Power dissipation management system

FIELD OF THE INVENTION

0001The present invention relates to a power dissipation management system for vehicles having one or more braking devices.

BACKGROUND OF THE INVENTION

0002Various braking systems designed to dissipate the kinetic energy of a vehicle are known. <patcit id="pcit0001" dnum="DE3000968"><text>DE 3 000 968</text></patcit> discloses a hydrodinamic drive unit that has an input coupled to 2drive trains. One such system is described in <patcit id="pcit0002" dnum="US5184875A"><text>U.S. Patent No. 5,184,875</text></patcit> which provides for an electronically controlled braking system. A control unit receives a braking signal from the driver. The unit selects one or more brakes of the vehicle to obtain deceleration proportional to the braking signal. The vehicle has a friction service brake and a wear-free auxiliary brake such as a fluid brake, an eddy current brake or a motor brake. Preferably, the wear-free brake is triggered and, if the braking signal is significant enough, the friction-affected brake is triggered. The system has signal transducers to detect the condition (temperature, thickness, frequency of use) of the friction-affected brake and the vehicle speed. If the system detects a condition in the brakes which has lowered their coefficient of friction, the service brake is triggered exclusively to correct the condition. If, however, the system determines that additional use of the service brakes may overheat them, it triggers the auxiliary brake additionally or exclusively.

0003<patcit id="pcit0003" dnum="US5303986A"><text>U.S. Patent No. 5,303,986</text></patcit> provides for a braking system having both an electronic pneumatic braking system and a retarder which applies a retarding torque to the vehicle driveline. The invention relates to integrating a retarder control system with a control system for the pneumatically actuated brakes to distribute the braking required between the systems without jeopardizing the braking balance between the driven and non-driven wheels. A controller receives a braking signal from the vehicle operator, from an engine or exhaust brake, or from the operator controlled retarder switches, in addition to a signal from a vehicle load sensor. The controller also receives data from sensors on each wheel regarding the speed of each wheel. The controller generates output signals to the retarder, and the engine and/or exhaust brake. During normal operation, the retarder is switched on, either manually or automatically, every time a brake application is effected. The braking signal to the drive wheels is adjusted for the effects of the retarders so that the braking balance front to rear is maintained.

0004<patcit id="pcit0004" dnum="US5441335A"><text>U.S. Patent No. 5,441,335</text></patcit> provides for an electronically controlled motor vehicle brake. An electrical braking valve pick-up generates an electrical output signal (U) as a function of the actuation path of the brake pedal and is connected to an electronic control unit. A gradient, ΔU/Δt, which represents a measure of the actuation rate of the braking value pick-up, is determined by the control unit from the variation with time of the output signal. If the gradient is above a limiting value, the unit recognizes rapid braking. The friction brake is engaged earlier and the auxiliary brake (e.g., engine brake, retarder, constant throttles) may not ever be engaged. If the gradient is below a minimum value, slow braking is present. The friction brake responds relatively late so that the slower auxiliary brake can respond first and absorb most or all of the braking need.

0005<patcit id="pcit0005" dnum="US5613743A"><text>U.S. Patent No. 5,613,743</text></patcit> provides for a method of controlling the slippage of driven wheels in a motor vehicle. Initially, a target braking torque for each of the respective driven wheels is determined. The torques are compared and the smallest of them is selected. A target engine torque is then determined from the smallest braking torque. The engine torque is adjusted to conform to the target engine torque. A residual braking torque for each wheel is calculated based upon the target engine torque and the respective target brake torques. The brake pressure at the driven wheels is varied so that the residual braking torques for each wheel are realized.

0006<patcit id="pcit0006" dnum="US5657838A"><text>U.S. Patent No. 5,657,838</text></patcit> provides for a method of operating a drive unit for a vehicle having an engine braking system. The unit has an engine, a gearbox and a retarder in a constant drive connection with the engine. The unit also has a cooling circuit where the coolant is the fluid for the retarder. The retarder acts as a pump for the cooling circuit. An overall braking output is measured and compared to a value. When the overall braking output is less than the value, the retarder is activated to deliver the required amount. When the braking output is more than the value, the engine braking system is activated along with the retarder. The retarder delivers the difference in braking between that provided by the engine braking system and required amount.

