瑞典专利SE1450309A1 Hybrid drive line with a gearbox, vehicles with such hybrid drive line, method for controlling such

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Summary The invention relates to a hybrid driveline comprising an internal combustion engine (4) and a gear shaft (2) having 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). which is 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 (G 1, 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 gear (12) and the output shaft (20), a coupling device (106) being arranged between the internal combustion engine (4) and the gearbox (2), so that the internal combustion engine (4) can be disengaged from the gearbox (2). The invention also relates to a method for controlling said hybrid driveline (3), a computer program (P) for controlling the hybrid driveline (3) 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. (Fig. 2)
公开号:SE1450309A1
申请号:SE1450309
申请日:2014-03-20
公开日:2014-09-28
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 PRIOR ART The present invention relates to a hybrid driveline according to the preamble of claim 1. The invention also relates to a vehicle comprising such a hybrid driveline according to the preamble of claim 12, a method for controlling such a hybrid driveline according to the preamble of claim 13, a method for controlling such a hybrid driveline according to the preamble of claim 25, a computer program for controlling a such a hybrid driveline according to the preamble of claim 30, and a computer program product comprising program code according to the preamble of claim 31.
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 rotates 2 leads 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 highest 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 can not 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. If additional components, such as a regenerative braking device, are to be included, another requirement is made 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 an increase in the size and weight of the gear shaft.
There are also requirements for high reliability and high reliability of the components that are in the drive device. In the event that 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. In the case where the hybrid driveline is arranged in a vehicle, this means that the vehicle is driven by the electric machines. In a hybrid driveline, problems can arise if only the electrical machines are activated. If the crankshaft of the internal combustion engine is driven by the electric machines without the internal combustion engine being activated, excessive wear of the internal combustion engine bearings may occur. The document EP-B1-1126987 shows a gearbox with double planetary shafts. The sun gear of each planetary gear is 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 shaft step arranged on the output shaft of the internal combustion engine.
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 wheel shallare, which is connected to the input shaft of the transmission.
Document WO2008 / 046185-A 1 shows a hybrid transmission with two planetary gearboxes, wherein 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 field, there is a need to further develop a hybrid driveline and a method for controlling such a hybrid driveline, in order to optimize the fuel consumption of the hybrid driveline. In particular, there is a need to further develop a hybrid driveline and a method for controlling the hybrid driveline, which enables electric operation in a simple manner.
The object of the invention is to provide a new and advantageous hybrid driveline, which enables electric operation in a simple manner.
Another 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 with the hybrid driveline stated in the preamble, which can be characterized by the features stated in the can-drawing 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 12.
These objects are also achieved by the method stated in the introduction, which can be characterized by the features stated in the characterizing part of claim 13.
These objects are also achieved by the method stated in the introduction, which can be characterized by the features stated in the characterizing part of the claim.
These objects are also achieved with the computer program for controlling the hybrid driveline, which is illustrated by the features set forth in the characterizing part of the claim.
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 31.
The hybrid line of the present invention comprises a gearbox and a gearbox connected to the gearbox. The gearbox in turn comprises an input shaft and an output shaft, a first planetary shaft which is connected to the input shaft, a second planetary shaft which is connected to the first planetary shaft, a first electric machine which is connected to the first the planetary gear, a second electric machine, which is connected 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. By providing the hybrid driveline with a coupling device arranged between the internal combustion engine and the gearbox, the internal combustion engine can be disengaged from the gearbox and the hybrid driveline can be electrically driven by the first and the second electric machine.
The internal combustion engine can be disengaged in order to save fuel or to avoid cooling of the internal combustion engine's exhaust after-treatment system. It is important that the output shaft of the internal combustion engine is as still as possible during electric operation. If the torque is transferred to the internal combustion engine when it is switched off, there is a risk that the shafts of the internal combustion engine move towards bearings without a supply of oil, which can lead to the bearings being enlarged. The output shaft of the internal combustion engine is allowed to stand still according to the present invention by arranging the coupling device between the output shaft of the internal combustion engine and the gearbox. When the coupling device is open, the combustion engine is disengaged from the gearbox and when the coupling device is closed, the combustion engine is connected to the gearbox. 6 In electric operation, the need for switching is reduced as the first and second electric machines each have a larger speed range, which they work 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.
