 Procedure for starting an internal combustion engine of a hybrid drivetrain, vehicles with such an i
专利摘要:
Summary The invention relates to a method for starting an internal combustion engine (4) in 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 planetary gear (10); a second electrical machine (16) coupled to the second planetary gear (12); at least one pair of gears (G1, 60, 72) connected to the first planetary gear (10) and the output shaft (20); and at least one pair of gears (G2, 66, 78) connected to the second planetary shaft (12) and the output shaft (20). The method comprises the steps of: a) coupling an output shaft (97) of the internal combustion engine (4) to the input shaft (8) of the gearbox (2), by means of a coupling device (106) arranged between the output shaft (97) and the input shaft (8). ); and b) controlling the first and second electric machines (14; 16) so that the internal combustion engine (4) is started. The invention also relates to a computer program (P) for starting an internal combustion engine (4) and a computer program product comprising program code for an electronic control unit (48) or another computer (53) for implementing the method according to the invention. 公开号:SE1450319A1 申请号:SE1450319 申请日:2014-03-20 公开日:2015-09-21 发明作者:Mathias Björkman；Niklas Pettersson；Johan Lindström；Mikael Bergquist 申请人:Scania Cv Ab； IPC主号:
专利说明:
A method of starting an internal combustion engine of a hybrid driveline, a vehicle with a side internal combustion engine, computer programs for starting an external combustion engine, and a computer program product comprising program code. BACKGROUND OF THE INVENTION AND PRIOR ART The present invention relates to a method for starting an internal combustion engine according to the preamble of claim 1. The invention also relates to a vehicle comprising such an internal combustion engine according to the preamble of claim 13, a computer program for starting such an internal combustion engine according to the preamble of claim 14, and a computer program product comprising program code according to the preamble of claim 15. 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 storage, such as an electrochemical energy storage for storing electrical energy and control equipment for regulating the flow of electrical energy between the energy storage and the electrical machine. The electric machine can alternately work as an engine 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 to each other. Alternatively, the electric 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 largest possible torque supplied by the internal combustion engine and the electric machine will be limited by any of these drives, the highest torque being lower than the other torque's highest torque. If 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 shifting processes in the gearbox entailed disadvantages, such as heating of the clutch slats, which results in wear of the clutch slats and also 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 shall be no other 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 accommodate large hails and torques that occur in such heavy vehicles. This results in the size and weight of the vdxelladan increasing. There are also requirements for high reliability and high reliability of the components that are in the drive device. If the gearbox contains lamella couplings, wear occurs, which affects the reliability and service life of the gearbox. 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 life of the energy storage is the number of cycles that the energy storage absorbs and absorbs strongly to and from the electrical machines. The more cycles, the shorter the lifespan of the energy storage. Under certain operating conditions, it is advisable to switch off the internal combustion engine in order to save fuel and to avoid cooling of the internal combustion engine's exhaust after-treatment system. If additional torque is added to the hybrid driveline or when the energy storage must be charged, the internal combustion engine must be started quickly and efficiently. The document EP-B1-1126987 shows a gearbox with double planetary shafts. The sun gears of each planetary gear are connected to an electric machine and the ring gears of the planetary gears are connected to each other. The planetary gear housings of each planetary gear are connected to a number of gear pairs, in such a way that an infinite number of gear steps are obtained. Another document, EP-B1-1280677, also shows how the planetary shafts 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 gearboxes. The planetary gearboxes 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 gearboxes, in which an electric machine is connected to one planetary gearbox and a double coupling cooperates with the other planetary gearbox. 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 starting an internal combustion engine of a hybrid driveline. The object of the invention is to provide a new and advantageous method for starting an internal combustion engine of a hybrid driveline. Another object of the invention is to provide a new and advantageous method for starting an internal combustion engine of a hybrid driveline when the internal combustion engine is disengaged. Another object of the invention is to provide a new and advantageous computer program for starting an internal combustion engine. 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 is characterized by the features stated in the characterizing part of claim 13. These objects are also achieved with the computer program for starting the internal combustion engine, which can be characterized by the features stated in the jugging part of claim 14. These objects are also achieved with the computer program product for starting the internal combustion engine, which can be characterized by the features set out in the characterizing part of the claim. With the method according to the invention an efficient and reliable start of the internal combustion engine is obtained when the first and / or the second electric machine achieves a desired torque of the shaft emanating from the gearbox. Such an operating condition can occur when the hybrid driveline is arranged in a vehicle and when the vehicle is driven by the first and / or the second electric machine. The internal combustion engine may be switched off in order to save fuel or to avoid cooling of the combustion engine's exhaust after-treatment system. If torque additions to the hybrid driveline are required when driving the vehicle or when the energy storage must be charged, the internal combustion engine can be started quickly and efficiently by balancing the first and second electric machines, so that the desired torque at the output shaft and required torque to start the internal combustion engine are achieved. The gearbox comprises an input shaft and an output shaft, a first planetary shaft connected to the input shaft, a second planetary shaft connected to the first planetary