• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A method for control of a gearbox, installed in a motor vehicle (1): The method effects a downshift of the gearbox (20) from a first gear (G1), for which the acceleration α of the vehicle (1) is negative, to a second gear (G2), for which the acceleration α is positive or substantially equal to nil. The downshift involves at least one intermediate gear step between the first gear (G1) and the second gear (G2), using an engine speed ωG1 in the first gear (G1) as an input parameter when effecting the downshift. Also a system, a motor vehicle, a computer program and a computer program product for performing the method are disclosed.
    公开号:SE1050957A1
    申请号:SE1050957
    申请日:2010-09-14
    公开日:2011-03-15
    发明作者:Fredrik Swartling；Mikael Waagberg
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    the engine 10, such as engine speed and engine number, from the engine 10 to the ECU via, for example, a CAN bus (Controller Area Network) in the motor vehicle 1.
    In conventional gear systems, the control unit 110 uses tabled engine speed limits, also called gear points, which indicate the engine speed at which a downshift or upshift is to be effected in the gearbox 20. This means that when the speed of the motor 10 passes an engine speed for one gear, the gear system shifts. The shift points can therefore be understood as including information partly about when a downshift or upshift is to take place and partly about the number of shift steps to be performed at the said downshift or upshift. It is common for each change point to indicate one to three change steps, but more change steps are possible.
    Figure 2 shows an example of a number of tabulated shift points forming lines SP1-SP6 in a graph where the x-axis represents motor torque and the y-axis speed of the motor 10 in the unit revolutions per minute (revolutions per minute, rpm). As long as a current motor speed is between the shift lines SP1 and SP4, no change takes place, but if the current motor speed passes an upshift line, SP1-SP3, a upshift is initiated, and correspondingly a downshift is initiated if the current engine speed goes below a downshift line, SP4 -SP6.
    The number of upshift and downshift steps for each of the lines SP1-SP6 in Figure 2 is given in Table 1 below. For example, if the engine speed goes over line SP1, an upshift occurs with one shift step and if the engine speed goes below line SP5, a downshift occurs with two shift steps.
    SP1 Upshift speed for 1 step up SP2 Upshift speed for 2 steps up SP3 Upshift speed for 3 steps up SP4 Shift speed for 1 step down SP5 Shift speed for 2 steps down SP6 Shift speed for 3 steps down Table 1: Number of shift steps for downshift and upshift SP6 of change points affects i.a. driving characteristics, acceleration, comfort and fuel consumption of the motor vehicle l, so these must be carefully calibrated by the motor vehicle manufacturers. The calibration is usually done so that different shifting strategies are tested in a field-based manner during different driving situations, such as at different throttles, road inclines and train weights.
    The test results must then be carefully analyzed to determine suitable shift points, which is very time consuming as there are an almost infinite number of combinations of different drivelines, driving situations and vehicle weights.
    Brief description of the invention An object of the invention is to provide a method for controlling a gearbox which completely or partially solves the problems with known technology. Another object of the present invention is to provide an alternative method of controlling a gearbox.
    According to an aspect of the invention, the above-mentioned object is achieved with a method for controlling a gearbox, which gearbox is arranged to be arranged in a motor vehicle, said method providing a downshifting of said gearbox from a first gear, for which the acceleration a of said motor vehicle is negative, to a second gear, for which the acceleration a is positive or substantially equal to zero, which downshift takes place by means of at least one intermediate gear step between said first and second gear, a maximum engine speed in each intermediate gear step being an equal, or a higher engine speed than a maximum engine speed in a previous intermediate gear step.
    Various embodiments of the above method are defined in the independent claims appended to claim 1.
    The invention further relates to a computer program comprising program code, which when said program code is executed in a computer causes said computer to perform the method for controlling a gearbox above. In addition, the invention relates to a computer program product belonging to said computer program.
    According to another aspect of the invention, the above-mentioned object is achieved with a system for controlling a gearbox, which system comprises at least one control unit arranged for controlling a gearbox in a motor vehicle, the system being arranged to effect a downshift of said gearbox from a first gearbox. , for which the acceleration a of said motor vehicle is negative, to a second gear, for which the acceleration a is positive or equal to zero, which downshifting takes place by means of at least one intermediate gear step between said first and second gear, a maximum engine speed in each intermediate gear step being a as high, or a higher engine speed than a maximum engine speed in a previous intermediate gear step.
    The system according to the invention can also be modified in accordance with the various embodiments of the method above. Furthermore, the invention relates to a motor vehicle comprising at least one system as above.
    An advantage of the invention is improved reversing since the speed of the motor vehicle at the entrance to a hill is used. Thus, fuel consumption can be reduced and the number of shifts reduced. Furthermore, the driver of the motor vehicle will experience it as force fi as a maximum engine speed in each intermediate gear step is an equal, or a higher engine speed than a maximum engine speed in a previous intermediate gear step up the hill and thereby utilize the engine's maximum power effectively.