Shifting during electric operation meant that the torque contribution from one electric machine must always be reduced during the shifting in order to be able to engage or disengage an arbitrary pair of shafts from a side shaft connected to the output shaft, and thus attach a gear.
The first planetary gearbox suitably comprises a first planetary gear carrier, which is connected to a second sun gear of the second planetary gearbox. 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. The first planetary gear carrier is preferably connected to the input shaft of the gearbox.
The coupling device is suitably arranged between the output shaft of the internal combustion engine and the first planetary shaft. Lamply the coupling device arranged between the output shaft of the internal combustion engine and the first planetary gear carrier. Preferably, the coupling device is arranged between the output shaft of the internal combustion engine and the input shaft of the gearbox.
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, gear 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 desired driving characteristics of the vehicle. 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 side shaft is arranged between the respective first and second planetary shafts and the output shaft, to which side shaft the at least one gear pair connected to the first planetary shaft and the at least one gear pair connected to the second planetary shaft are also connected. Lampwise, the side shaft is connected to the output shaft via a fifth pair of gears. The fact that the at least one gear pair connected to the first planetary shaft and the at least one pair of gears connected to the second planetary shaft are connected to the side shaft may mean that the gear pairs are readily and releasably arranged on the side shaft. Alternatively, this means that the at least one gear pair connected to the first planetary shaft is readily and releasably arranged on the first main shaft and that the at least one gear pair connected to the second planetary shaft is readily and releasably arranged on the second main shaft.
A clutch mechanism is arranged between the first main shaft and the output shaft.
By providing the gearbox, which comprises two interconnected planetary shafts, with a gear element, which is arranged between a side shaft and the output shaft of the gearbox, a number of gear steps are obtained, where torque from one planetary shaft can be transmitted to the side shaft and further from the side shaft to a the second planetary shaft connected to the main shaft to finally transmit torque to the output shaft of the gearbox.
The electrical machines, which are connected to the planetary shafts, can generate current and / or supply torques depending on the desired operating condition. The electrical machines can also supply each other with power during certain operating conditions.
According to one embodiment, the hybrid driveline is provided with a number of gear pairs, which comprise mechanically weldable gears with the side shaft. The gears that can be loaded on the side axle also mean that a compact design with high reliability and high reliability is obtained.
According to one embodiment, a first and a second coupling unit are arranged between planetary gear carriers and sun gear at the respective planetary shafts. 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 force 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.
Preferably, a method of controlling the hybrid driveline comprises the steps of ensuring that the internal combustion engine is disengaged by means of a coupling device, rotatable components of the second planetary gear from each other; connect the gear pair connected to the first planetary gear; disengage the gear pair connected to the second planetary gear; and two rotatable components of the second planetary gear with each other.
Preferably, a method of controlling the hybrid driveline comprises the steps of ensuring that the internal combustion engine is disengaged by means of a coupling device; disengaging rotatable components of the first planetary gear from each other; coupling a pair of gears connected to the second planetary gear; disengage a pair of gears connected to the first planetary gear; and interconnecting two rotatable components of the first planetary gear.
In order to be able to disengage a planetary gear's planetary gear carrier and sun gear from each other, the hybrid driveline is controlled, so that torque balance is achieved in the planetary gear. 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 planetary gear carrier and the planetary gear ratio, while a torque acts on the planetary gear sun gear, corresponding to the torque acting on the planetary gear and planetary gear gear ratio). In the event that two of the planetary gear unit's input parts, sun gear, ring gear or planet gear holder, 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 input parts of the planetary gear to be disengaged. 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 a hybrid driveline according to the present invention, Fig. 2 shows a schematic side view of a hybrid driveline with a gearbox according to the present invention, Fig. 3 shows a simplified schematic view of the hybrid driveline in Fig. 2, Fig. 4 shows a flow chart of a method for controlling a hybrid driveline according to the present invention, and Fig. shows a flow chart of a method of controlling 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 engage 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 cardan shaft 9. The drive wheels 6 are provided with braking devices 7 for braking the vehicle 1.
Fig. 2a 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 major axis 34 parallel to and adjacent to the second major axis 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 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 diverted 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. The internal combustion engine 4 is connected to the gearbox 2 by 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. By opening the coupling device 106 the internal 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 the machine 14, 16. The coupling device 106 can be constituted by splined portions, which 11 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 attaching the first coupling unit 56, so 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, 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 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.