shaft, a first electric machine connected to the first planetary shaft, a second electric shaft machine coupled to the second planetary shaft, at least one pair of gears connected to the first planetary shaft and the output shaft and at least one pair of gears connected to the second planetary shaft and the output shaft. A shaft emanating from the internal combustion engine is suitably connected to a first planetary gear carrier of the first planetary gear via the input shaft of the gearbox, which first planetary gear carrier is connected to a second sun gear of the second planetary gear. Furthermore, a first sun gear of the first planetary shaft is fixedly coupled to a first major shaft and a second planetary gear holder of the second planetary shaft is fixedly coupled to a second major shaft. It is important that the output shaft of the internal combustion engine is as still as possible during electrical operation when the internal combustion engine is switched off. If torque is transmitted to the internal combustion engine when it is switched off, there is a risk that the shoulders of the internal combustion engine move towards bearings without a supply of oil, which can cause the bearings to wear and eventually enlarge. The output shaft of the internal combustion engine is kept suitably stationary by disengaging the output shaft from the input shaft of the gearbox by means of a coupling device arranged between the output shaft of the internal combustion engine and the input shaft of the gearbox. Thus, when the clutch device is open, the internal combustion engine is disengaged from the input shaft of the gearbox and when the clutch device is closed, the internal combustion engine is connected to the input shaft of the gearbox. In electric operation, the need for shifts becomes smaller as the first and second electric machines each have a larger speed range within which they operate efficiently, compared to the internal combustion engine. Both the first and the second electric machine preferably drive the vehicle forward during electric operation, which entails a large number of combination possibilities of different shifting steps. Shift during electric operation means that the torque contribution from one electric machine must always be reduced during the shift in order to be able to engage or disengage any pair of gears from a side shaft connected to the output shaft, and thus fire a gear shaft. In electric operation, for example, the internal combustion engine is disengaged by means of a coupling device arranged between the output shaft of the internal combustion engine and the input shaft of the shaft shaft, while the first planetary gear carrier is connected to the first sun gear and the second planetary gear carrier is connected to the second solar wheel holder. A pair of axles connected to the first planetary axle coupled to the side shaft and one with the second planetary axle is disengaged from the side axis, or vice versa. In this way, the first electric machine and the second electric machine receive the same speed, which results in a simple load distribution between the first and the second electric machine. Alternatively, the internal combustion engine is disengaged by means of the coupling device at the same time as the first planetary gear carrier is connected to the first sun gear and the second planetary gear carrier is disengaged from the second sun gear. Alternatively, the first planet wheel holder and the first sun wheel are disengaged from each other and the second planet wheel holder and the second sun wheel are connected. A pair of shaft shafts connected to the first planetary shaft is connected to the side shaft and one with the second planetary shaft is also connected to the side shaft. Alternatively, the internal combustion engine is disengaged by means of the coupling device at the same time as the first planetary gear carrier and the first sun gear are disengaged from each other and the second planetary gear carrier is disengaged from the second sun gear. A pair of shaft shafts connected to the first planetary shaft is connected to the side shaft and one with the second planetary shaft is also connected to the side shaft. The method of starting the internal combustion engine comprises the step of coupling the output shaft of the internal combustion engine to the input shaft of the gearbox, by means of the coupling device arranged between the output shaft and the input shaft. The process further comprises the step of controlling the first and second electric machines so that the internal combustion engine is started. According to the method, the output shaft of the internal combustion engine is connected to the input shaft of the gearbox by controlling the first and / or the second electric machine, so that a synchronous speed is achieved between the output shaft of the internal combustion engine and the input shaft of the gearbox. Since the output shaft of the internal combustion engine is stationary, the first electric machine is controlled so that the input shaft of the gearbox stops. The synchronous speed is thus zero. The second electric machine is controlled in the meantime, so that a desired torque of the output shaft of the gearbox is achieved. The second electric machine is suitably controlled so that the first electric machine can counteract the reaction moment produced by the second electric machine and at the same time achieve a synchronous speed between the output shaft of the internal combustion engine and the input shaft of the gearbox. When the input shaft of the gearbox has stopped, the coupling device is controlled so that the output shaft of the internal combustion engine and the input shaft of the gearbox are connected. The internal combustion engine is preferably started by controlling the first and second electric machines so that a torque required to start the internal combustion engine is provided on the output shaft of the internal combustion engine while providing a predetermined desired torque on the output shaft of the gearbox. How the first resp. the second electric machine is controlled by balancing between the desired torque of the output shaft and the torque required to start the internal combustion engine, for the selected gear. With the predetermined value of the torque required to start the internal combustion engine and the desired driveline torque, it can be determined which torques the first resp. the other electrical machine shall provide. on such salt, the internal combustion engine can be started at the same time as the hybrid driveline is electrically driven. According to one embodiment, a first planet gear carrier arranged at the first planetary gearbox and a first sun gear are interconnected, while a second planetary gear carrier arranged at the second planetary gearbox and a second sun gear wheel are disengaged. Furthermore, a pair of gears connected to the first planetary shaft 8 connected to the side shaft and a pair of gears connected to the second