    Additional advantages and applications of a method and system according to the invention will become apparent from the following detailed description.
    BRIEF DESCRIPTION OF THE DRAWINGS The present invention is described with reference to the accompanying figures, in which: Figure 1 schematically shows a part of a driveline for a motor vehicle; figure 2 shows a graph of down and upshift lines; Figure 3 shows a diagram of a embodiment of an embodiment of the invention; figure 4 shows an example of downshifting from a first gear G1 to a second gear G2 according to the invention; and - figure 5 shows a control unit to be part of a system according to the invention.
    Detailed Description of the Invention Conventional shift systems described above select gears according to prevailing driving conditions, such shift systems using fixed shift points as shown in Figure 2. For example, if the motor vehicle 1 is driving uphill and a current gear is not suitable because motor vehicle 1 loses speed uphill, the gearing system select a new gear unit for driving the motor vehicle 1.
    A problem in this case is to choose a gear which gives low fuel consumption and which also means that the engine 10 operates at engine speed which gives sufficient power for the motor vehicle 1 to be experienced as power fi all through the entire uphill slope of the driver. By force fi illt is meant here that the engine speed is close to the engine's 10 maximum power speed.
    Since motor vehicle 1 can have different vehicle specifications, such as gearbox transmission, rear axle gear ratio and wheel radius, this means that the same vehicle speed can be achieved at different engine speeds for motor vehicles 1 with different vehicle specifications. This in turn means that the use of fixed shift points becomes problematic as these may fit some vehicle specifications, but not others. The same problem can also occur if a motor vehicle 1, for example, changes from one wheel radius to another and thus receives a changed total gear ratio.
    When a motor vehicle 1 drives up a hill, a situation may therefore arise that a downshift takes place too early, or alternatively too late, due to that the fixed changeover points are not suitable for a particular vehicle specification. A premature downshift means that the motor vehicle 1 can be perceived as "nervous", i.e. shifts too often and is unstable, while fuel consumption increases. A late downshift, on the other hand, means that the power of the engine 10 is not used optimally because the motor vehicle 1 loses more speed than necessary.
    The present invention therefore relates to a method which realizes a shifting strategy for a gearbox 20, which completely or partially obviates the disadvantages of the prior art. Preferably, the gearbox 20 is of the type included in an automated shifting system, which is controlled by a control unit 110 (ECU). In such a system, shifts are performed automatically by the control unit 110, but it is also common for the driver to perform manual shifting in such an automated shifting system, so-called manual shift in automatic mode (automatic mode). Furthermore, the gearbox 20 comprises a number of gears, for example 12 forward gears and one or more reverse gears.
    The idea of a method according to the invention is that a downshift strategy is applied where the shifting system shifts from a first gear G1 for which the acceleration a of the motor vehicle 1 is negative (power deficit gear), to a second lower gear G2 for which the acceleration a is positive or equal to zero of the motor vehicle 1, via one or fl your intermediate stages. In addition, according to the present invention, the highest engine speed in each intermediate gear step shall be equal to or higher than the engine speed in a previous intermediate gear step. The engine speed for each intermediate gear step is, for example, within the engine speed range 1000-2500 rpm for e.g. trucks and buses.
    The terms "negative" or "positive or equal to zero" in this description are to be understood to mean substantially "negative" and substantially "positive or equal to zero", respectively.
    The reason is that the acceleration a of the motor vehicle 1 can momentarily assume a value which is "positive or equal to zero" for the first gear G1, but averaged over a period of time, the acceleration a is nevertheless negative. Correspondingly, this applies to the acceleration a of the motor vehicle 1 when the motor vehicle 1 is propelled with the second gear G2 engaged, as will be appreciated by those skilled in the art.
    In this description, a "power deficit gear" is further understood to mean a gear with such a gear ratio that the motor vehicle 1 does not have a driving force sufficient to maintain a constant speed on this gear. By a "power balance gear" is meant the highest gear with which the motor vehicle 1 can maintain a constant speed, which means that the motor vehicle 1 has a power balance. It should be noted that the negative acceleration a on the first gear G1 is due to the motor 10 not being able to supply sufficient power on the first gear G1, so a power deficit occurs.
    According to an embodiment of the invention, the maximum engine speed in each intermediate gear step increases by a parameter value p1. , where (of is the highest engine speed in an intermediate gear step and (of, is the highest engine speed in the previous intermediate gear step).
    Engine speed m; in an intermediate gear step is thus a maximum engine speed that the motor vehicle 1 has had since the acceleration a became negative - ie. the highest engine speed that motor vehicle 1 has had since motor vehicle 1 went into power deficit. Said engine speed co; can be interpreted as a target speed which the shifting system strives to reach after each intermediate shifting step in the downshift according to this embodiment of the invention.