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 shaft 10 and the output shaft 20. The first gear pair 60 includes a first gear gear 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 10 and the output shaft 20. The third gear pair 72 comprises 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 and 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 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 82.
The first, second, third and fourth gears 64, 70, 76 resp. 82 can be individually fixed 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 layer a relative rotation may 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 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 releasably arranged 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, for example, the first shaft. the gear pair 60. Thereby a number of gear steps are obtained, where moments 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 gear shaft 2 output shaft 20. This presupposes, however, 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 engages the spline sleeve 87. the 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 input shaft 8 of the gearbox 2 to the output shaft 20 of the gearbox 2 can take 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 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 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 to the output shaft 20, which upon rotation will thus have the same speed. By disengaging the fifth gear pair 52 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 transfer 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 this salt. During certain operating cases, 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 output shaft 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. The output shaft 97 of the internal combustion engine 4 is disengaged so as to become independent of the idle speed of the internal combustion engine during braking. Thus, only one or the two electric machines 14 resp. 16 to act as a brake and 16 to generate electrical energy, which is stored in the energy store 46.
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 for 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 electrical 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 planet 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 The coupling sleeves are preferably displaced by power means (not shown), such as hydraulically or pneumatically driven cylinders. It 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 14 resp. 16. However, it is possible to design a 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, a shift from a first gear to a sixth gear is described when the hybrid driveline 3 is arranged in a vehicle 1. The first planet gear carrier 50 and the first sun gear 26 are connected by means of the first coupling unit 56. Furthermore, the second planet gear carrier 51 and the second the sun gear 32 is connected by means of the second coupling unit 58. The coupling unit 106 is open and the internal combustion engine 4 is thereby disengaged and the vehicle 1 is propelled by the first and the second electric machine 14, 16.
At a first gear, the gear pairs 60, 72 connected to the first planetary gear 10 are disengaged from the side shaft 18 while the fourth gear pair 78 is coupled to the side shaft 18. Thus, the fourth gear 82 is coupled to the side shaft 18 by the fourth coupling member 90. The fifth gear pair 21 is coupled to the side shaft 18.
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 in comparison with 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, so in such an embodiment it the second gear pair 66 would be engaged when the lowest gear is engaged.
To shift to a second gear, the first electric machine 14 and the second electric machine 16 are controlled so that torque balance is achieved in the second planetary gear 12. Then the second clutch unit 58 is displaced so that the second planetary gear holder 51 and the second sun gear 32 are disengaged. each other. The first electric machine 14 is then controlled so that a synchronous speed is achieved between the side shaft 18 and the first gear pair 60, i.e. a synchronous speed is achieved between the first gear 64 and the side shaft 18. Then the first gear 64 is coupled to the side shaft 18. by means of the first coupling element 84. The first and the second electric machine 14, 16 are then controlled, so that a torqueless state is achieved between the side shaft 18 and the fourth gear 82, after which the fourth coupling element 90 is displaced, so that the fourth gear 82 and thus the fourth gear pair 78 is disengaged from the side shaft 18. Finally, the second electric machine 16 is controlled so that a synchronous speed is achieved in the second planetary gear 12, after which the second planet gear holder 51 and the second sun gear 32 are connected by means of the second clutch gear. unit 58. Vehicle 1 is now propelled by a second gear.
To shift from a second to a third gear, the first electric machine 14 and the second electric machine 16 are controlled so that torque balance 5. is established in the first planetary gear 10. Then the first clutch unit 56 is displaced, so that the first planetary gear carrier 50 and the first sun gear 26 is disengaged from each other. The second electric machine 16 is then controlled so that a synchronous speed is achieved between the side shaft 18 and the second gear pair 66, the viii saga said that a synchronous speed is achieved between the second gear 70 and the side shaft 18. Then the second gear 70 is engaged to the side shaft 18 by means of the second coupling element 86. The first and the second electric machine 14, 16 are then controlled, so that a torqueless state is created between the side shaft 18 and the first gear 64, after which the first coupling element 84 is displaced, so that the first the gear 64 and thus the first gear pair 60 are disengaged from the side shaft 18. Finally, the first electric machine 14 is controlled so that a synchronous speed is achieved in the first planetary gear 10, after which the first planet gear carrier 50 and the first sun gear 26 are connected by the first coupling 56. Vehicle 1 is now propelled by a third gear.