planetary shaft are also connected to the side shaft. The method then comprises the step of the step of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox, disengaging the first planetary gear carrier and the first sun gear from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the first planetary gear, whereby a first clutch unit is displaced, so that the first planetary gear carrier and the first sun gear are disengaged from each other. Torque balance means a state 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 sun gear of the planetary gear, corresponding to the torque acting on the planetary gear. (1-planetary gear ratio). In the event that two of the planetary gear unit's input parts, sun gear, ring gear or planet gear carrier, are connected by means of a coupling unit, no torque between the planetary gear unit parts reaches the torque balance lines opposite this coupling unit. This allows the clutch unit to be easily displaced and the integral parts of the planetary gear to be disengaged. According to another embodiment, the first planet gear carrier and the first sun gear are disengaged while the second planet gear carrier and the second sun gear are interconnected. Furthermore, a pair of gears connected to the first planetary shaft is connected to the side shaft and a pair of gears connected to the second planetary shaft is also connected to the side shaft. The method then comprises the step of the step of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox, disengaging the second planet gear holder and the second sun gear from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the second planetary gear, whereby a second clutch unit is displaced, so that the second planetary gear carrier and the second sun gear are disengaged from each other. According to a further embodiment, a first planet gear carrier arranged at the first planetary gearbox and a first sun gear wheel are connected and a second planetary gear carrier arranged at the second planetary gearbox and a second sun gear wheel are equally connected. Furthermore, a pair of gears connected to the first planetary shaft is coupled to the side shaft and the pairs of gears connected to the second planetary shaft are disengaged from the side shaft. The method then comprises the step of 9 connecting the output shaft of the internal combustion engine to the input shaft of the gearbox, disengaging the first planetary gear carrier and the first sun gear from each other. Preferably, this is accomplished by controlling the first and / or second electric machine so that torque balance is achieved in the first planetary gearbox, displacing a first clutch unit so that the first planetary gear carrier and the first sun gear are disengaged from each other. The method preferably further comprises, after the internal combustion engine has been started, coupling a pair of gears connected to the second planetary gear to the side shaft, so as to engage in a gear and enable trailing. Preferably, the engagement of the gear pair is performed by controlling the internal combustion engine to provide a synchronous speed between the gear pair connected to the second planetary gear shaft and the side shaft. According to a further embodiment, a first planet gear carrier arranged at the first planetary gearbox and a first sun gear are interconnected and a second planetary gear carrier arranged at the second planetary gearbox and a second sun gear wheel are equally connected. Furthermore, a pair of gears connected to the first planetary shaft is coupled to the side shaft and the pairs of gears connected to the second planetary shaft are disengaged from the side shaft. The method then comprises the step of the step of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox, first disengaging the first planetary gear carrier and the first solar wheel from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the first planetary gear, whereby a first clutch unit is displaced, so that the first planetary gear carrier and the first sun gear are disengaged from each other. Then a pair of gears connected to the second planetary shaft is connected to the side shaft. The coupling of the gear pair is performed by controlling the second electric machine in order to achieve a synchronous speed between the gear pair connected to the second planetary gear shaft and the side shaft. Then the second planet wheel holder and the second sun wheel are disengaged from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the second planetary gear, whereby a second coupling unit is displaced, so that the second planet gear holder and the second sun gear are disengaged from each other. The method then comprises the steps of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox and of starting the internal combustion engine as previously described. According to a further embodiment, a first planetary gear carrier arranged at the first planetary gearbox and a first sun gear are interconnected and a second planetary gear carrier arranged at the second planetary gearbox and a second solar wheel are likewise interconnected. Furthermore, the gear pair connected to the first planetary shaft is disengaged from the side shaft, while a pair of gears connected to the second planetary shaft is connected to the side shaft. The method then comprises the step of the step of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox, disengaging the second planetary gear carrier and the second sun gear from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the second planetary gear, whereby a second coupling unit is displaced, so that the second planet gear holder and the second sun gear are disengaged from each other. The method preferably further comprises, after the internal combustion engine has been started, coupling a pair of gears connected to the first planetary shaft to the side shaft, in order to place a gear in this way and enable crimping. Lamply, the engagement of the gear pair is performed by controlling the speed of the internal combustion engine to provide a synchronous speed between the gear pair connected to the first planetary gear and the side shaft. According to a further embodiment, a first planet gear carrier arranged at the first planetary gearbox and a first sun gear are interconnected and a second planetary gear carrier arranged at the second planetary gearbox and a second solar wheel are likewise interconnected. Furthermore, the gear pairs connected to the first planetary shaft are disengaged frail the side shaft, while a gear pair connected to the second planetary shaft is connected to the side shaft. The method then comprises the step of the step of coupling the output shaft of the internal combustion engine to the input shaft of the gearbox, first disengaging the second planet gear carrier and the second sun gear from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the second planetary gear, whereby a second clutch unit is displaced, so that the second planet gear holder and the second sun