    Furthermore, the parameter value pl. is interpreted as a tolerance value because the engine speed after each shift may deviate from a simulated engine speed. In addition, the size of the tolerance value pl. varied so as to influence how quickly said engine quarter co; shall increase for example for different driving modes such as economy or power node. It should also be noted that the parameter value pi does not have to be a constant but can be a variable and assume different values for different gears.
    According to a further embodiment of the invention, the acceleration a is zero or substantially zero for the second gear G2. The acceleration a, expressed in, for example, m / sz or rpm / s, for the second gear G2 can be compared with a threshold value A to check whether the condition that it is positive or zero is met. In addition, the acceleration a can be compared against this threshold value A for a certain period of time in order to avoid instantaneous deviations from the acceleration a which could lead to an error in the comparison. The value of the acceleration a for the second gear can also be checked by comparing a calculated driving resistance with a calculated driving force to thereby determine whether the acceleration a will be greater than or equal to zero on the second gear G2.
    Regarding the intermediate gear steps in the present method, one or more intermediate gear steps may be performed between the first G1 and the second G2 gear according to an embodiment of the invention. Furthermore, the number of shift steps between the first gear G1 and an intermediate gear step, and / or between two successive intermediate gear steps, and / or between an intermediate gear step and the second gear G2 may comprise one or more of your gear steps.
    According to a preferred embodiment of the invention, each intermediate change step lasts for a longer period of time than a threshold value. The period of time how long the motor vehicle 1 can run on a certain intermediate gear can preferably be compared with a gear-specifically calibrated threshold value. This means that, according to an embodiment of the invention, if an intermediate gear is to be considered as a permissible intermediate gear between the first G1 and the second gear G2, the motor vehicle 1 be able to run on the intermediate gear for at least a period of time greater than the threshold value T. for this specific gear.
    The reason why it is not appropriate for the motor vehicle 1 to run for a short time on an intermediate gear is that the motor vehicle 1 loses a power transmission from the driveline during the execution of a gear shift and will thus lose speed during the actual gearing process. For this reason, it is preferable if such a situation can be avoided because the motor vehicle 1 can lose more speed if the shifting system chooses to shift via an intermediate gear than if the shifting system skips said intermediate gear and instead shifts down another one or fl your steps at downshifting.
    Carrying out a downshift and then driving on this gear for a too short period of time also means a comfort disturbance for the driver and any passengers, and for this reason the gearshift system can use calibrated gear-specific threshold values T. as described above. With these calibrated threshold values TI. also determines how likely it is that the shifting system skips an intermediate gear or not when calculating a downshift from the first G1 to the second G2 gear. The larger the value that a gear-specific calibrated threshold value T. assumes, the more likely it is that the shifting system skips an intermediate gear, and the smaller the value as the threshold value TI. assumes, the less likely the shifting system skips an intermediate gear. Due to the above, the threshold value T. can be used as a parameter for determining the number of shift steps in each intermediate shift step and / or for determining the number of intermediate shift steps between the first G1 and second G2 gears according to various embodiments of the invention.
    Time values for the gear-specific threshold values T. can preferably assume a value between 1-second for heavy motor vehicles 1, such as trucks and buses, depending on the behavior desired during the downshift such as e.g. downshift speed and downshift rhythm. Thus, the threshold values Tl. can be used as design parameters in performing different downshift behaviors of the shifting system because the threshold values T. will determine the number of intermediate shifts and the number of shift steps in each intermediate step as described above.
    According to another embodiment of the invention, a current intermediate gear step lasts for as long a period of time as a time period for a subsequent intermediate gear step, since the downshift will then be experienced as consistent and positive by most drivers.
    The reason is that drivers usually do not want the shifting system to make arbitrary shifts "a little now and then", which can be perceived as nervous and arbitrary by the driver. By "an equal period of time" in this context is meant that the periods of time are approximately equal in length.
    The inventors have also realized in their work of invention that an engine speed of the first gear G1 com can be used as an input parameter in determining a downshift from a first gear G1 to a second gear G2 according to a preferred embodiment of the invention.
    This engine speed (if is a speed the engine 10 has when the motor vehicle 1 is propelled with the first gear G1 engaged.
    Said engine speed (if is preferably the engine speed the motor vehicle 1 has when the motor vehicle 1 enters a state of power deficit on the first gear G1, for example at the entrance of an uphill slope. This means that it is the highest engine speed on the first gear G1 which will be said engine speed (if and this engine speed can be interpreted as an engine speed when a current driving force on the first gear G1 becomes less than a current driving resistance on the same gear. Figure 4 shows an example of said engine speed (if.