To shift from a third gear to a fourth gear, the first electric machine 14 and the second electric machine 16 are controlled so that torque balance is achieved in the second planetary gear 12. Then the second clutch unit 58 is displaced, so that the second planetary gear holder 51 and the second the sun gear 32 is disengaged from each other. The first electric machine 14 is then controlled so that a synchronous speed is achieved between the side shaft 18 and the third gear pair 72, the viii saga so that a synchronous speed is achieved between the third gear 76 and the side shaft 18. Then the third gear 76 is coupled to the side shaft 18 by means of the third clutch element 88. The first and the second electric machine 14, 16 are then controlled, so that a torqueless state is created between the side shaft 18 and the second gear 70, after which the second clutch element 86 is displaced, so that the second gear 70 and thus the second gear pair 66 is disengaged from the side shaft 18. Finally, the second electric machine 16 is controlled so that a synchronous speed is achieved in the second planetary gear 12, after which the second planet gear carrier 51 and the second sun gear 32 are connected by means of the second clutch unit 58. The vehicle 1 is now propelled with a fourth gear.
To shift from a fourth to a sixth gear, the first and second electric machines 14, 16 are controlled so that torque balance is achieved in the second planetary gear 12. Then the second clutch unit 58 is shifted so that the second planetary gear holder 51 and the second the sun gear 32 is disengaged from each other. Then the second electric machine 16 is controlled, so that a synchronous speed is achieved between the side shaft 18 and the second or the fourth pair of gears 66, 78. Then the second or the fourth gear 70, 82 is coupled to the side shaft 18 18 by means of the second or the fourth coupling element 86, 90. Thereafter, the first and second electric machines 14, 16 are controlled so that a torqueless state is created between the side shaft 18 and the third gear 76, after which the third clutch member 88 is displaced, so that the third gear 76 and thus the third gear pair 72 is disengaged from the side shaft 18. The first electric machine 14 is then controlled so as to provide a synchronous speed between the first main shaft 34 and the output shaft 20, after which the clutch mechanism 96 is controlled to interconnect the first main shaft 34 and the output shaft 20. Vi The first and second electric machines 14, 16 are controlled so that a torqueless state a is provided between the side shaft 18 and the second or fourth gear pair 66, 78, which were previously coupled, after which the second or fourth coupling element 86, 90 is displaced, so that the second or fourth gear pair 66, 78 is disengaged from the side shaft 18. Then the second electric machine 16 is controlled, so that a torque-free state is achieved between the fifth gear pair 21 and the side shaft 18. When a torque-free state has arisen, the fifth coupling element 93 is disengaged and the fifth gear pair 21 is disengaged from the side shaft 18. Finally, the second electric machine 16 is controlled. , so that a synchronous speed is achieved in the second planetary gear 12, after which the second planetary gear holder 51 and the second sun gear 32 are interconnected by means of the second coupling unit 58.
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 pair of gears connected to the first main shaft 34 and below the first planetary shaft 10 and G2 is constituted by at least one pair of gears connected to the second main shaft 36 and thus the second planetary shaft 12. These gear pairs G1, G2 are awn 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 consist of one or more gear pairs.
In the following, embodiments for controlling the hybrid driveline 3 are described. The first planet gear carrier 50 and the first sun gear 26 are connected by means of the first clutch unit 56. Furthermore, the second planet wheel holder 51 and the second sun gear 32 are also connected by means of the second clutch unit 58. The clutch unit 106 is open and the internal combustion engine 4 is thus disengaged and the hybrid driveline 3 is driven by the first and second electric machines 14, 16. Preferably, at least one gear pair G3 connected to the side shaft 18 and the output shaft 20 is engaged and loaded on the side shaft 18, from the first and the second electric machine 14, 16, respectively, is transmitted to the output shaft via the side shaft 18 and the gear pair G3.
According to one embodiment, an upshift from one gear to another is accomplished by controlling the hybrid driveline 3 to disengage the second planet gear carrier 51 and the second sun gear 32. This is accomplished by controlling the first and second electric machines 14, 16, so that torque balance arises in the second planetary gear 12. Then 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.
Furthermore, the first electric machine 14 is controlled so that a synchronous speed is achieved between the side shaft 18 and a gear pair G1 connected to the first planetary shaft, after which the gear pair G1 connected to the first planetary shaft 10 is connected to the side shaft 18. The first and second electric machines 14, 16 is then controlled so that a torqueless state is achieved between the side shaft 18 and a gear pair G2 connected to the second planetary shaft 12, after which the gear pair G2 connected to the second planetary shaft 12 is disengaged from the side shaft 18. Thereafter the second electric machine is controlled 16, so that a synchronous speed is achieved between the second planet gear holder 51 and the second sun gear 32, after which the second planet wheel holder 51 and the second sun wheel 32 are connected by means of the second coupling unit 58.
According to one embodiment, an upshift from one gear to another is effected by further controlling the hybrid driveline 3 to disengage the first planet gear carrier 50 and the first sun gear 26 from each other. This is accomplished by controlling the first electric machine 14 and the second electric machine 16 so that torque balance is achieved in the first planetary gear 10. Thereafter, the first clutch assembly 56 is displaced so that the first planetary gear carrier 50 and the first sun gear 26 are disengaged from each other. .