gear are disengaged from each other. Then a pair of gears connected to the first planetary shaft is connected to the side shaft. Lamply, the engagement of the gear pair is performed by controlling the first electric machine to provide a synchronous speed between the gear pair connected to the first planetary gear and the side shaft. Then the first planetary gear carrier and the first sun gear are disconnected from each other. Preferably this is achieved by controlling the first and / or the second electric machine, so that torque balance is achieved in the first planetary gear, whereby a first clutch unit is displaced, so that the first planetary gear carrier and the first sun gear are disengaged from each other. The method then comprises the steps of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox and starting the internal combustion engine as previously described. According to a further embodiment, a first planet gear carrier arranged at the first planetary gearbox and a first sun gear are disengaged from each other and a second planetary gear carrier arranged at the second planetary gearbox and a second sun gear wheel are likewise disengaged from each other. Furthermore, a pair of gears connected to the first planetary shaft is connected to the side shaft and a pair of closed gears connected to the second planetary shaft are likewise connected to the side shaft. The method of starting the internal combustion engine then comprises the steps of interconnecting the output shaft of the internal combustion engine with the input shaft of the gearbox and controlling the first and second electric machines so that the internal combustion engine is started. According to one embodiment, the desired torque of the output shaft is achieved via a fifth gear pair arranged between the output shaft and the side shaft. 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 comprise with a side shaft mechanically loadable and disengageable gears. This provides a number of fixed gear steps, which can be geared 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 to be loadable and disengageable on the first or second main shaft. The gear pairs each have a gear ratio, which is adapted to the vehicle's desired chore 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. 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 gear 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 wheels do 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 shows a schematic side view of a vehicle comprising a hybrid driveline with an internal combustion engine, arranged to be started according to the method Fig. 2 shows a schematic side view of a hybrid driveline with an internal combustion engine, which is arranged to be started according to the method, according to the present invention, Fig. 3 shows a simplified schematic view of the hybrid driveline in Fig. 2, and Figs. 4a-4b show flocculation diagrams regarding methods for starting an internal combustion engine in 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 2 and an internal combustion engine 4, which is engaged in a hybrid driveline 3. The internal combustion engine 4 is connected to the gearbox 2 and the gearbox 2 is 2 further connected to the drive wheel 6 of the vehicle 1 via a cardan 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 main shaft 34 parallel to and next to the second main shaft 36. 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 boat, 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 conducted 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 inlet shaft 8 of the gearshaft 2 is connected to the first planet gear holder 50. shaft 8 is further connected to the output shaft 97 of the internal combustion engine 4 via a coupling device 106. By opening the coupling device 106, the combustion engine 4 can be disengaged from the gearbox 2 and the vehicle 1 can thus be electrically driven by the first and second electric machines 14, 16. The coupling device 106 can consists of splined parts, which cooperate with a coupling sleeve. Alternatively, the coupling device 106 may be a friction coupling. 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 will 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, so 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 to 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 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 carrier 51 and the second sun gear 32 are 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 planet gear holder 51. However, it is possible to arrange an additional or alternative coupling unit (not shown) between the first ring gear 22 and the first planet wheel holder 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. Connected to the first and second main shafts 34, 36 is a transmission device 19, which comprises a first gear pair 60, which is arranged between the first planetary gear shaft 10 and the output shaft 20. The first gear pair 60 comprises a first gear drive 62 and a first gear 64 , which are in engagement with each other. A second gear pair 66 is disposed between the second planetary gear 12 and the output shaft 20. The second gear pair 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 gear pair 78 is disposed between the second planetary gear 12 and the output shaft 20. The fourth gear pair 78 includes a fourth gear gear 80 and a fourth gear 82, which are engaged with each other. On the first main shaft 34, the first and third gear gears 62 and 62, respectively. 74 arranged. The first and third gears 62 and 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 are the first, second, third and fourth gears 64, 70, 76 and 76, respectively. 82 stored 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 16 fifth and sixth coupling sleeves 83, 85, which mechanically engage with the splined portions of the 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 can occur between the 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 is 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 pair of shafts 66 and to further transmit torque from the side shaft 18 to the output shaft 20 via, for example, the output shaft 20. the gear pair 60. Thereby a number of gear steps are obtained, where torque from one planetary 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 output shaft 2, however, this presupposes that a coupling mechanism 96 arranged between the first main shaft 34 and the output shaft 20 is coupled, 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 formed by spline-provided portions formed on the fifth gear 92 and the side shaft 18, which cooperate with a ninth coupling sleeve 87, which clamping sleeve 87 the portions of the fifth gear 92 and the side shaft 18. In the disengaged joint, 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 input shaft 8 of the gearbox 2 to the output shaft 20 of the gearbox 2 takes place via the first or the second planetary gear 10 or 12 and the side shaft 18. The torque transmission can also take place directly via the first planetary gear shaft 10, the first sun gear 26 via the first main shaft 34 is connected to the shaft shaft 20 output shaft 2 via a coupling mechanism 96. The coupling mechanism 96 preferably comprises a splined seventh coupling sleeve 100, which is axially displaceable on the first major shaft 34 and the output shaft 20 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 downwards will have the same speed. By disengaging the fifth gear pair 92 of the fifth gear pair 21 from the side shaft 18, torque from the second planetary gear 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 gear shaft 10 to finally transmit torque to the gear shaft 96 via the clutch mechanism 96. 