. Thus, the speed of the first main shaft 34 and the speed of the side shaft 18 can be determined by given gear ratios.
    The second main shaft 36 now rotates at the same speed as the output shaft 97 of the internal combustion engine 4 and the second main shaft 36 now drives the second gear gear 68 via the second main shaft 36. Since the second gear 70 is engaged with the second gear gear 68 and is engaged with the side shaft 18, the second gear 70 will drive the side shaft 18, which in turn drives the fifth gear 92 on the side shaft 18. The fifth gear 92 in turn drives the output shaft 20 of the gearbox 2 via the sixth gear 94, which is arranged on the output shaft 20 of the gearbox 2. The vehicle 1 is now propelled by a third gear.
    When the side shaft 18 is caused to rotate by the second gear 70 on the side shaft 18, the first gear 64 on the side shaft 18 will also rotate. Thus, the side shaft 18 drives the first gear 64, which in turn drives the first gear 62 on the first main shaft 34. As the first main shaft 34 rotates, the first sun gear 26 will also rotate, thus depending on the speed of the output shaft of the internal combustion engine 4. 97 and thus the speed of the first planetary gear carrier 50, will cause the first ring gear 22 and the first rotor 24 of the second electric machine 16 to rotate. In this case, it is possible to make the first electrical machine 14 operate as a generator to supply electricity to the energy storage 46 and / or to supply the second electrical machine 16 with electricity. Alternatively, the first electrical machine 14 may deliver a torque supplement by the controller 48 controlling the first electrical machine 14 to provide propulsive torque.
    To perform the shift from a third gear to a fourth gear, the loading between the second sun gear 32 and the second planet gear holder 51 must cease, which is accomplished by controlling the first and / or the second electric machine 14, 16 so that torque balance is achieved in the second the planetary gear 12, after which the second clutch unit 58 is controlled, so that it releases the second sun gear 32 and the second planet wheel holder 51 from each other. A fourth gear is then engaged by the control unit 48 controlling the internal combustion engine 4 so that a synchronous speed occurs between the first planet gear carrier 50 and the first sun gear 26, to provide a load between the first planet wheel carrier 50 and the first sun gear 26. This is accomplished by that the first clutch unit 56 is controlled, so that the first planet gear holder 50 and the first sun gear 26 are mechanically connected to each other.
    By synchronizing the control of the internal combustion engine 4 and the second and first electric machine 14 resp. 16, a smooth and uninterrupted transition from a third to a fourth gear can be made. The first main shaft 34 now rotates and is driven by the output shaft 97 of the internal combustion engine 4 and the first main shaft 34 now drives the first gear drive 62. The first planetary gear carrier 50 thus drives the first gear 62 via the first gear 26 and the first main shaft 34. Since the first gear 64 engages the first gear 62 and is engaged with the side shaft 18, the first gear 64 will drive the side shaft 18, which in turn drives the fifth gear. 92 on the side axle 18. The fifth gear 92 in turn drives the output shaft 20 of the gearbox 2 via the sixth gear 94, which is arranged on the output shaft 20 of the gearbox 2. The vehicle 1 is now propelled by a fourth gear.
    When the side shaft 18 is caused to rotate by the first gear 64, the second gear 70 will also rotate. Thereby, the side shaft 18 drives the second gear 70, which in turn drives the second gear gear 68 on the second main shaft 36. When the second main shaft 36 rotates, the second planet gear holder 51 will also rotate, as a result, depending on the speed of the internal combustion engine 4 output shaft 97 and thus the speed of the first planet gear holder 50, will cause the second ring gear 28 and the second rotor 30 of the second electric machine 16 to rotate. In this case, it is possible to make the second electrical machine 16 operate as a generator to supply electricity to the energy storage 46 and / or to supply the first electrical machine 14 with electricity. The second electric machine 16 can also deliver a torque supplement by the control unit 48 controlling the second electric machine 16 to provide propulsive torque.
    To shift from a fourth gear to a fifth gear, the first gear 64 must be disengaged from the side shaft 18 so that the fourth gear is disengaged. This is accomplished by controlling the internal combustion engine 4 and the first electric machine 14 so that the first gear 64 is brought into a torqueless state relative to the side shaft 18. When a torqueless state has arisen, the first coupling element 84 is disengaged, so that it the first gear 64 disengages the side shaft 18.