0007<patcit id="pcit0007" dnum="US5816665A"><text>U.S. Patent No. 5,816,665</text></patcit> provides for a retarder system for a drive train where the system is driven by a multi-cylinder engine via a transmission. The system has a compression brake adapted to operate in multiple stages to provide various degrees of braking to the engine. A fluid retarder, also adapted to operate in multiple stages to absorb power from the engine, is coupled for rotation with the vehicular drive train. Each stage of the retarder corresponds to a specific braking level output from the retarder. For example, stage one provides only a small amount of fluid to circulate within the retarder housing thus resulting in a small braking effect. Stage three, however, adds a predetermined amount of fluid to the retarder housing thus providing a larger braking effect. A controller is electrically connected to the compression brake and the fluid retarder to control them both to slow the speed of the vehicle.

0008<patcit id="pcit0008" dnum="US6287237B"><text>U.S. Patent No. 6,287,237</text></patcit> provides for a method of controlling a drive train including the steps of converting a braking signal from a brake petal into a braking torque. A setpoint value for an engine drag torque is determined based upon the braking torque. A downshift characteristic diagram is provided to determine a setpoint transmission ratio. The ratio is a function of the setpoint value for the engine drag torque and also of a variable functionally associated with the speed of the vehicle. The diagram has characteristic curves defined by taking into account a minimum engine torque. Lastly, a transmission ratio is automatically set by reference to the diagram.

0009The present invention has the advantage over the prior art by distributing the kinetic energy of the vehicle among various components of the hydrodynamic transmission based upon the actual thermal capacity of the component. Distributing the kinetic energy among the components of the transmission allows the size of the service brakes to be reduced and hence lowers their cost.

SUMMARY OF THE INVENTION

0010The present invention is directed toward a method and apparatus for a power dissipation management system for vehicles wherein the thermal condition for a plurality of driveline components is determined. Based upon the thermal condition of each driveline component, a quantity of energy each can accept is determined. A braking signal is provided to one or more of the driveline components based at least in part upon the quantity of energy the component can accept.

BRIEF DESCRIPTION OF THE DRAWINGS

0011The above, as well as other advantages of the present invention, will become readily apparent to those skilled in the art from the following detailed description when considered in the light of the accompanying drawings in which: <ul id="ul0001" list-style="none" compact="compact"><li><figref idref="f0001">Fig. 1</figref> is a schematic of an embodiment of the present invention;</li><li><figref idref="f0002">Fig. 1a</figref> is a schematic of another embodiment of the present invention;</li><li><figref idref="f0003">Fig. 2</figref> is a schematic of a component of the invention depicted in <figref idref="f0001">Figs. 1</figref> and <figref idref="f0002">1a</figref>;</li><li><figref idref="f0004">Fig. 3</figref> is a flow chart depicting a step sequence of the present invention;</li><li><figref idref="f0005">Fig. 4</figref> is a chart of torque against engine speed; and</li><li><figref idref="f0006">Fig. 5</figref> is a chart of turbine torque against turbine speed.</li></ul>

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

0012It is to be understood that the invention may assume various alternative orientations and step sequences, except where expressly specified to the contrary. It is also to be understood that the specific devices and processes illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the inventive concepts defined in the appended claims. Hence, specific dimensions, directions or other physical characteristics relating to the embodiments disclosed are not to be considered as limiting, unless the claims expressly state otherwise.

0013<figref idref="f0001">Fig. 1</figref> schematically represents a portion of a power dissipation management system 10 for a vehicle (not shown). The system 10 comprises a plurality of driveline components 12 comprising a torque converter 14, at least one forward clutch 16, at least one reverse clutch 18 and at least one service brake 20. Although the following will describe the invention in terms of a single forward and a single reverse clutch, those skilled in the art will readily appreciate that the present invention incorporates vehicles having more than one forward clutch and/or more than one reverse clutch or more than one clutching mechanism.

0014As known to those skilled in the art, coolant fluid, such as oil, is provided from at least one reservoir (not shown) through at least one fluid line 21a, 21b, 21c, and 21d to each of the components 14, 16, 18, and 20, respectively. In one embodiment, a thermal sensor is operatively connected to each fluid line for each component as shown in <figref idref="f0001">Fig. 1</figref>. Thus, the torque converter 14 has a thermal sensor 22, the forward clutch 16 has thermal sensor 24, the reverse clutch 18 has a thermal sensor 26, and the service brake 20 has a thermal sensor 28. The thermal sensors 22, 24, 26, 28 sense the temperature of the fluid entering each component 14, 16, 18, and 20, respectively. Each thermal sensor 22, 24, 26, 28 is connected to a computer 30 to provide the computer 30 with each sensed temperature.