Furthermore, the second electric machine 16 is controlled so that a synchronous speed is achieved between the side shaft 18 and a gear pair G2 connected to the second planetary shaft 12. The gear pair G2 connected to the second planetary shaft is then connected to the side shaft 18. The first and second electric machines 14, 16 are then controlled so that a torqueless state is created between the side shaft 18 and a pair of gears G1 connected to the first planetary gear. The first pair of gears 10 connected to the first pair of planetary gears 10 are then disengaged from the side shaft 18. Then the first electric machine 14 is controlled so that a synchronous speed is achieved between the first planet gears 50 and the first sun gear 26, after which the first planet gears 50 and the first gears 26 coupling unit 56.
According to a further embodiment, an upshift from one gear to another is achieved by further controlling the hybrid driveline 3 to disengage the second planet gear holder 51 and the second sun gear 32. This is achieved by controlling the first and the second electric machine 14, 16, so that torque balance then arises in the second planetary gear 12. Then 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.
Thereafter, the second electric machine 16 is controlled, so that a synchronous speed is achieved between the side shaft 18 and a gear pair G2 connected to the second planetary shaft 12. Then the gear pair G2 connected to the second planetary shaft 12 is connected to the side shaft 18. Then the first and the second electric machine 14, 16 are controlled, so that a torqueless state is achieved between the side shaft 18 and a gear pair G1 connected to the first planetary gear, the gear pair G1 connected to the first planetary gear 10 is disengaged from the side shaft 18.
The first electric machine 14 is then controlled so that a synchronous speed is achieved between the first main shaft 34 and the output shaft 20, after which the coupling mechanism 96 is controlled so as to interconnect the first main shaft 34 and the output shaft 20. Furthermore, the first and the second electric machine 14, 16, so that a torque-free state is created between the side shaft 18 and the gear pair G2 connected to the second planetary shaft 12, which was previously connected, after which the gear pair G2 connected to the second planetary shaft 12 is disengaged from the side shaft 18. The second electric the machine 16 is then controlled so that a torqueless state is achieved between the gear pair G3 connected to the side shaft 18 and the output shaft 20 and the side shaft 18. When a torqueless state has arisen, the gear pair G3 connected to the side shaft 18 is finally disengaged with the side shaft 18 and the output shaft 20. the second electric machine 16 is controlled, so that a synchronous speed is achieved between them n the second planet gear holder 51 and the second sun gear 32, after which the second planet wheel holder 51 and the second sun wheel 32 are interconnected by means of the second coupling unit 58. Fig. 4 shows a flow chart of a method for controlling a hybrid driveline 3 in electric operation. The hybrid driveline 3 comprises an internal combustion engine 4 and a gearbox 2, which in turn comprises 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 shaft 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.
According to one embodiment, the method comprises the steps of: ensuring that the internal combustion engine 4 is disengaged by means of a coupling device 106; disengaging rotatable components 28, 32, 51 of the second planetary gear 12 from each other; coupling a gear pair G1, 60, 72 connected to the first planetary gear 10; d) disengage a gear pair G2, 66, 78 connected to the second planetary gear 12; and e) interconnecting two rotatable components 28, 32, 51 of the second planetary gear 12 with each other.
Lamply, the internal combustion engine 4 is disengaged from the gearbox by means of the coupling device 106 arranged between a shaft 97 emanating from the internal combustion engine 4 and the shaft 8 entering the gearbox 2.
The rotatable components 28, 32, 51 of the second planetary gear 12 comprise a second planet gear holder 51 and a second sun gear 32, whereby they are disengaged in step b) by controlling the first and the second electric machine 14, 16, so that torque balance arises. more in the second planetary gear 12. Then a 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 gear pair G1, 60, 72 connected to the first planetary gear 10 is suitably connected in step c) by controlling the first electric machine 14 so that a synchronous speed is achieved between a side shaft 18 and the gear pair G1 connected to the first planetary gear 10. 60, 72, after which the gear pair G1, 60, 72 connected to the first planetary gear 10 is coupled to the side shaft 18. The gear pair G2, 66, 78 connected to the second planetary gear 12 is decoupled in step d) by the first and the second the electric machine 14, 16 is controlled, so that a torqueless state is achieved between the side shaft 18 and the gear pair G2, 66, 78 connected to the second planetary shaft 12, after which the gear pair G2, 66, 78 connected to the second planetary shaft 12 is disengaged from the side shaft. 18.
The rotatable components 28, 32, 51 of the second planetary gear 12 comprise a second planetary gear holder 51 and a second sun gear 32, they being interconnected in step e) by controlling the second electric machine 16 so that a synchronous speed is achieved between the second the planet gear holder 51 and the second sun gear 32, after which the second planet wheel holder 51 and the second sun wheel 32 are connected by means of the second coupling unit 58.
According to another embodiment, the method in addition to steps a) -e) above also comprises the steps of: f) disengaging rotatable components 22, 26, 50 of the first planetary gear 10 from each other; coupling a gear pair G2, 66, 78 connected to the second planetary gear 12; disengage a gear pair G1, 60, 72 connected to the first planetary gear 10; and interconnecting two rotatable components 22, 26, 50 of the first planetary gear 10 with each other.
The two rotatable components 22, 26, 50 of the first planetary gear 10 comprise a first sun gear 26 and a first planet gear carrier 50, they being disengaged in step f) by controlling the first and the second electric machine 14, 16 so that torque balance arises in the first planetary gear 10. Then a first coupling unit 56 is displaced, said. that the first planet gear holder 50 and the first sun gear 26 are disengaged from each other.