2 output shaft 20. During operation, the gearbox 2 can 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 aid 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 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 work as a generator to generate electrical energy for the energy storage 46. Alternatively, the electrical machine 14 resp. 16 provide a torque supplement so as 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 releases the vehicle's accelerator pedal (not shown). The output shaft 20 of the shaft load 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 hdr electrical energy which is stored in the energy storage 46 in the vehicle 1. This operating state bends the regenerative braking. 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. Disengagement of the output shaft 97 of the internal combustion engine 4 can be performed when the vehicle is to be driven by only one or both electric machines 14 resp. 16 with internal combustion engine shut-off. If one or 18 of the two electric machines 14 resp. 16 torques overcome the 4 torques of the internal combustion engine and with regard to the gear ratio between them, the internal combustion engine 4 will not be able to 5,11a. against the large torque that the electric machines 14 resp. 16, so that a disengagement of the output shaft 97 of the internal combustion engine 4 becomes necessary. The control unit 48 is connected to the electrical machines 14 resp. 16 and is adapted to control the electrical machines 14 resp. 16 so that during 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 the output energy of the output shaft 2 of the output shaft 2 uses 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 gear shaft 2 to collect 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 controls the alien flow of electrical energy between the energy storage 46 and resp. stator 40 resp. 44 of the electric 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 electric machines 14 resp. 16 works as a generator supplied with electrical energy from 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. preferably displaced by power means (not shown), such as hydraulically or pneumatically driven cylinders. The 5,104 is also possible to displace the coupling sleeves with electrically driven power means. 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 19 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. According to the embodiment above, it is stated that the gearbox 2 comprises on main shafts 34, 36 resp. side shafts 18 provide 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 is constituted by at least one gear pair connected to the first main shaft 34 and below the first planetary shaft 10 and G2 is constituted by 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, for example, be 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. Embodiments for starting the internal combustion engine 4 are described below. According to one embodiment, the internal combustion engine 4 is disengaged from the shaft 8 of the gear shaft 2 by means of the coupling device 106, while the first planet gear holder 50 and the first sun gear 26 are disengaged from each other and the second planet wheel holder 51 is disengaged from the second sun wheel 32. the first planetary gear 10 connected gear pair G1 is connected to the side shaft 18 and a gear pair G2 connected to the second planetary shaft 12 is similarly connected to the side shaft 18. The method of starting the internal combustion engine 4 then comprises the step of connecting the output shaft 97 of the internal combustion engine 4 to the shaft 8 , by means of the coupling device 106. The first and the second electric machine 14, 16 are controlled so that a synchronous speed is achieved between the output shaft 97 of the internal combustion engine 4 and the input shaft 8 of the gearbox 2, after which the coupling device 106 is controlled so that the ram shafts 97, 8 are connected. The method further comprises the step of controlling the first and the second electric machine 14, 16, so that the internal combustion engine 4 is started. This meant that the first resp. the second electric machine 14, 16 is controlled, so that a sufficient torque TFlywheel is obtained on the shaft 97 of the internal combustion engine 4 at the same time as a predetermined desired torque Tdrv on the output shaft 20 of the gearbox is provided. How the first resp. the second electric machine 14, 16 is controlled by balancing between the desired torque Tdrv of the output shaft 20 and the torque required THywheei to start the internal combustion engine 4, for the selected gear. The torque THywhm obtained on the internal combustion engine 4 is determined by the equation El below: S + R1 TEM 2 S = TEm 1 TFlywheel R [El] TEmi is the torque emitted by the first electric machine 14 and TEm2 is the torque emitted by the second electric machine 16, Si is the number of teeth of the first sun gear 26, R1 is the number of teeth of the first ring gear 22, S2 is the number of teeth of the second sun wheel and R2 is the number of teeth of the second ring wheel 28. In cases where the gear pair G3 connected to the side shaft 18 and the output shaft 20 is connected and loaded on the side shaft 18 and a coupling mechanism S6, 96 arranged between the first main shaft 34 and the output shaft 20 is open, the desired torque Td r is determined „Of the output shaft 20, also called the driveline torque, by a combination of torques from the first and the second electric machine 14, 16 according to equation E2 below: S + R 1 TDrv = —TEM 1 S1 + TEM 2 22 R1 G1G3R2 G2G3 Gi is the gear ratio between the first main shaft 34 and the side shaft 18, G2 is the gear ratio between the second main shaft 36 and the side shaft 18, and G3 is the gear ratio between the side shaft 18 and the output shaft 20, for selected gear pairs G1, G2, G3. [E2] In cases where the gear pair G3 connected to the side shaft 18 and the output shaft 20 is disengaged, the side shaft 18 and the clutch mechanism S6, 96 are loaded and claimed, the first 21 main shaft 34 and the output shaft 20, 1) become the torque Tdn , of the output shaft 20 of the gear E1 'of the equation E2' below: T S2 ± R2 G1 „= —T - D EM + TEM2 R2 G2 [E2 '] With predetermined values of torque TFlywheel required to start the internal combustion engine 4 