    An advantage of this embodiment is that since the shifting system is based on the engine speed the motor vehicle 1 had when it went into the hill, ie. the engine quarter the motor vehicle had when it went into a power deficit coGl, the shift points are automatically adjusted to have the same behavior for different drivelines. For this reason, calibration of gear points is not related to different engine types or drivelines according to the invention, but only for different driving nodes, e.g. economic or powerrnod. The advantage of this procedure is that time does not have to be spent on calibration with respect to different types of drivelines or engines, but focus can instead be placed on calibrating a general behavior for all types of motor vehicles 1.
    A further advantage of this embodiment is that if the driver himself shifts down manually before, or in, the hill, the shifting system will perceive the engine speed increased by the driver in the same way as if the shifting system itself had made an aggressive downshift. The shift system will consequently continue to shift aggressively up the entire hill. This allows the driver to easily control the way in which reversing is to be carried out because a high value of the engine speed for the first gear G1 (if leads to a more aggressive reversing than for a lower value of the engine speed for the first gear G1 ma.
    According to another preferred embodiment of the invention, shifting takes place in an intermediate gearing stage at a higher engine speed than an engine speed for shifting in a previous intermediate gearing step, which means that the engine speed when shifting increases for each intermediate gearing step. With this embodiment, the driver experiences the motor vehicle 1 as power fi everything and that the motor vehicle l “takes in”, for example on an uphill slope, since the motor vehicle 1 will run more on the maximum power of the engine 10 for each subsequent intermediate gear at downshift. Given that the engine speed does not exceed the engine's 10 maximum power speed (often around 1800 rpm for trucks), a higher engine speed will mean that the engine 10 gives a higher power. Therefore, the engine 10 becomes and is experienced stronger for each shift in the downshift because the motor vehicle 1 will be propelled at higher and higher engine speeds according to this embodiment of the invention.
    Figure 3 shows a fate diagram of an exemplary embodiment of a method according to the present invention. This flow is intended to be evaluated continuously by the shifting system throughout the time the motor vehicle 1 is in power deficit, which means that the shifting system evaluates whether a shifting should be performed or not based on step F1 at a predetermined frequency.
    In step F1, it is checked whether a current engine speed is a higher engine speed than a maximum engine speed that the motor vehicle 1 has had since it has been in power deficit, i.e. a <0. If so, this current engine speed is saved to a first maximum engine speed m; to be used as a reference motor speed in the shifting process.
    In step F2, a suitable minimum engine speed is selected o) Mm which must not be less than when the acceleration a is negative (ie when the motor vehicle 1 is in power deficit) i.a. depending on how fast the motor vehicle 1 loses speed, the derivatives of the road slope and which driving mode the motor vehicle 1 uses. For example, a lower minimum engine speed (mM) can be selected in case the derivative of the road slope is decreasing, i.e. when the motor vehicle 1 approaches the crest of a hill.
    Minimum engine speed a) M1. is preferably also selected so that a current engine speed never falls below the maximum torque curve of the motor 10 in order for the motor 10 to deliver sufficient power throughout the downshift process and to avoid uncomfortable vibrations from the driveline.
    In step P3, a suitable maximum engine speed coMax defined as an engine speed is selected, which must not be exceeded during the shifting procedure when a <0. This maximum engine speed mMax can, for example, be related to fuel consumption and / or desired engine power. For heavy motor vehicles l, this maximum engine speed (nMax eg can be 1600 rpm if the fuel consumption should not be too high or 2100 rpm if it is maximum engine power that is prioritized. It is therefore understood that said maximum engine speed wMax may depend on the driving node with which the motor vehicle 1 is performed.
    In step F4, the engine speed is limited; so that it assumes a value within the range defined by the minimum motor speed comMm and the maximum motor speed mMax. Sold can m; set to the minimum motor speed wMín (Obj = wMin) if to; assumes a value below the interval, and to the maximum motor speed wMax (mf. = u)) of 0); assumes a value over the range.
    Max In step P5, the second gear G2 is searched by calculating which of the possible available lower gears the motor vehicle 1 must shift to in order for the acceleration a to be greater than or equal to zero on this gear, i.e. a20. The second gear G2 is calculated by the gear system checking at which lower gear the driving force 12 of the motor vehicle 1 exceeds a calculated driving resistance, i.e. the total force counteracting the motor vehicle 1 in its direction of travel. In practical terms, the second gear G2 can be calculated by stepwise calculating the maximum driving force of the vehicle for gears lower than the first gear G1, and selecting the first lower gear - if the calculation is stepwise from higher to lower gears - which has a maximum driving force equal to greater than or greater than the calculated driving efficiency of the motor vehicle 1.