    Thereafter, the speed of the first major shaft 34 is synchronized with the speed of the output shaft 20, after which the clutch mechanism 96 is controlled to interconnect the first major shaft 34 with the output shaft 20.
    Thereafter, the internal combustion engine 4 and the first electric machine 14 are controlled, so that the propulsion torque takes place via the first main shaft 34 and through the coupling mechanism 96 and further to the output shaft 20. By reducing the torque from the second electric machine 16, the fifth coupling element 93 can be brought into a torque-free condition in relation to the side shaft 18. When a torque-free condition has arisen, the fifth clutch element 93 is forced out of engagement, so that the fifth gear 92 of the fifth gear pair 21 is disengaged from the side shaft 18.
    Then, with the aid of the second electric machine 16, the speed of the side shaft 18 is synchronized with the speed of the third gear 76, after which the third clutch element 88 is controlled so that it connects the third gear 76 to the side shaft 18. When this coupling is performed, the propulsion torque can be performed. is divided between the internal combustion engine 4, the fixed electric machine 14 and the second electric machine 16. Then a torque balance is created in the first planetary gear 10, after which the first clutch unit 56 disengages the first planetary gear carrier 50 and the first sun gear 26 from each other. Finally, the second planet gear holder 51 is synchronized with the second sun gear 32, after which the second clutch unit 58 interconnects the second planet wheel holder 51 and the second sun wheel 32 with each other.
    The second main shaft 36 now rotates and is driven by the output shaft 97 of the internal combustion engine 4 and the second main shaft 36 drives the second gear 68. Since the second gear 70 engages the second gear gear 68 and is coupled to the side shaft 18 by the second clutch member 86, the second gear 70 will drive the side shaft 18, which in turn drives the third gear 76 on the side shaft 18. The third gear 76 in turn drives the first main shaft 34 via the third gear gear 74 and the output shaft 20 output shaft 20 is thus driven via the clutch mechanism 96 which interconnects the first main shaft 34 and the output shaft 20 of the gearbox 2. The vehicle 1 is now propelled by a fifth gear. To shift from a fifth to a sixth gear, the loading between the second sun gear 32 and the second planet gear holder 51 must cease, which is accomplished by controlling the first and / or the second electric machine 14, 16 so that torque balance is achieved in the second planetary gear. 12, after which the second clutch unit 58 is controlled so as to release the second sun gear 32 and the second planet gear holder 51 from each other. A sixth gear is then engaged by the control unit 48 controlling the internal combustion engine 4 so that a synchronous speed occurs between the first planet gear carrier 50 and the first sun gear 26, to provide a load between the first planet gear carrier 50 and the first sun gear 26. This is accomplished by the first clutch unit 56 is controlled so that the first planet gear holder 50 and the first sun gear 26 are mechanically connected to each other. By synchronizing the control of the internal combustion engine 4 and the second and first electric machine 14 resp. 16, a smooth and uninterrupted transition from a fifth to a sixth gear can be performed.
    The first main shaft 34 now rotates and is driven by the output shaft 97 of the internal combustion engine 4, the first main shaft 34 driving the output shaft 20 of the gearbox 2 via the clutch mechanism 96 connecting the first main shaft 34 and the output shaft 20 of the gearbox 2. The vehicle 1 is now propelled by a sixth gear.
    To shift from a sixth to a seventh gear, first the third gear 76 on the side shaft 18 must first be disengaged from the side shaft 18 with the third coupling element 88, so that the third gear 76 can rotate freely in relation to the side shaft 18. Then the side shaft 18 is coupled with the first gear 64 on the side shaft 18 through the first clutch member 84. Since the side shaft 18 and the first gear 64 on the side shaft 18 have a synchronous speed, the first gear member 84 is controlled so that the first gear 64 and the side shaft 18 are engaged.