0015In another embodiment schematically depicted in <figref idref="f0002">Fig. 1a</figref>, the coolant fluid is provided from a single reservoir R through coolant lines L to the components 14, 16, 18 and 20. In this embodiment, only a single sensor S senses the temperature of the entering coolant fluid. Sensor S provides the computer 30 with the sensed temperature.

0016As schematically depicted in <figref idref="f0003">Fig. 2</figref>, the computer 30 is comprised of a plurality of modules including a driver intention module 32, an engine control module 34, a thermal module 36, a clutch control module 38 and a braking module 40. Preferably, each of the above modules 32, 34, 36, 38 and 40 are connected to a driving module 42.

0017The term module is used to describe functions of the computer 30, as will be discussed in detail below. The modules 32, 34, 36, 38, 40, 42 may be combined with one another in any combination, or they may exist individually, as depicted in <figref idref="f0003">Fig. 2</figref>. Alternatively, the modules 32, 34, 36, 38, 40, 42 may be physically combined in a single computer 30. Regardless of the embodiment, the computer 30 can execute one or more of the modules 32, 34, 36, 38, 40, 42 in any order or sequence, including simultaneously.

0018As schematically depicted in <figref idref="f0003">Fig. 2</figref>, the driver intention module 32 is connected to a sensor 44 on an accelerator pedal 46, a sensor 48 on a brake pedal 50 and it may also be connected to one or more sensors 52 on hydraulic controls 54 for the vehicle. The hydraulic controls 54 may be used for auxiliary vehicle hydraulic systems (not shown) as known to those skilled in the art. The desired acceleration V_out, based upon the sensed position of the accelerator pedal 46, or the desired deceleration B_i, based upon the sensed position of the brake pedal 50, is received by the driver intention module 32 and sent to the driving module 42. The sensed position of the hydraulic controls 54 may be similarly received and sent.

0019The driver intention module 32 also comprises a speed sensor 55 for measuring the speed of the vehicle V_M. V_M is sent to driving module 42.

0020The engine control module 34 measures the actual revolutions per minute of the engine in any manner known to those skilled in the art. The measured engine speed is transferred from the engine control module 34 to the driving module 42.

0021In a preferred embodiment, the clutch control module 38 is connected to at least one sensor 58 for sensing a forward clutch torque M_F of the forward clutch 16, at least one sensor 62 for sensing a reverse clutch torque M_R of the reverse clutch 18, and at least one sensor 66 for sensing a service brake torque M_AB of the service brake 20. Each of these sensors 58, 62, 66 communicates some or all of the torques M_F, M_R, M_AB to the clutch control module 38 which in turn communicates them to the driving module 42.

0022If, for any reason, some or all of the torques M_F, M_R, M_AB cannot be sensed, the torque M_F, M_R, and/or M_AB is assumed to be equal to the desired clutch torque for that component. The desired clutch torque is determined by the braking module 40 and provided to modules 38 and 42. The desired clutch torque is proportional to the amount of braking desired.

0023In the process of using the present invention, the sensed position of the brake pedal 50, the sensed position of the accelerator pedal 46 and the sensed positions of the vehicle hydraulic controls 54 (if any) are provided to the driver intention module 32. The driver intention module 32 determines the desired acceleration V_out, the desired deceleration B_i and/or the desired engine speed (throttle) of the vehicle based upon the respectively sensed positions stated above. The desired acceleration V_out, the desired deceleration B_i, the desired engine speed of the vehicle (throttle) and/or V_M are sent to the driving module 42 from the driver intention module 32. The driving module 42 signals the engine control module 34 of the desired engine speed through a throttle signal and the engine control module 34 maintains the engine at that speed.

0024By way of a first example, if the sensor 44 on the accelerator pedal 46 determines the accelerator pedal 46 is being deflected, the vehicle operator likely wants the vehicle to accelerate. In that case, the driver intention module 32 signals the driving module 42 that no braking through the driveline components 12, as described in more detail below, is requested.

0025By way of a second example, if the sensors 52 on the vehicle hydraulic controls 54 senses that the controls 54 have been engaged, the driver likely wants to use the auxiliary systems on the vehicle. In that case, the driver intention module 32 signals the driving module 42 that no braking through the driveline components 12, as described below, is requested.