    In step F6, it is then calculated at which engine speed on the second gear G2 that the driving force of the motor vehicle 1 exceeds or is equal to the driving resistance (a 20) of the motor vehicle 1 in order to determine when a downshift to the second gear G2 is to be performed. the second gear G2 shall be close to the equilibrium engine speed immediately after downshifting, where the equilibrium engine speed is the engine speed at which the acceleration of the motor vehicle 1 is substantially zero.
    In step F7, it is calculated how long the motor vehicle 1 can run on each of the intermediate gears if there are a number of intermediate gears between the first G1 and the second G2 gear. The time how long the motor vehicle 1 can run on each intermediate gear is compared with a gear-specifically calibrated time value, i.e. compared to a threshold value Ti, for each intermediate gear. From these comparisons, the highest intermediate gear is selected from among the permissible intermediate gears, i.e. those gears which have a calculated time value greater than the threshold value TI. for each gear. It should be noted that the gear selected in step F7 is the second gear G2 if no higher gear meets the requirement as above.
    Furthermore, in step C1, when shifting from the first gear G1, the condition is checked whether the engine 10 has dropped more in engine speed than a calibrated limit value R from the highest engine speed the motor vehicle 1 had when it went into power deficit (if. Limit value R can vary depending on driving node Only when the engine speed has dropped more than the calibrated limit value R (preferably 1-100 rpm) is a downshift allowed.This limit value R is used in the procedure so that the motor vehicle 1 is not perceived as nervous or unstable, e.g. This step in step C1 does not need to be done from intermediate 13 gears because the motor vehicle 1 is then already on a hill, which means that the check in C1 is only relevant from the first gear Gl.
    In step P8, no downshift is performed if the engine speed has not dropped more than the limit value R during the check in Cl. This is to avoid the shifting system shifting when the driving resistance temporarily increases, such as on small slopes, and therefore makes the motor vehicle 1 perceived as nervous.
    In step C2, it is checked whether the current motor speed is close to the minimum motor speed m MZ. and if so, a downshift is immediately performed in step F9 P1 to the gear selected in step F7 because then there is a risk that the engine speed will drop below the minimum engine speed m Mm.
    Otherwise, in step F10, the engine speed of the motor vehicle 1 after a í + 1 T is predicted, if the current completed downshift to the gear selected in step F7, i.e. m the engine speed in step C2 is not below the minimum engine speed m Mm.
    Then, in step CS, it is checked whether the current motor speed etc. predicted in step F10 is less than m; + pi, which is the highest engine speed the engine 10 has had since the motor vehicle 1 went into power deficit and a tolerance value pl. according to fl = m; + p I., í = 1,2,3 ..., as described above. It should be noted that according to this embodiment (1) of the invention, the first highest engine speed is m; the same as the highest engine speed on the first gear G1, i.e. m; = mm (see step Fl). Thus, the highest engine speed on the first gear G1 will affect the entire downshift process and therefore act as an input parameter for the same.
    In step F11, a downshift is performed to the gear selected in step F7 if the current engine speed is within the interval I at the control in step CS. Otherwise, in step F12, the time period that the gearbox 20 can run on the gear selected in step F7 is calculated. In a practical application, the shifting system calculates how long the motor vehicle 1 can run on each intermediate gear from the first gear G1 to the second gear G2, and then selects the highest of these intermediate gears which satisfies the requirement that its estimated time value is greater than its gear-specific calibrated threshold value TI ..
    When the shifting system calculates the time period that the motor vehicle 1 can run on an intermediate gear, the system can use the minimum motor speed wMín which is a minimum motor speed which the motor vehicle 1 must not fall below, e.g. if a current engine speed drops so that it falls below, for example, COM. "= 1100 rpm, the shifting system must perform a downshift. The system then calculates how long the motor vehicle l can run on the intermediate gear from the engine speed the system ends up after shifting until the system ends up on The minimum gear system thus calculates how long the motor vehicle 1 will be able to run on the intermediate gear by calculating how fast the engine 10 will lose speed at the intermediate gear by knowing the minimum engine speed etc. after shifting will end up on.
    Finally, in step C4, it is checked whether the time period calculated in step F12 is as long a time period as the time period the motor vehicle 1 has been running on a current gear since the acceleration a became negative. In step F14 there is a downshift to the gear selected in step F7 if the answer is yes at the check in step C4. If, on the other hand, the answer is no in step C4, no step is taken in step F13.
    Figure 4 shows an example of a downshift of a motor vehicle 1 according to the invention, in a diagram where the x-axis represents the time and the y-axis the speed of the engine 10 in rpm. At the time t] when the motor vehicle 1 is propelled with the first gear Gl loaded, the motor vehicle 1 moves into an uphill slope, so that a power deficit occurs and the acceleration a of the motor vehicle 1 becomes negative. It is at this time t] that the engine speed of the first gear G1 (if determined which can be used as an input parameter in the downshift according to an embodiment of the invention).