and desired driveline torque Tdrv, the two equations El, E2, alternatively El, E2 ', can be solved in order to determine on which salt the torques the first resp. the second electrical machine 14, 16 shall provide. In this way, the internal combustion engine 4 can be started at the same time as the hybrid driveline is electrically driven. According to another embodiment, the internal combustion engine 4 is disengaged by the coupling device 106 at the same time as the first planet gear holder 50 is connected to the first sun gear 26 and the second planet wheel holder 51 is disengaged from the second sun wheel 32. Alternatively, the first planet gear holder 50 and the first sun gear 26 are disengaged from each other and the second planet wheel holder 51 and the second sun gear 32 are interconnected. A gear pair G1 connected to the first planetary gear 10 is connected to the side shaft and a gear pair G2 connected to the second planetary shaft 12 is similarly connected to the side shaft. The fifth gear pair G3 is suitably engaged and loaded on the side shaft 18. The method of starting the internal combustion engine 4 then comprises the step of disengaging the first planet gear carrier 50 and the first sun gear 26 from each other, or alternatively disengaging the second planet wheel holder 51 and the second sun gear 32 separate from each other, depending on which are connected. The disengagement is achieved by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved in the current planetary gear 10, 12, after which a coupling unit 56, 58 is displaced, so that the planetary gear holder 50, 51 and the sun gear 26, 32 are disengaged. each other. Thereafter, the output shaft 97 of the internal combustion engine 4 is connected to the input shaft 8 of the gearbox 2, by means of the coupling device 106 and the first and second electric machines 14, 16 are controlled to start the internal combustion engine 4 in accordance with the embodiment described above. According to a further embodiment, the internal combustion engine 4 is disengaged from the input shaft 8 of the gearbox 2 by means of the coupling device 106 while the first planet gear holder 22 is coupled to the first sun gear 26 and the second planet gear holder 51 is coupled to the second sun wheel 32. One with the first the gear shaft 10 connected to the planetary shaft 10 is connected to the side shaft 18 and the gear pairs G2 connected to the second planetary gear 12 are disengaged from the side shaft 18. The fifth gear pair G3 is suitably engaged and loaded on the side shaft 18. The method then comprises the step of disengaging it at the front plane. the gear 10 arranged the first planet gear holder 50 and the first sun gear 26 apart. This 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, the first clutch unit 56 being displaced so that the first planet gear carrier 50 and the first sun gear 26 are free. disconnected from each other. The method further comprises the step of coupling a gear pair G2 connected to the second planetary shaft 12 to the side shaft 18. The second electric machine 16 is controlled so that a synchronous speed is achieved between the gear pair G2 connected to the second planetary shaft 12 and the side shaft 18. Then a coupling element ( for example 86, 90), so that the gear pair G2 is coupled to the side shaft 18. The method further comprises the step of disconnecting the second planet gear holder 51 and the second sun gear 32 from each other by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved in the second planetary gear 12, whereby the second clutch unit 58 is displaced, so that the second planetary gear holder 51 and the second sun gear 32 are disengaged from each other. The method further comprises the steps of subsequently connecting the output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of the coupling device 106 and of controlling the first and second electric machines 14, 16 to start the internal combustion engine 4, in accordance with the embodiments described. above. According to a further embodiment, the internal combustion engine 4 is disengaged from the input shaft 8 of the gearbox 2 by means of the coupling device 106 at the same time as the first planet gear holder 50 is coupled to the first sun gear 26 and the second planet gear holder 51 is coupled to the second planet wheel 32. Connected gear pair G1 air connected to the side shaft 18 and the gear pairs G2 air connected to the second plane gear 12 disengaged from the side shaft 18. The fifth gear pair G3 air is suitably connected and loaded on the side shaft 18. The method then comprises the step of disengaging it at the first planetary gear 10, the first planet gear holder 50 and the first sun gear 26 are spaced apart. This is accomplished by controlling the first and / or second electric machine 14, 16, so that torque balance is achieved in the first planetary gear 10, the first clutch unit 56 being displaced, so that the first planetary gear carrier 50 and the first sun gear 26 are disengaged. from each other. The method further comprises the steps of coupling the output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of the coupling device 106 and controlling the first and second electric machines 14, 16 to start the internal combustion engine 4, in accordance with the embodiments described above, with the difference that the second electric machine 16 does not have a flaw effect in equations E2 and E2 '. Thereafter, the method includes the step of coupling a pair of gears G2 connected to the second planetary shaft 12 to the side shaft 18. The internal combustion engine 4 is thereby controlled so as to provide a synchronous speed between the pair of gears G2 connected to the second planetary shaft 12 and the side shaft 18. for example 86, 90), so that the gear pair G2 is connected to the side shaft 18. In this way, the monitoring is possible after the internal combustion engine has started. According to a further embodiment, the internal combustion engine 4 is disengaged from the input shaft 8 of the gearbox 2 by means of the coupling device 106 while the first planet gear holder 50 is coupled to the first sun gear 26 and the second planet gear holder 51 is coupled to the second sun gear 32. One with the second planet shaft 32. 