0026The thermal module 36 uses a plurality of inputs to calculate a forward clutch temperature T_F, a reverse clutch temperature T_R, a service brake temperature T_AB, and/or a torque converter temperature T_TC. The inputs are provided from the driving module 42 and preferably comprise a power dissipated in the forward clutch P_F, a power dissipated in the reverse clutch P_R, a power dissipated in the torque converter P_TC, and a power dissipated in the service brake P_AB.

0027The power dissipated values P_F, P_R, and P_AB are calculated from V_M, the gear ratios of the vehicle transmission, the engine speed and the clutch torques M_F, M_R, and M_AB, respectively. As known to those skilled in the art, the gear ratios of the vehicle transmission vary from transmission to transmission. Preferably, information on the gear ratio for a particular transmission is provided to the driving module 42 as a configuration file. Those skilled in the art know that for each power dissipation calculation for each clutch, the power dissipated is the product of the speed difference over that clutch and the torque flowing through that clutch.

0028A power dissipated in the torque convert P_TC is calculated from V_M, the gear ratios of the vehicle transmission, the engine speed and the characteristics of the torque converter. Those skilled in the art know that the power dissipated is determined from standard tables using the engine speed and the turbine speed.

0029The inputs also include the entering coolant fluid temperature as determined from the thermal sensors 22, 24, 26 and 28 for each respective component or thermal sensor S. Each temperature T_F, T_R, T_AB, and T_TC is calculated using the respective sensed cooling fluid entering temperature, or the cooling fluid entering temperature from sensor S, and by knowing the thermal properties of each component 14, 16, 18 and 20. Those skilled in the art know that the thermal properties of the components 14, 16, 18 and 20 comprise the thermal mass of the component, the coolant flow through the component, the amount of heat dissipated in the component and the geometry of the component.

0030In an alternative embodiment to that describe above, those skilled in the art will readily appreciate that the temperature of each component T_F, T_R, T_AB, and T_TC can be directly measured from the respective component.

0031Regardless of which of the above methods is used to determine T_F, T_R, T_AB, and T_TC, preferably, each of these temperatures T_F, T_R, T_AB, T_TC are communicated to the driving module 42.

0032As depicted in <figref idref="f0003">Figs. 2</figref> and <figref idref="f0004">3</figref>, the braking module 40 receives as inputs the forward clutch temperature T_F, the reverse clutch temperature T_R, the service brake temperature T_AB, the torque converter temperature T_TC, the desired acceleration V_out and the deceleration value B_i. The braking module 40 determines the amount of energy the forward clutch 16, the reverse clutch 18, the service brake 20 and the torque converter 14 can safely accept based upon the above inputs. The braking module 40 then compares the amount of energy each of the above components 14, 16, 18, 20 can accept with a plurality of braking profiles 64. The braking profiles are depicted as N, N+1,... N+... in <figref idref="f0004">Fig. 3</figref>. If the amount of energy available in any of the above components 14, 16, 18, 20 is less than the braking energy called for in a braking profile 78 for any component 14, 16, 18, 20 then another braking profile 64 is selected. The amount of energy called for in a braking profile 64 for the forward clutch is B_F, for the reverse clutch is B_R, for the torque converter is B_TC and for the service brake is B_AB. The braking profiles 64 are provided to the braking module 40 in order of highest braking efficiency for the vehicle to lowest braking efficiency.

0033A braking profile 64 is selected that does not require more than, or is at least equal to, the braking energy that the forward clutch 16, the reverse clutch 18, the service brake 20 and/or the torque converter 14 can accept. It is within the scope of the present invention that some profiles do not require braking on each drivetrain component.

0034The selected braking profile 64 converts the forward clutch temperature T_F, the reverse clutch temperature T_R, the service brake temperature T_AB, the torque converter temperature T_TC, the desired acceleration V_out and the deceleration B_i value into one or more of the following: a forward clutch torque M_F, a reverse clutch torque M_R, a service brake torque M_AB and/or a throttle setting (throttle).

0035Some or all of the torques M_F, M_R, M_AB are communicated to the clutch control module 38 where they are converted to one or more of a forward clutch fluid pressure, a reverse clutch fluid pressure, a torque converter pressure and/or a service brake pressure. The pressures are communicated to their respective components in a manner known to those skilled in the art. Similarly, the throttle setting (throttle) is communicated to the engine control module 34 where it is converted to a torque converter pressure to the torque converter.