    To perform the shift from a sixth gear to a seventh gear, the loading between the first sun gear 26 and the first planet gear holder 50 must cease, which is accomplished by controlling the first and / or the second electric machine 14, 16 so that torque balance is achieved in the first planetary gear 10, after which the first clutch unit 56 is controlled so as to release the first sun gear 26 and the first planet gear holder 50 apart. Thereafter, the internal combustion engine 4 is controlled so that a synchronous speed occurs between the second sun gear 32 and the second planet gear holder 51, so that the second coupling unit 58 can be engaged so as to thereby connect the coupling sleeve 57 to the second sun wheel 32 with the second planter wheel holder 51. to synchronize the control of the internal combustion engine 4 and the second and first electric machine 14 resp. 16, a smooth and uninterrupted transition from a sixth to a seventh gear can be performed.
    The second main shaft 36 now rotates at the same speed as the output shaft 97 of the internal combustion engine 4 and the second main shaft 36 drives the second gear gear 68. Since the second gear 70 engages the second gear gear 68 and is engaged with the side shaft 18, the second gear 70 driving the side shaft 18, which in turn drives the first gear 64 on the side shaft 18. The first gear 64 in turn drives the first main shaft 34 via the first gear gear 62 and the output shaft 20 output shaft 20 is thus driven via the clutch mechanism 96 which engages the first main shaft 34 and the output shaft 20 of the gearbox dance 2. The vehicle 1 is now propelled by a seventh gear.
    According to the embodiment above, it is stated that the gearbox 2 comprises on main shafts 34, 36 resp. side axle 18 arranged gear gears 62, 68, 74, 80 and gears 64, 70, 76, 82 to transmit speed and torque. However, it is possible to use another type of transmission, such as chain and belt transmissions to transmit speeds and torques in the gearbox 2.
    According to the exemplary embodiment above, the transmission device 19 has four gear pairs 60, 66, 72, 78. However, the transmission device 19 may comprise any number of gear pairs.
    According to Fig. 3, the hybrid driveline 3 according to Fig. 2 is illustrated in a simplified view where certain components have been excluded for the sake of clarity. G1 in Fig. 3 consists of at least one gear pair connected to the first main shaft 34 and thus the first planetary shaft 10 and G2 consists of at least one gear pair connected to the second main shaft 36 and thus the second planetary shaft 12. These gear pairs G1, G2 are also connected to the output shaft 20 via the side shaft 18. G1 and G2, respectively, may be one or more gear pairs. The gear pair G1 connected to the first planetary gear 10 may, for example, be the first gear pair 60 and / or the third gear pair 72, as described in Fig. 2. The gear pair G2 connected to the second planetary gear 12 may be, for example, the second gear pair 66 and / or the fourth gear pair 78, as described in Fig. 2. Furthermore, at least one gear pair G3 connected to the output shaft 20 and the side shaft 18 is shown, which may be the fifth gear pair 21, which is described in Fig. 2. G3 may be of one or more gear pairs.
    Fig. 4 shows a flow chart of a method for controlling a hybrid driveline 3 comprising a gear shaft 2 with an input shaft 8 and an output shaft 20, a first planetary shaft 10, which is coupled to the input shaft 8, a second planetary shaft 12, which is coupled to the first planetary gear 10, a first electric machine 14, which is coupled to the first planetary gear 10, a second electric machine 16, which is coupled to the second planetary gear 12, a first gear pair 60 and a third gear pair 72, arranged between the first planetary shaft 10 and the output shaft 20 and a second pair of gears 66 arranged between the second planetary shaft 12 and the output shaft 20, an internal combustion engine 4 being connected to the first planetary shaft 10 via the input shaft 8. The first gear pair 60 includes a first gear gear 62 engaged and a first gear 64, the first gear 62 being fixedly provided with the first planetary gear 10 and which a first gear 64 is coupled and disengaged on the side shaft 18. The third gear pair 72 includes a third gear gear 74 and a third gear 76 in engagement with each other, the third gear gear 74 being fixedly provided with the first planetary gear 10 and the third gear 76 The second gear pair 66 includes a second gear gear 68 and a second gear 70 in engagement with each other, the second gear gear 68 being fixedly disposed with the second planetary gear 12 and the second gear 70 being connected to each other. detachably arranged on the side shaft 18.
    The method includes step a) disengaging the first gear pair 60. To disengage the first gear pair 60, the internal combustion engine 4 and the first electric machine 14 are controlled so that a torqueless state is created between the first gear 64 of the first gear pair 60 and the side shaft 18. Then a first gear element 84 is displaced so that the first gear 64, and thus the first gear pair 60, is disengaged from the side shaft 18. The first gear 64 can then rotate freely in relation to the side shaft 18 and thus the first gear pair 60 is disengaged.