The gear pair G2 connected to the second planetary gear 12 is suitably coupled. 66, 78 in step g) by controlling the second electric machine 16 so that a synchronous speed is achieved between the side shaft 18 and the gear pair G2, 66, 78 connected to the second planetary shaft 12, after which the gear pair G2 connected to the second planetary shaft 12 , 66, 78 is coupled to the side shaft 18.
The gear pair G1, 60, 72 connected to the first planetary shaft 10 is freely disengaged in step h) by controlling the first and second electric machines 14, 16, so that a momentary state is achieved between the side shaft 18 and the one with the first the gear pair G1, 60, 72 connected to the planetary shaft, after which the gear pair G1, 60, 72 connected to the first planetary gear 10 is disengaged from the side shaft 18.
Lamply, the two rotatable components 22, 26, 50 of the first planetary gear comprise a first sun gear 26 and a first planet gear shall be 50, they being interconnected in the step by controlling the first electric machine 14 so as to provide a synchronous speed between the the first planet gear holder 50 and the first sun gear 26, after which the first planet wheel holder 50 and the first sun wheel 26 are connected by means of the first coupling unit 58.
According to a further embodiment, the method in addition to steps a) -e) above also comprises the steps of: repeating step b); k) coupling a gear pair G2, 66, 78 connected to the second planetary gear 12; 1) disengage a gear pair G1, 60, 72 connected to the first planetary gear 10; m) connecting the first planetary shaft 10 to the output shaft 20 by means of a clutch mechanism 96; n); repeat step d); o) disengage a gear pair G3, 21 arranged between the side shaft 18 and the output shaft 20; and p) repeat step e).
The gear pair G2 connected to the second planetary gear 12 is suitably coupled. 66, 78 in step k) by controlling the second electric machine 16 so that a synchronous speed is achieved between the side shaft 18 and the gear pair G2, 66, 78 connected to the second planetary shaft 12, after which the gear pair connected to the second planetary shaft 12 the gear pair G2, 66, 78 is coupled to the side shaft 18.
The gear pair G1, 60, 72 connected to the first planetary gear 10 is decoupled in step 1) by controlling the first and the second electric machine 14, 16, so that a momentless state is created between the side shaft 18 and the one with the first planetary gear. The pair of gears G1, 60, 72 is connected, after which the pair of gears G1, 60, 72 connected to the first planetary shaft 10 is disconnected from the side shaft 18. In this case, the first planetary gear shaft 10 is connected to the output shaft 20 in step m) by the machine 14 is controlled so that a synchronous speed is achieved between a first main shaft 34 connected to the first planetary shaft shaft 10 and the output shaft 20, after which the clutch mechanism 96 is controlled so as to interconnect the first main shaft 34 and the output shaft 20.
Preferably, the gear pair G3, 211 arranged between the side shaft 18 and the output shaft 20 is disengaged by step o) by controlling the second electric machine 16, so that a torqueless state is created between the side shaft 18 and the pair of shaft shafts G3 arranged between the output shaft 18 and the output shaft 20. , 21, after which the torque pair G3, 21 arranged between the side shaft 18 and the output shaft 20 is disengaged from the side shaft 18.
Fig. 5 shows a flow chart of a method for controlling a hybrid driveline 3 in electric operation. The hybrid driveline 3 comprises an internal combustion engine 4 and a gearbox 2, which in turn comprises 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 shaft 10; a first electric machine 14 coupled to the first planetary gearbox 10; a second electrical machine 16, which is coupled to the second planetary gear shaft 12; at least one gear pair G1, 60, 72 connected to the first planetary gear shaft 10 and the output shaft 20 and at least one gear pair G2, 66, 78 connected to the second planetary gear shaft 12 and the output shaft 20.
The method comprises the steps of: a) ensuring that the internal combustion engine 4 is disengaged by means of a coupling device 106; f) disengaging rotatable components 22, 26, 50 of the first planetary gear 10 from each other; coupling a gear pair G2, 66, 78 connected to the second planetary gear shaft 12; disengage a gear pair G1, 60, 72 connected to the first planetary gear shaft 10; and interconnecting two rotatable components 22, 26, 50 of the first planetary gear shaft 10 with each other.
Preferably, the two rotatable components 22, 26, 50 of the first planetary gear shaft 10 comprise a first sun gear 26 and a first planet gear carrier 50, they being disengaged in step 1) by controlling the first and second electric machines 14, 16 so that torque balance occurs in the first planetary gear 10. Then a first clutch unit 56 is displaced, so that the first planetary gear carrier 50 and the first sun gear 26 are disengaged from each other.
The gear pair G2, 66, 78 connected to the second planetary shaft 12 is coupled in step g) by controlling the second electric machine 16 so that a synchronous speed is achieved between the side shaft 18 and the gear pair G2 connected to the second planetary shaft 12. 66, 78, after which the gear pair G2, 66, 78 connected to the second planetary shaft 12 is coupled to the side shaft 18.
The gear pair G1, 60, 72 connected to the first planetary gear 10 is freely disengaged in step h) by controlling the first and second electric machines 14, 16, so that a torqueless state is achieved between the side shaft 18 and the one connected to the first planetary gear 10. the gear pair G1, 60, 72, after which the gear pair G1, 60, 72 connected to the first planetary gear 10 is disengaged from the side shaft 18.
Lamply, the two rotatable components 22, 26, 50 of the first planetary gear 10 comprise a first sun gear 26 and a first planet gear carrier 50, they being interconnected in step i) by controlling the first electric machine 14 so as to provide a visible speed. between the first planet gear holder 50 and the first sun gear 26, after which the first planet wheel holder 50 and the first sun wheel 26 are connected by means of the first coupling unit 58.
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 another of a computer 53 weldable medium. 1 the scope of the invention combi-