0036The following braking profiles are provided in no particular order of preference, but are provided as examples of preferred embodiments of the present invention. A first braking profile has no thermal limitations, however, the engine must be operating at a minimum revolutions per minute, often the idle speed of the motor. In this profile, the engine is used to brake the driveline by decreasing the throttle. The engine speed decreases and the torque converter 14 provides torque to the driveline in the opposite direction of its rotation to slow the vehicle as known to those skilled in the art. The maximum braking torque depends in part upon the engine speed and is higher for the higher engine speeds of the vehicle as shown in <figref idref="f0005">Fig. 4</figref>.

0037A second braking profile decreases the engine speed, as provided above, to engage the torque converter 14 as a brake on the driveline. The operator may prevent the engine speed from decreasing beyond a set point to keep engine driven components provided with sufficient power. Initially, fluid pressure is increased to the reverse clutch 18 while the forward clutch 16 is kept under full pressure. The reverse clutch 18 slips and transfers torque through the forward clutch 16, thus braking the driveline.

0038As known to those skilled in the art, once the engine drops below a certain limit determined by the engine speed, the torque converter 14 will begin to drive the driveline. At that moment, the forward clutch 16 is completely opened, thus preventing the torque converter 14 from providing energy to the driveline. The reverse clutch 18 continues to absorb energy from the driveline, thus slowing it down further.

0039A third braking profile increases fluid pressure to just the reverse clutch 18 or both the reverse clutch 18 and the forward clutch 16 in any proportion. For example, the desired braking may be 100% in the reverse clutch 18, 80% in the reverse clutch 18 and 20% in the forward clutch 16, 50% in the reverse clutch 18 and 50% in the forward clutch 16 or 20% in the reverse clutch 18 and 80% in the forward clutch 16. Naturally, other proportions of reverse 18 and forward clutch 16 braking are well within the scope of the present invention.

0040Under this third braking profile, the torque converter 14 can be put into at least three different modes by closed loop controlling the throttle and the torque flow through the clutches 16, 18 or in an open loop system as known by those skilled in the art. The three modes of the torque converter 14 include (a) counter rotation mode, (b) normal mode, and (c) braking mode. These three modes are graphically depicted in <figref idref="f0006">Fig. 5</figref>.

0041As seen in <figref idref="f0006">Fig. 5</figref>, during counter rotation mode the turbine torque is high and the turbine speed is low and slightly negative, thus the torque converter 14 is taking away energy from the drivetrain and helping in braking. In this mode, those skilled in the art will appreciate that the forward clutch 16 is stressed much more than the reverse clutch 18 to assist in braking.

0042In normal mode, there are two zones b1 (high turbine torque and low turbine speed) and b2 (low turbine torque and high turbine speed) that can be used for driveline braking. However, other than these two zones it is preferred that this mode is avoided. In these zones, both the reverse 18 and forward clutches 16 can be slipped in various proportions as mentioned above.

0043In zone b1, the differential speed of the forward clutch 16 and the reverse clutch 18 are more or less equal. Thus, the forward clutch 16 is stressed more or less equally as the reverse clutch 18.

0044In zone b2, the differential speed of the forward clutch 16 is low and the differential speed of the reverse clutch 18 is high. Thus, the reverse clutch 18 is stressed more than the forward clutch 16 to assist in braking.

0045In the braking mode, also depicted in <figref idref="f0006">Fig. 5</figref>, the turbine torque is low and negative and the turbine speed is high. The differential speed of the forward clutch 16 is low, but the differential speed of the reverse clutch 18 is high. Thus, the reverse clutch 18 is stressed much more than the forward clutch 16 to assist in braking.

0046Entering into any of the above-described modes depends upon the amount of energy the forward 16 and the reverse 18 clutches can accept. When the reverse clutch 18 cannot accept additional energy, the energy is stored in the forward clutch 16 and vice versa. If neither clutch 16, 18 can accept any additional energy, the braking module will move to the next braking profile.

0047A fourth braking profile can be used if neither the forward 16 or the reverse 18 clutches can accept any additional energy or the amount of braking the forward 16 and/or the reverse 18 clutches can accept is not sufficient. In this braking profile, the service brakes 20 are engaged to provide the additional amount of braking required.