    The method further comprises the step b) of connecting the first planetary shaft 10 to the output shaft 20 by means of a coupling mechanism 96. In order to establish a connection between the first planetary shaft 10 and the output shaft 20, the internal combustion engine 4 is controlled so that a synchronous speed is provided between a first main shaft 34 and the output shaft 20 connected to the first planetary shaft 10, and then the coupling mechanism 96 is displaced so that it 26 connects the first main shaft 34 and the output shaft 20, thereby connecting the first planetary shaft 10 and the output shaft 20.
    The method then comprises the step c) of disengaging a fifth gear pair 21 connected to the output shaft 20 and the side shaft 18. To disengage the fifth pair of gears 21, the second electric machine 16 is controlled, so that a torqueless state is achieved between the fifth pair of gears 21 and the side shaft 18, after which a fifth coupling element 93 is displaced, so that the fifth gear pair 21 is disengaged from the side shaft 18. The fifth gear pair 21 comprises an engaging fifth and sixth gears 92, 94, which sixth gear 94 is fixedly arranged on the output shaft 20. and which fifth gear 92 is coupled and disengaged on the side shaft 18 by means of the fifth coupling element 93. Thus in step c) a torque-free condition is achieved between the fifth gear 92 and the side shaft 18, after which the fifth gear 92, and thus the fifth pair of gears 21 , disengages the side shaft 18.
    The method further comprises the step c1) of coupling the third gear pair 72 to the side shaft 18.
    The second electric machine 16 is controlled so that a synchronous speed is achieved between the side shaft 18 and the third gear pair 72, after which a third coupling element 88 is displaced so that it connects the third gear pair 72 to the side shaft 18. Preferably a synchronous speed is provided between the side shaft 18 and the third gear 76 of the third gear pair 72, after which the third clutch member 88 is displaced so that the third gear 76 is coupled to the side shaft 18.
    The method further comprises the step d) of transmitting a torque from the second planetary shaft 12 to the side shaft 18 via the second gear pair 66. In order to be able to transmit a torque from the second planetary shaft 12 to the side shaft 18, the movable parts of the first planetary shaft 10 must be disengaged and the second the 12 moving parts of the planetary gear must be interconnected. The first and / or the second electric machine 14, 16 are therefore controlled, so that torque balance is achieved in the first planetary gear 10, after which a first coupling unit 56 is displaced, so that it disengages a first sun gear 26 arranged at the first planetary gear 10 and a first planet gear holder. 50 from each other. Thereafter, the internal combustion engine 4 is controlled so that a synchronous speed is achieved between a second sun gear 32 arranged at the second planetary gear 12 and a second planet wheel holder 51, after which a second coupling unit 58 is displaced so as to interconnect the second planet wheel holder 51 and the second sun wheel 32. . The second planetary gear 12 thereby drives the second gear gear 68 of the second gear pair 27 66. Since the second gear 70 is engaged with the second gear gear 68 and is engaged with the side shaft 18, the second gear 70 drives the side shaft 18 and thereby transfers a torque flan the second planetary shaft 12 to the side shaft 18.
    The method further comprises the step e) of transmitting a torque from the side shaft 18 to the output shaft 20 via the third gear pair 72. Since the third gear 76 is coupled to the side shaft and the second planetary shaft 12 drives the side shaft 18, a torque will be transmitted from the side shaft 18 to the third gear 76. Since the third gear 76 engages the third gear 74, the drive torque is transmitted to the third gear 74.
    The third gear gear 74 is provided with the first main shaft 34, which is coupled to the output shaft 20 via the clutch mechanism 96. Thereby, a torque is transmitted from the side shaft 18 to the output shaft 20 via the third gear pair 72.
    According to the invention, a computer program P stored in the control unit 48 and / or the computer 53 is provided, which may comprise routines for controlling the hybrid driveline 3 according to the present invention.
    The program P can be stored in an executable manner or in a compressed manner in a memory M and / or in a read / write memory.
    The invention also relates to a computer program product comprising a program code stored on a computer readable medium for performing the above step steps when said program code is crossed on the control unit 48 or another computer 53 connected to the control unit 48. Said program code may be non-volatile stored on said of a computer 53 weldable medium.