    Since the motor vehicle 1 is in power deficit, the engine speed decreases and a first downshift occurs at time t2, which results in the engine speed going up again at time t3. Also at this next gear (first intermediate gear) a power deficit occurs and a new downshift is necessary for the motor vehicle 1 to be able to drive up the hill, which takes place at time t4. In this way the downshift takes place via one or fl your intermediate gears until the gearbox 20 reaches a power balance gear, i.e. the second gear G2, which takes place at time t7 in fi gur 4. At this second gear G2 (from time t8) the acceleration a is substantially zero, so that the motor vehicle 1 can maintain its speed on this gear.
    It should be further noted that the maximum engine speed for each intermediate gear is a higher or equal engine speed as the highest engine speed since the motor vehicle 1 ran out of power, i.e. when acceleration a became negative, as shown at times 13, t5 and t7 in Figure 4. This is achieved in order for the motor vehicle 1 to maintain its speed through the hill as well as possible by being close to the maximum power speed of the motor 10 on the intermediate gears. It also means that the motor vehicle 1 is perceived as aggressive and powerful on, for example, long steep slopes if it is driven at high speed because the engine speed increases for each downshift step and thus ends up closer to the engine speed that the motor vehicle 1 can maintain at maximum second gear G2. By better maintaining the speed at the entrance to the hill, the number of downshift steps can also be reduced if the hill should run out before the motor vehicle 1 reaches the second gear G2.
    It should further be noted that the various calculation steps in the method according to the invention are calculated in real time, as will be appreciated by those skilled in the art. Furthermore, the person skilled in the art realizes that a method for controlling a gearbox according to the present invention can also be implemented in a computer program, which when executed in a computer causes the computer to perform the method. The computer program is included in a computer-readable medium of a computer program product, said computer-readable medium consisting of a suitable memory, such as for example: ROM (Read-Only Memory), PROM (Programmable Read-Only Memory), EPROM (Erasable PROM), Flash memory, EEPROM (Electrically Erasable PROM), a hard disk drive, etc.
    Furthermore, the present invention relates to a system for controlling a gearbox. The system comprises at least one control unit 110 arranged to control a gearbox 20 in a motor vehicle 16 and is arranged to provide a downshift from a first gear G1, for which the acceleration a is negative, to a second gear G2, for which the acceleration a is positive or equal to zero. The downshifting takes place by means of at least one intermediate gear stage between the first G1 and second G2 gears, a maximum engine speed in each intermediate gear stage being an equal, or a higher engine speed than a maximum engine speed in a previous intermediate gear stage.
    A system described above can be further modified according to the various embodiments of the method above. In addition, the present invention relates to a motor vehicle 1, such as a truck or bus, comprising at least one system as above.
    Figure 5 schematically shows a control unit 110 to be part of a system according to the invention.
    The control unit 110 comprises a calculation unit 111, which may be constituted by substantially any suitable type of processor or microcomputer, e.g. a Digital Signal Processor (DSP), or an Application Specific Integrated Circuit (ASIC). The calculation unit 11 is connected to a memory unit 112 arranged in the control unit 110, which provides the calculation unit 111 e.g. the stored program code and / or the stored data calculation unit lll need to be able to perform calculations. The calculation unit lll is also arranged to store partial or final results of calculations in the memory unit 112.
    Furthermore, the control unit 110 is provided with devices 113, 114, 115, 116 for receiving and transmitting input and output signals, respectively. These input and output signals may contain waveforms, pulses, or other attributes, which of the input signals 113, 116 may be detected as information and may be converted into signals which may be processed by the computing unit III. These signals are then provided to the computing unit 111. The devices 114, 115 for transmitting output signals are arranged to convert signals obtained from the computing unit 111 for creating output signals by e.g. modulate the signals, which can be transmitted to other parts of the system for determining down and upshift points. One skilled in the art will appreciate that the above-mentioned computer may be constituted by the computing unit 111 and that the above-mentioned memory may be constituted by the memory unit 112. 17 Each of the connections to the devices for receiving and transmitting input and output signals, respectively, may be constituted by one or more of a cable; a data bus, such as a CAN bus (Controller Area Network bus), a MOST bus (Media Orientated Systems Transport), or any other bus configuration; or by a wireless connection. The connections 70, 80, 90, 100 in Figure 1 can also consist of one or more of these cables, buses, or wireless connections.
    Finally, it should be understood that the present invention is not limited to the above-described embodiments of the invention but relates to and encompasses all embodiments within the scope of the appended independent claims.