12 connected gear pair G2 is connected to the side shaft 18 and the gear pairs G1 connected to the first planetary shaft 10 are disengaged from the side shaft 18. The fifth gear pair G3 is suitably engaged and loaded on the side shaft 18. The method comprises the step of disengaging the second planetary gear 12 the planet gear holder 51 and the second sun gear 32 frail each other. This is achieved by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved in the second planetary gear 12, the second clutch unit 58 being displaced, so that the second planetary gear holder 51 and the second sun gear 32 are disengaged from each other. The method further comprises the step of coupling a gear pair G1 connected to the first planetary shaft to the side shaft 18. The first electric machine 14 is controlled so that a synchronous speed is achieved between the gear pair G1 connected to the first planetary gear 10 and the side shaft 18. Then a coupling element (for example 84, 88), so that the gear pair G1 is coupled to the side shaft 18. The method further comprises the step of disengaging the first planet gear holder 50 and the first sun gear 26 from each other by controlling the first and / or the second electric machine 14, 16, so torque balance is achieved in the first planetary gear 10, the first clutch unit 56 being displaced so that the first planetary gear carrier 50 and the first sun gear 26 are disengaged from each other. The method further comprises the steps of subsequently connecting the output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of the coupling device 106 and of controlling the first and second electric machines 14, 16 to start the internal combustion engine 4, according to the embodiments described above. According to a further embodiment, the internal combustion engine 4 is disengaged from the input shaft 8 of the gearbox 2 by means of the coupling device 106 while the first planet gear holder 50 is coupled to the first sun gear 26 and the second planet gear holder 51 is coupled to the second sun gear 32. One with the second planet shaft 32. 12 connected gear pair G2 is connected to the side shaft 18 and the gear pairs G1 connected to the first planetary shaft 10 are disengaged from the side shaft 18. The fifth gear pair G3 is suitably engaged and loaded on the side shaft 18. The method then comprises the step of disengaging it at the second planetary gear 12, the second planet gear holder 51 and the second sun gear 32 are arranged apart. This 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, the second clutch unit 58 being displaced, so that the second planet gear holder 51 and the second sun gear 32 are disengaged. each other. The method then comprises the steps of coupling the output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of the coupling device 106 and controlling the first and second electric machines 14, 16 to start the internal combustion engine 4, in accordance with the embodiments described above, with the difference that the first electric machine 14 does not have a flaw effect in equations E2 and E2 '. Thereafter, the method suitably comprises the step of coupling a gear pair G1 connected to the first planetary shaft 10 to the side shaft 18. The internal combustion engine 4 is controlled armed so that a synchronous speed is provided between the gear pair G1 connected to the first planetary gear 10 and the side shaft 18. coupling elements (for example 84, 88), so that the gear pair G1 is connected to the side shaft 18. In this way, monitoring is possible after the internal combustion engine has been started. Fig. 4a shows a method for starting an internal combustion engine 4 in a hybrid driveline 3, comprising a gearbox 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 gear 12, which is coupled to the first planetary gear 10; a first electric machine 14 coupled to the first planetary gear 10; a second electrical machine 16 coupled to the second planetary shaft 12; at least one gear pair G1, 60, 72 connected to the first planetary gear 10 and the output shaft 20; and at least one gear pair G2, 66, 78 connected to the second planetary shaft 12 and the output shaft 20, the method comprising the steps of: coupling an output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of a coupling device 106 arranged between the output shaft 97 and the input shaft 8; and control the first and second electric machines 14, 16, so that the internal combustion engine 4 is started. The output shaft 97 of the internal combustion engine 4 is coupled to the input shaft 8 of the gearbox 2 by controlling the first electric machine 14, so that a synchronous speed is achieved between the output shaft 97 of the internal combustion engine 4 and the input shaft 8 of the gearbox 2. 97 is stationary when the coupling device 106 is open, the first electric machine 14 is controlled so that the input shaft 8 of the gearbox 2 stops. When the input shaft 8 has stopped, the coupling device 106 is controlled so that the output shaft 97 of the internal combustion engine 4 and the input shaft 8 of the gearbox 2 are connected. The internal combustion engine is preferably started by controlling the first and second electric machines 14, 16 so that a torque TFlywheel required to start the internal combustion engine 4 is provided on the output shaft 97 of the internal combustion engine 4 while a predetermined desired torque Tdrv on the output shaft 2 of the gearbox 2 20 is achieved. How the first resp. the second electric machine 14, 16 is controlled by balancing between the desired torque Tdrv of the output shaft 20 and the torque required TRywheel to start the internal combustion engine 4, for the selected gear. Fig. 4b shows a flow chart of a method of starting an internal combustion engine 4 in a hybrid driveline 3 where the first sun gear 26 arranged at the first planetary gear 10 and the first planetary gear holder 50 are interconnected and the second sun gear 32 and the second planetary gear 12 arranged at the second planetary gear shaft 12 are connected. the second planet gear holder 51 is interconnected. The gear pair G1, 60, 72 connected to the first planetary shaft 10 is connected to the side shaft 18 by means of coupling elements 84, 88 (see Fig. 2) and the gear pair G2, 66, 78 connected to the second planetary shaft 12 is disengaged from the side shaft 18. The internal combustion engine 4 is disengaged from the input shaft 8 of the gearbox 2 through a coupling device 106, arranged between the output shaft 97 of the internal combustion engine 4 and the input shaft 8 of the gearbox 2. The internal combustion engine 4 is thus stationary. The method of starting the internal combustion engine 4 comprises the step c) of disengaging the first planet gear holder 50 and the first sun gear 26 from each other by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved in the first planetary gear 10. Then a second clutch assembly 56 is displaced so that the first planet gear holder 50 and the first sun gear 26 are disengaged from each other. The method further comprises the step e) of coupling a gear pair G2, 66, 78 connected to the second planetary shaft 12 to the side shaft 18, by controlling the second electric machine 16, so that a synchronous speed is achieved between the gear pair G2 connected to the second planetary gear 12, 66, 78 and the side shaft 18. Then a coupling element (for example 86 or 90) is controlled, so that the gear pair G2, 66, 78 is connected to the side shaft 18. The method then comprises step d) disengaging a second planet gear holder 51 and a second sun gear 32 arranged at the second planetary gear 12, 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 a second clutch unit 58 is displaced, so that the second planet gear