权利要求:
Claims (31)
[1]
A hybrid driveline comprising an internal combustion engine (4) and a gearbox (2) having an input shaft (8) and an output shaft (20); a first planetary shaft (10), as coupled to the input shaft (8); a second planetary gear (12) coupled to the first planetary gear (10); a first electric machine (14), which is connected 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 shaft (10) and the output shaft (20); and at least one gear pair (G2, 66, 78) connected to the second planetary gear shaft (12) and the output shaft (20), characterized in that a coupling device (106) is arranged between the internal combustion engine (4) and the gear shaft (2), so that the internal combustion engine (4) can be disengaged from the gearbox (2).
[2]
Hybrid driveline according to Claim 1, characterized in that the coupling device (106) is arranged between a shaft (97) emanating from the internal combustion engine (4) and a shaft (8) entering the shaft shaft (2).
[3]
Hybrid driveline according to claim 1 or 2, characterized in that a first main shaft (34) is coupled to the first planetary shaft (10) and that a second main shaft (36) is coupled to the second planetary shaft (12).
[4]
A hybrid driveline according to any preceding bay, characterized in that a side shaft (18) is arranged between the respective first and second planetary shafts (10, 12) and the output shaft (20);
[5]
Hybrid driveline according to claim 4, characterized in that the at least one gear pair (G1, 60, 72) connected to the first planetary gear shaft (10) and the at least one gear pair (G2, 66, 78) connected to the second planetary gear shaft (12) also connected to the side shaft 18.
[6]
A hybrid driveline according to any one of claims 3-5, characterized in that a first planet gear holder (50) of the first planet gear (10) is connected to a second sun gear (32) of the second planet gear (12); that a first sun gear (26) of the first planetary shaft (10) is connected to the first major shaft (34); and 28 that a second planet gear holder (51) of the second planetary shaft (12) is connected to the second major shaft (36).
[7]
Hybrid driveline according to claim 6, characterized in that the input shaft (8) is connected to the first planetary gear carrier (50).
[8]
Hybrid driveline according to any one of the seas 3 - 7, characterized in that a coupling mechanism (96) is arranged between the first main shaft (34) and the output shaft (20).
[9]
Hybrid driveline according to any preceding hay, characterized in that the side shaft (18) is connected to the output shaft (20) via a fifth gear pair (G3, 21).
[10]
A hybrid driveline according to any preceding hay, characterized in that a first rotor (24) of the first electric machine (14) is connected to a first ring gear (22) of the first planetary gear (10); and that a second rotor (30) of the second electric machine (16) is connected to a second ring gear (28) of the second planetary gear (12).
[11]
Hybrid driveline according to any one of hay 6-10, characterized in that a first coupling unit (56) is arranged to releasably connect the first sun gear (26) to the first planet gear holder (50); and that a second coupling unit (58) is arranged to releasably connect the second sun gear (32) to the second planet gear holder (51).
[12]
Vehicle comprising a hybrid driveline according to any one of the oceans 1-11.
[13]
A method of controlling a hybrid driveline (3), comprising an internal combustion engine (4) and a gearbox (2) having 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 gear pair (G1, 60, 72) connected to the first planetary shaft 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), characterized by the steps of: 29 1. ensuring that the internal combustion engine (4) is disengaged by means of a coupling device (106); 2. disengage rotatable components (28, 32, 51) of the second planetary gear (12) from each other; 3. connect a pair of wheels (G1, 60, 72) connected to the first planetary gear shaft (10); d) disengage a pair of gears (G2, 66, 78) connected to the second planetary gear shaft (12); and e) interconnecting two rotatable components (28, 32, 51) of the second planetary shaft (12) with each other;
[14]
A method according to claim 13, characterized in that in step b) the rotatable components (28, 32, 51) of the second planetary gear (12) comprise a second planet gear holder (51) and a second sun gear (32), wherein the the first and / or the second electric machine (14, 16) is controlled, so that torque balance arises in the second planetary gear (12), after which a second clutch unit (58) is displaced, so that the second planetary gear carrier (51) and the second sun gear (32) ) are disconnected from each other.
[15]
Method according to claim 13 or 14, characterized in that in step c) the first electric machine (14) is controlled, so that a synchronous speed is achieved between a side shaft (18) and the pair of gears (G1 connected to the first planetary gear shaft (10). , 60, 72), after which the gear pair (G1, 60, 72) connected to the first planetary gear (10) is coupled to the side axle (18).
[16]
A method according to any one of claims 13-15, characterized in that in step d) the second electric machine (16) is controlled, so that a torque-free state is achieved between the side shaft (18) and the pair of gears connected to the second planetary gear shaft (12). (G2, 66, 78) after which the pair of gear shafts (G2, 66, 78) connected to the second planetary gear shaft (12) are disengaged from the side shaft (18).
[17]
A method according to any one of claims 13-16, characterized in that in step e) the rotatable components (28, 32, 51) of the second planetary gear (12) comprise a second planetary gear holder (51) and a second sun gear (32), wherein the second electric machine (16) is controlled, so that a synchronous speed is achieved between the second planet wheel holder (51) and the second sun gear (32), after which the second planet wheel holder (51) and the second sun wheel (32) are connected by means of the second coupling unit. (58).
[18]
A method according to any one of claims 13-17, characterized by the further steps of: 6. disengaging rotatable components (22, 26, 50) of the first planetary gear (10) from each other; 7. coupling a gear pair (G2, 66, 78) connected to the second planetary gear (12); 8. disengage a gear pair (G1, 60, 72) connected to the first planetary gear (10); and i) interconnecting two rotatable components (22, 26, 50) of the first planetary gear (10) with each other.
[19]
A method according to claim 18, characterized in that in step f) the two rotatable components (22, 26, 50) of the first planetary gear (10) comprise a first sun gear (26) and a first planet gear holder (50), the first and / or the second electric machine (14, 16) is controlled so that torque balance occurs in the first planetary gear (10), after which a first clutch unit (56) is displaced, so that the first planetary gear carrier (50) and the first sun gear (26) disconnected from each other.