    权利要求:
    Claims (18)
    [1]
    Method for controlling a gearbox, which gearbox (20) is arranged to be arranged in a motor vehicle (1), characterized by providing a downshift of said gearbox (20) from a first gear (G1), for which the acceleration a of said motor vehicle (1) is negative, to a second gear (G2), for which the acceleration a is positive or substantially equal to zero, which downshift takes place by means of at least one intermediate gear step between said first (G1) and second (G2) gear, wherein a the maximum engine speed in each intermediate gear step is equal to one, or a higher engine speed than a maximum engine speed in a previous intermediate gear step.
    [2]
    The method of claim 1, wherein said highest engine speed in each intermediate gear step assumes a value that is p1. higher than said maximum engine speed in a previous intermediate gear step, wherein pl. is a parameter value.
    [3]
    The method of claim 1, wherein the ratio between said maximum engine speed in each intermediate gear step and said maximum engine speed in a previous intermediate gear step is given by: må "= 0); + pl. , where (of is said maximum engine speed in each intermediate gear step and co; is said maximum engine speed in a previous intermediate gear step.
    [4]
    A method according to any one of the preceding claims, wherein each intermediate change step lasts for a longer period of time than a threshold value Ti.
    [5]
    The method of claim 4, wherein said threshold value TI. is used as a parameter for determining the number of shift steps in a shift between said first gear (G1) and an intermediate shift step, and / or between two successive intermediate shift steps, and / or between an intermediate shift step and said second gear (G2). 10 15 20 25 30 19
    [6]
    A method according to claim 4 or 5, wherein said threshold value TI. is used as a parameter for determining the number of intermediate gear stages between said first (G1) and second (G2) gears.
    [7]
    A method according to any one of claims 4-6, wherein said threshold value T. is specific to each intermediate shift step.
    [8]
    A method according to any one of claims 4-7, wherein said threshold value T. is within the range of 1-15 seconds.
    [9]
    A method according to any one of claims 4-8, wherein a current intermediate change step lasts for a period of time as long as a time period for a subsequent intermediate change step.
    [10]
    A method according to any one of the preceding claims, wherein an engine speed com on said first gear (G1) is used as an input parameter in effecting said downshift.
    [11]
    A method according to claim 10, wherein said engine speed com on said first gear (G1) is an engine speed said motor vehicle (1) assumes when an acceleration a of said motor vehicle (1) becomes negative on said first gear (G1).
    [12]
    A method according to claim 10 or 11, wherein said engine speed (if on said first gear (G1) is a maximum engine speed on said first gear (G1).
    [13]
    A method according to any one of the preceding claims, wherein an engine speed when shifting in an intermediate gear step is a higher engine speed than an engine speed when shifting in a previous intermediate gear step.
    [14]
    A method according to any one of the preceding claims, wherein a shift between said first gear (G1) and an intermediate gear step, and / or between two successive intermediate gear steps, and / or between an intermediate gear step and said second gear (G2) ) include one or more of your switching steps.
    [15]
    A computer program comprising program code, which when said program code is executed in a computer causes said computer to perform any method according to any one of the preceding claims.
    [16]
    A computer program product comprising a computer readable medium and a computer program according to claim 15, wherein said computer program is included in said computer readable medium belonging to any of the group comprising: ROM (Read-Only Memory), PROM (Programmable ROM), EPROM (Erasable PROM), Flash memory, EEPROM (Electrically EPROM) and hard disk drive.
    [17]
    A system for controlling a gearbox (20), which system comprises at least one control unit (110) arranged for controlling a gearbox (20) in a motor vehicle (1), characterized in that the system is arranged to effect a downshift of said gearbox. (20) from a first gear (G1), for which the acceleration a of said motor vehicle (1) is negative, to a second gear (G2), for which the acceleration a is positive or equal to zero, which downshifting takes place by means of at least one intermediate gear step between said first (G1) and second (G2) gears, a maximum engine speed in each intermediate gear step being an equal, or a higher engine speed than a maximum engine speed in a previous intermediate gear step.
    [18]
    A motor vehicle (1), such as a truck or bus, comprising at least one system according to claim 17.