    The stated components and features stated above can be combined within the scope of the invention between different specified embodiments. 28
    权利要求:
    Claims (13)
    [1]
    1. disengage the first gear pair (60); 2. connecting the first planetary shaft (10) to the output shaft (20) by means of a coupling mechanism (96); c) disengage a fifth gear pair (21) connected to the output shaft (20) and a side shaft (18); 4. transmitting a torque from the second planetary gear (12) to the side shaft (18) via the second gear pair (66); and 5. transmitting a torque from the side shaft (18) to the output shaft (20) via the third gear pair (72).
    [2]
    A method according to claim 1, characterized in that the first gear pair (60) comprises a first gear gear (62) engaging with each other and a first gear (64), the first gear (62) being fixedly provided with the first planetary gear (10). ) and the first gear (64) is coupled and disengaged on the side shaft (18) and the third gear pair (72) includes a third gear gear (74) and a third gear (76) in engagement with each other, the third gear (76) 74) is fixedly arranged with the first planetary shaft (10) and which third gear (76) is coupled and disengageable on the side shaft (18).
    [3]
    A method according to claim 1 or 2, characterized in that the second gear pair (66) comprises a second gear gear (68) engaged with each other and a second gear (70), which second gear gear (68) is fixedly arranged with the second planetary gear (12) and which second gear (70) is connectably and disengageably arranged on the side shaft (18). 29
    [4]
    A method according to any one of the preceding claims, characterized in that step a) comprises controlling the internal combustion engine (4) and the first electric machine (14), so that a torqueless state is achieved between the first gear pair (60) and the side shaft (18), after which a first coupling element (84) is displaced, so that the first pair of gears (60) is disengaged from the side shaft (18).
    [5]
    Method according to any one of the preceding claims, characterized in that step b) comprises controlling the internal combustion engine (4) and / or the first electric machine (14), so that a synchronous speed is achieved between a first connected to the first planetary gear (10) main shaft (34) and the output shaft (20), after which the clutch mechanism (96) is displaced so as to interconnect the first main shaft (34) and the output shaft (20).
    [6]
    A method according to any preceding hay, characterized in that step c) comprises controlling the second electrical machine (16), so that a torqueless state is achieved between the fifth gear pair (21) and the side shaft (18) followed by a fifth coupling element (93 ) advance. said that the fifth gear pair (21) is disengaged from the side shaft (18).
    [7]
    A method according to any one of the preceding claims, characterized by the further step of: c 1) before step d) coupling the third pair of gears (72) to the side shaft (18).
    [8]
    Method according to claim 6, characterized in that step c1) comprises controlling the second electric machine (16), so that a synchronous speed is achieved between the side shaft (18) and the third pair of gears (72), after which a third coupling element ( 88) offset, so that it connects the third pair of gears (72) to the side shaft (18).
    [9]
    The method according to any of the preceding claims, characterized in that step d) comprises controlling the first and / or the second electric machine (14; 16), so that torque balance is achieved in the first planetary gear (10), after which a first coupling unit (56) is displaced so that it disengages a first sun gear (26) arranged at the first planetary gear (10) and a first planet gear holder (50) from each other.
    [10]
    The method according to any of the preceding claims, characterized in that step d) further comprises controlling the internal combustion engine (4), so that a synchronous speed is achieved between a second sun gear (32) arranged at the second planetary gear (12) and a second planet gear holder ( 51), after which a second coupling unit (58) is displaced, so that it interconnects the second planet gear carrier (51) and the second sun gear (32) with each other.
    [11]
    Vehicle, characterized in that the vehicle (1) comprises a hybrid driveline (3), which is controlled according to the method in any one of claims 1-10.
    [12]
    Computer program (P) for controlling a hybrid driveline (3), wherein said computer program (P) comprises program code for causing an electronic control unit (48) or another computer (53) connected to the electronic control unit (48) to perform the steps according to any one of claims 1-10.