holder 51 and the second sun gear 32 are disengaged from each other. The method further comprises the step a) of coupling the output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of the coupling device 106. The first electric machine 14 is controlled so that a synchronous speed is achieved between the output shaft 97 of the internal combustion engine 4 and shaft 8 of the gear shaft 2, after which the coupling device 106 is controlled, so that the output shaft 97 of the internal combustion engine 4 and the shaft 8 of the gear shaft 2 are connected. The method further comprises step b) controlling the first and second electric machines 14, 16, so that the internal combustion engine 4 is started, by balancing a desired torque Tthy of the output shaft 20 and the required torque TRywheel to start the internal combustion engine 4, for selected vaxel. Fig. 4c shows a flow chart of a method for starting an internal combustion engine 4 in a hybrid driveline 3 where the first sun gear 26 arranged at the first planetary gear 10 and the first planet gear holder 50 are interconnected and the second sun gear 32 and the second planetary gear 12 arranged at the second planetary gear second planetary gear holder 51 dr interconnected. The gear pair G 1, 60, 72 connected to the first planetary shaft 10 is disengaged from the side shaft 18 and the gear pair G2, 66, 78 connected to the second planetary shaft 12 is connected to the side shaft 18 by means of coupling elements 86, 90 (see Fig. 2). . The internal combustion engine 4 is disengaged from the input shaft 8 of the gearbox 2 through a coupling device 106, arranged between the output shaft 97 of the internal combustion engine 4 and the input shaft 8 of the gearbox 2. The internal combustion engine 4 is thus stationary. Method of starting the internal combustion engine 4 comprises the step d) of disengaging the second planet gear holder 51 and the second sun gear 32 from each other, by controlling the first and / or the second electric machine 14, 16, so that torque balance is achieved in the second planet gear 12 , after which a second clutch unit 58 is displaced, so that the second planet gear holder 51 and the second sun gear 32 are disengaged from each other. The method then comprises the step a) of coupling the output shaft 97 of the internal combustion engine 4 to the input shaft 8 of the gearbox 2, by means of the coupling device 106. The first electric machine 14 is controlled so that a synchronous speed is achieved between the output shaft 97 of the internal combustion engine 4 and the gearbox 2 input shaft 8, after which the coupling device 106 is controlled, so that the output shaft 97 of the internal combustion engine 4 and the input shaft 8 of the gearbox 2 are connected. The method further comprises the step b) of controlling the first and the second electric machine 14, 16, so that the internal combustion engine 4 is started, by balancing a desired torque Tdrv of the output shaft 20 and the required torque Tnywh „If to start the internal combustion engine 4, for selected gear. After starting the internal combustion engine 4, the method suitably comprises the step f) of coupling a gear pair G1, 60, 72 connected to the first planetary gear shaft to the side shaft 18, by controlling the internal combustion engine 4, so that a synchronous speed is achieved between that connected to the first planetary gear shaft 10. the gear pair Gl, 60, 72 and the side shaft 18. pa so sat possible- Ors ivagkorning. According to the invention, there is provided a computer program P. stored in the control unit 48 and / or the computer 53 which may comprise routines for starting the internal combustion engine 4 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 behalf of a computer 53 weldable medium. The stated components and features mentioned above can be combined within the scope of the invention between different specified embodiments. 29
权利要求:
Claims (1) [1] 1. .z 'Co 9/6 91, 4/4
类似技术:
公开号 | 公开日 | 专利标题 SE1450309A1|2014-09-28|Hybrid drive line with a gearbox, vehicles with such hybrid drive line, method for controlling such hybrid drive line, computer program for controlling such hybrid drive line, and a computer program product comprising program code 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 SE540230C2|2018-05-02|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 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 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 SE1450325A1|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 SE540406C2|2018-09-11|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 SE539028C2|2017-03-21|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 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 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 SE538187C2|2016-03-29|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 SE540693C2|2018-10-09|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 SE538188C2|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 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 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 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 SE537896C2|2015-11-17|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 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 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 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
同族专利:
公开号 | 公开日 RU2016140149A|2018-04-20| RU2653340C2|2018-05-07| KR20160135786A|2016-11-28| US20170015310A1|2017-01-19| US10384671B2|2019-08-20| WO2015142269A1|2015-09-24| SE539661C2|2017-10-24| EP3120009A4|2017-11-29| KR101828987B1|2018-03-29| EP3120009A1|2017-01-25|
引用文献:
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申请号 | 申请日 | 专利标题 SE1450319A|SE539661C2|2014-03-20|2014-03-20|Method for starting an internal combustion engine of a hybrid drive line, vehicles with such an internal combustion engine, computer programs for starting such an internal combustion engine, and a computer program product comprising program code|SE1450319A| SE539661C2|2014-03-20|2014-03-20|Method for starting an internal combustion engine of a hybrid drive line, vehicles with such an internal combustion engine, computer programs for starting such an internal combustion engine, and a computer program product comprising program code| RU2016140149A| RU2653340C2|2014-03-20|2015-03-17|Method of the internal combustion engine starting, vehicle and electronic control device for starting the engine| KR1020167029157A| KR101828987B1|2014-03-20|2015-03-17|Method for starting a combustion engine in a hybrid driveline| EP15765068.0A| EP3120009A4|2014-03-20|2015-03-17|Method for starting a combustion engine in a hybrid driveline| US15/124,845| US10384671B2|2014-03-20|2015-03-17|Method for starting a combustion engine in a hybrid driveline| PCT/SE2015/050309| WO2015142269A1|2014-03-20|2015-03-17|Method for starting a combustion engine in a hybrid driveline| 相关专利
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