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    US8688335B2|2014-04-01|
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    EP2478270B1|2020-05-27|
    CN102686915A|2012-09-19|
    US20120179343A1|2012-07-12|
    CN102686914B|2015-03-25|
    US20120173097A1|2012-07-05|
    EP2478269A4|2013-08-07|
    RU2012114591A|2013-10-27|
    CN102575758A|2012-07-11|
    EP2478264A1|2012-07-25|
    US8694216B2|2014-04-08|
    CN102686914A|2012-09-19|
    BR112012005610A2|2020-10-13|
    RU2514623C2|2014-04-27|
    BR112012005610B1|2021-02-02|
    WO2011031231A1|2011-03-17|
    BR112012005608B1|2021-03-23|
    EP2478271B1|2014-12-31|
    RU2515952C2|2014-05-20|
    BR112012005609A2|2020-07-21|
    RU2514969C2|2014-05-10|
    RU2012114598A|2013-10-27|
    SE534936C2|2012-02-21|
    EP2478271A1|2012-07-25|
    CN102575762B|2015-05-06|
    BR112012005607A2|2016-06-14|
    CN102575758B|2015-03-25|
    EP2478270A4|2013-08-07|
    RU2012114596A|2013-10-27|
    BR112012005608A2|2016-06-21|
    WO2011031232A1|2011-03-17|
    BR112012005607B1|2021-03-23|
    CN102686915B|2015-03-25|
    EP2478264B1|2014-12-17|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP0270708B1|1986-12-05|1990-08-29|Eaton Corporation|Control and method for controlling amt system including manually operated engine compression brake|
    US4916979A|1988-04-18|1990-04-17|Eaton Corporation|On-grade shift logic with provision for skip downshifts|
    US5487004A|1993-10-29|1996-01-23|Eaton Corporation|Control system/method for automated mechanical transmission systems|
    DE19703561A1|1997-01-31|1998-08-06|Zahnradfabrik Friedrichshafen|Device for evaluating vehicle, drive and operating parameters|
    US6085140A|1997-12-05|2000-07-04|Hyundai Motor Company|Shift control method and system for an automatic transmission|
    US6085606A|1998-11-03|2000-07-11|Eaton Corporation|Mechanical transmission with reduced ratio steps in upper transmission ratios|
    KR100335916B1|1999-12-10|2002-05-10|이계안|Shift controlling methode for automatic transmission of vehicle|
    JP3736345B2|2000-12-22|2006-01-18|日産自動車株式会社|Automotive engine control device|
    SE520231C2|2001-10-31|2003-06-10|Volvo Lastvagnar Ab|Vehicle and method for automatic selection of a gearbox of a gearbox included in a vehicle|
    SE518727C2|2001-12-17|2002-11-12|Scania Cv Abp|Building system for synchronization devices for a gearbox|
    US6702713B2|2001-12-21|2004-03-09|Eaton Corporation|Shift strategies for mock continuously variable transmission|
    US6893378B2|2003-05-19|2005-05-17|Eaton Corporation|Transmission system and method of operation to accommodate engagement of centrifugal clutch|
    JP4301224B2|2005-02-16|2009-07-22|トヨタ自動車株式会社|Automobile and control method thereof|
    EP1960698B1|2005-12-09|2014-04-02|Volvo Lastvagnar AB|A method for gear selection during driving of a vehicle in a heavy uphill drive condition|
    DE102006017712A1|2006-04-15|2007-10-25|Zf Friedrichshafen Ag|Method for switching control of an automated stepped gearbox|
    JP5061616B2|2006-10-05|2012-10-31|トヨタ自動車株式会社|Control device for automatic transmission|
    JP5292807B2|2007-12-28|2013-09-18|アイシン・エィ・ダブリュ株式会社|Shift control device for automatic transmission|
    JP4329864B2|2008-02-12|2009-09-09|トヨタ自動車株式会社|Control device for vehicle power transmission device|DE102009055833A1|2009-11-26|2011-06-01|GM Global Technology Operations LLC, , Detroit|Method for controlling a switching operation of an automatic transmission|
    JP5786648B2|2011-10-28|2015-09-30|トヨタ自動車株式会社|Shift control device and shift control method|
    SE536699C2|2012-10-17|2014-06-03|Scania Cv Ab|Systematic choice of vehicle specification|
    US9017217B2|2012-11-08|2015-04-28|Ford Global Technologies, Llc|Pilot downshifting system and method|
    US8974346B2|2012-11-08|2015-03-10|Ford Global Technologies, Llc|Method and system to control vehicle operation|
    CN104088998A|2014-07-01|2014-10-08|盛瑞传动股份有限公司|Automobile, and leapfrogging gear lowering control method and system of automatic transmission of automobile|
    RU2650330C1|2017-02-13|2018-04-11|Общество с ограниченной ответственностью "Международная инжиниринговая компания по разработке новой техники" |Method of gearbox control|
    JP6503396B2|2017-03-27|2019-04-17|本田技研工業株式会社|Control device of automatic transmission for vehicle|
    US10619724B2|2017-08-02|2020-04-14|GM Global Technology Operations LLC|Method of adjusting deceleration dependent shift points|
    CN110159749B|2019-04-29|2021-02-09|东风商用车有限公司|Control method for short-time overspeed mode of ramp of AMTload-carrying truck|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE0901182|2009-09-14|
    SE1050957A|SE534886C2|2009-09-14|2010-09-14|Method for controlling a gearbox|SE1050957A| SE534886C2|2009-09-14|2010-09-14|Method for controlling a gearbox|
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