[20]
A method according to any one of claims 18-19, characterized in that in step i) the two rotatable components (22, 26, 50) of the first planetary gear (10) comprise a first sun gear (26) and a first planet gear holder ( 50), the first electric machine (14) being controlled so that a synchronous speed is achieved between the first planetary gear carrier (50) and the first sun gear (26), after which the first planetary gear carrier (50) and the first solar wheel (26) co-exist. is disconnected by means of the first coupling unit (58).
[21]
A method according to claim 13, characterized by the further steps of: 10. repeating step b); 11. coupling a pair of gears (G2, 66, 78) connected to the second planetary gear (12); 1) disengage a pair of gears (G1, 60, 72) connected to the first planetary gear (10); m) connecting the first planetary shaft (10) to the output shaft 20 by means of a coupling mechanism (96); n); repeat step d); 15. disengage a gear pair (G3, 21) arranged between the side shaft (18) and the output shaft (20); and 16. repeat step e).
[22]
Method according to any one of claims 18-21, characterized in that in steps g) and k) the second electric machine (16) is controlled, so that a synchronous speed is achieved between a side shaft 31 (18) and that with the second planetary shaft ( 12) connected the gear pair (G2, 66, 78), after which the gear pair (G2, 66, 78) connected to the second planetary gear (12) is connected to the side shaft (18).
[23]
Method according to any one of claims 18-22, characterized in that in steps h) and 1) the first electric machine (14) is controlled, so that a torque-free state is achieved between the side shaft (18) and that with the first planetary shaft ( 10) connected the gear pair (GI, 60, 72), after which the gear pair (GI, 60, 72) connected to the first planetary gear (10) is disengaged from the side shaft (18).
[24]
Method according to any one of claims 21-23, characterized in that in step m) the first electric machine (14) is controlled, so that a synchronous speed is achieved between a first main shaft (34) connected to the first planetary shaft (10) and the output shaft (20), after which the clutch mechanism (96) is controlled so as to interconnect the first main shaft (34) and the output shaft (20).
[25]
A method of controlling a hybrid driveline (3), comprising an internal combustion engine (4) and a gearbox (2) having 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), 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 gear (12); at least one gear pair (G1, 60, 72) connected to the first planetary gear 10 and the output shaft (20) and 5. at least one gear pair (G2, 66, 78) connected to the second planetary gear (12) and the output shaft (20) ), characterized by the steps of: a) ensuring that the internal combustion engine (4) is disengaged by means of a coupling device (106); f) disengaging rotatable components (22, 26, 50) of the first planetary gear (10) from each other; 7. coupling a gear pair (G2, 66, 78) connected to the second planetary gear (12); 8. disengage a gear pair (G1, 60, 72) connected to the first planetary gear (10); and 9. interconnecting two rotatable components (22, 26, 50) of the first planetary gear (10) 30 with each other.
[26]
A method according to claim 25, characterized in that in step f) the two rotatable components (22, 26, 50) of the first planetary gear (10) comprise a first sun gear (26) and a first planet gear holder (50), the first and / or the second electric machine (14, 32 16) is controlled so that torque balance arises in the first planetary gear (10), after which a first clutch unit (56) is displaced, so that the first planetary gear carrier (50) and the first sun gear (26) ) are disconnected from each other.
[27]
A method according to any one of claims 25-26, characterized in that in step i) the two rotatable components (22, 26, 50) of the first planetary gear (10) comprise a first sun gear (26) and a first planet gear holder (50) , the first electric machine (14) being controlled so that a synchronous speed is achieved between the first planetary gear carrier (50) and the first solar wheel (26), after which the first planetary gear carrier (50) and the first solar wheel (26) are connected by means of the first coupling unit (58).
[28]
Method according to any one of claims 25-27, characterized in that in step g) the second electrical machine (16) is controlled, so that a synchronous speed is achieved between a side shaft (18) and the gear pair connected to the second planetary shaft (12). (G2, 66, 78), after which the gear pair (G2, 66, 78) connected to the second planetary shaft (12) is coupled to the side shaft (18).
[29]
A method according to any one of claims 25-28, characterized in that in step h) the first electric machine (14) is controlled, so that a torqueless state is achieved between the side shaft (18) and the gear pair (10) connected to the first planetary shaft (10). G1, 60, 72), after which the gear pair (G1, 60, 72) connected to the first planetary shaft (10) is disengaged from the side shaft (18).
[30]
Computer program (P) for starting an internal combustion engine (4), 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 13-29.
[31]
A computer program product comprising a program code stored on a computer readable medium for performing the method steps of any of claims 13-29, when said program code is read on an electronic control unit (48) or another computer (53) connected to it. - tronic control unit (48). i, 99 I. `6! d 16 12 28 36 G2, 66, 78 58 Ii

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WO2014158078A1|2014-10-02|

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SE1450308A1|2014-09-28|

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CN105246727A|2016-01-13|

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RU2628618C2|2017-08-21|

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EP2978622A1|2016-02-03|

CN105246726B|2017-10-20|

KR101725882B1|2017-04-11|

RU2637052C2|2017-11-29|

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法律状态:

优先权:

申请号 | 申请日 | 专利标题

SE1350392A|SE1350392A1|2013-03-27|2013-03-27|Gearbox, vehicles with such gearbox, method for controlling such gearbox, computer program for controlling such gearbox, and a computer software product comprising program code|

SE1350394A|SE1350394A1|2013-03-27|2013-03-27|Gearbox, vehicles with such gearbox, method for controlling such gearbox, computer program for controlling such gearbox, and a computer software product comprising program code|

SE1350393A|SE1350393A1|2013-03-27|2013-03-27|Gearbox, vehicles with such gearbox, method for controlling such gearbox, computer program for controlling such gearbox, and a computer software product comprising program code|

SE1450309A|SE538194C2|2013-03-27|2014-03-20|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|SE1450309A| SE538194C2|2013-03-27|2014-03-20|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|

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