    [13]
    A computer program product comprising a program code stored on a computer readable medium for performing the method steps according to any one of claims 1-10, when said program code is crossed on an electronic control unit (48) or another computer (53) connected to the electronic the control unit (48). 9 0: L6 3
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    SE1450306A1|2014-09-28|Gearbox, vehicles with such gearbox, method for controlling such gearbox, computer program for controlling such gearbox, and a computer software product comprising program code
    SE1451144A1|2016-03-30|Hybrid drivetrain and a vehicle with such a hybrid drivetrain
    SE1450326A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1551239A1|2016-03-30|Hybrid drive line, method for controlling such hybrid drive line, vehicles comprising such hybrid drive line, computer program for controlling such hybrid drive line, and a computer program product comprising program code
    SE1451147A1|2016-03-30|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450315A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE538189C2|2016-03-29|Gearbox, vehicles with such gearbox, method for controlling such gearbox, computer program for controlling such gearbox, and a computer software product comprising program code
    SE1450314A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450328A1|2015-09-21|Procedure for driving a vehicle with a hybrid drivetrain, vehicles with such a hybrid drivetrain, computer programs for controlling a vehicle's driving, and a computer software product comprising program code
    SE1450324A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450327A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, a computer program for controlling a hybrid driver, and a computer software product comprising program code
    SE1450321A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450323A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450305A1|2014-09-28|Gearbox, vehicles with such gearbox, method for controlling such gearbox, computer program for controlling such gearbox, and a computer software product comprising program code
    SE1451142A1|2016-03-30|A method for controlling a hybrid driver, vehicles comprising such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450311A1|2015-09-21|Method of starting an internal combustion engine in a hybrid drive line, vehicles with such a hybrid drive line, computer programs for starting an internal combustion engine, and a computer program product comprising programs
    SE1451141A1|2016-03-30|A method for controlling a hybrid driver, vehicles comprising such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450322A1|2015-09-21|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code
    SE1450310A1|2015-09-21|Method of starting an internal combustion engine in a hybrid drive line, vehicles with such a hybrid drive line, computer programs for starting an internal combustion engine, and a computer program product comprising program code
    SE537897C2|2015-11-17|Procedure for driving a vehicle with a hybrid drivetrain, vehicles with such a hybrid drivetrain, computer programs for controlling a vehicle's driving, and a computer software product comprising program code
    SE1450318A1|2015-09-21|Method of starting an internal combustion engine in a hybrid drive line, vehicles with such a hybrid drive line, computer programs for starting an internal combustion engine, and a computer program product comprising programs
    SE1451151A1|2016-03-30|A method of operating a hybrid driver, vehicles with such a hybrid driver, computer programs to control such a hybrid driver, and a computer software product comprising program code
    SE1450319A1|2015-09-21|Procedure for starting an internal combustion engine of a hybrid drivetrain, vehicles with such an internal combustion engine, computer programs for starting such an internal combustion engine, and a computer software product included
    同族专利:
    公开号 | 公开日
    RU2653332C2|2018-05-07|
    EP3119652A4|2017-11-08|
    RU2016140145A|2018-04-20|
    KR20160132478A|2016-11-18|
    SE539030C2|2017-03-21|
    EP3119652A1|2017-01-25|
    US20170015300A1|2017-01-19|
    WO2015142252A1|2015-09-24|
    US9944273B2|2018-04-17|
    KR101828975B1|2018-02-13|
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    法律状态:
    2019-10-29| NUG| Patent has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    SE1450314A|SE539030C2|2014-03-20|2014-03-20|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code|SE1450314A| SE539030C2|2014-03-20|2014-03-20|A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code|
    PCT/SE2015/050292| WO2015142252A1|2014-03-20|2015-03-17|Method for controlling a hybrid driveline in order to achieve gear change without interruption of torque|
    EP15765393.2A| EP3119652A4|2014-03-20|2015-03-17|Method for controlling a hybrid driveline in order to achieve gear change without interruption of torque|
    US15/124,116| US9944273B2|2014-03-20|2015-03-17|Method for controlling a hybrid driveline in order to achieve gear change without interruption of torque|
    RU2016140145A| RU2653332C2|2014-03-20|2015-03-17|Method of management of a hybrid power transmission for transfer switching without torque moment interruption, vehicle and electronic device for hybrid power transmission control|
    KR1020167028705A| KR101828975B1|2014-03-20|2015-03-17|Method for controlling a hybrid driveline in order to achieve gear change without interruption of torque|
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