Abstract:
A system and method is employed to regulate a minimum transmission input speed based on automatic fluid temperature. The system includes a temperature sensor for sensing a temperature of the automatic transmission fluid and a controller for setting a minimum engine speed of the engine based on the temperature of the automatic transmission fluid. The size of a transmission pump may be reduced while the pump is still able to supply enough automatic transmission fluid to friction elements and gear ratios to provide lubrication and enable friction element actuators to engage and disengage the friction elements in a timely and effective manner In a preferred form of the invention, when the temperature of the automatic transmission fluid is below 210° F., the minimum engine speed is set to no greater than 900 rpm; and when the temperature of the automatic transmission fluid is above 210° F., the minimum engine speed is set to no less than 1000 rpm.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is a divisional of U.S. patent application Ser. No. 12/435,715 filed May 5, 2009. The entire contents of these applications are incorporated herein by reference. 
     
    
     FIELD OF THE INVENTION 
       [0002]    The present invention pertains to the art of control systems and, more particularly, a system and method for controlling an automotive vehicle transmission in response to temperature changes in automatic transmission fluid passing through the transmission. 
       BACKGROUND OF THE INVENTION 
       [0003]    Automotive vehicles often have an automatic transmission located in a powertrain that delivers power from an engine to traction wheels of the vehicle. When the vehicle accelerates from a standing start, the transmission automatically changes the relative ratio of a transmission input shaft that receives power from the engine and a transmission output shaft that delivers power from the transmission to downstream elements of the powertrain and eventually to the wheels. The ratio changes are generally performed by selectively braking components of interlinked planetary gear sets or selectively engaging components of the gear sets to other components of the gear sets by the use of friction elements. The gear sets are mounted in a housing that also contains actuators for the friction elements. A pump is used to supply automatic transmission fluid to the friction element actuators to enable them to perform the gear changing function and also provides fluid to the gear sets so that they are properly lubricated. 
         [0004]    It is considered desirable in the art to ensure that automobile transmissions allow the complete powertrain to be as efficient as possible. However, because of adjustments required to properly manage transmission operation when the temperature of the automatic transmission fluid is elevated, efficiency can be compromised. The elevated temperature leads to lower viscosity in the automatic transmission fluid which, in turn, leads to reduced pump efficiency and to more fluid leakage as the fluid progresses around the transmission. In order to maintain a required lubrication flow and fluid pressure to supply the friction element actuators so that they may control the friction elements in a timely and effective manner, a minimum allowable pump speed must be increased. Since the pump usually obtains power from the engine, a minimum allowable engine speed must also be increased. Increasing the minimum allowable pump and engine speeds increases fuel consumption and worsens fuel economy. 
         [0005]    Generally, prior art solutions to the problem of supplying sufficient automatic transmission fluid that has an elevated temperature were directed to requiring a minimum engine speed that would provide an adequate supply of fluid under worst-case temperature conditions. These solutions had the advantage of simplicity in that once the minimum allowable engine speed was set no further control was necessary. Also, the minimum engine speed required by other factors, such as drivability, vehicle noise and harshness, was frequently higher than the minimum required due to increased automotive fluid temperature so the increased temperature was not a major factor when trying to reduce engine speed. However, in order to reduce parasitic loss of power caused by the transmission fluid pump, transmission designers are reducing transmission pump displacements which, in turn, is requiring higher pump speeds. Thus, the need to provide an adequate supply of transmission fluid can become a controlling factor on minimum engine speed. 
         [0006]    Other prior art solutions have been directed to increasing fuel efficiency by addressing different problems. For example, Japanese Patent Document JP 4066337 discloses an oil pump that is directly connected to an engine. The idle speed of the engine is increased when the oil temperature reaches a certain level. Basically, this arrangement is not concerned with setting a minimum engine speed during transmission gear ratio shifts, but rather focuses on adjusting engine idle speed. 
         [0007]    Another prior art solution is set forth in U.S. Pat. No. 5,556,349 which discusses a known automatic transmission having a normal temperature shift pattern and a high temperature shift pattern. The goal is to have the automatic controller constantly monitor the transmission fluid temperature and prevent it from overheating by switching to the high temperature shift pattern. The high temperature shift pattern avoids heating the transmission fluid as much as the normal temperature shift pattern in that the high temperature pattern shifts to a higher gear at a higher speed than the normal temperature pattern. This increases torque converter average speed and reduces torque converter average torque, both of which changes reduce the amount of heat generated, particularly by an open torque converter. 
         [0008]    As can be seen by the above discussion, there is a need in the art for a system that will effectively reduce the minimum allowable engine speed requirement during gear shifts, while still providing adequate amounts of automatic transmission fluid needed for lubrication and for friction element actuators. 
       SUMMARY OF THE INVENTION 
       [0009]    The present invention is directed to a transmission fluid supply system method employed in a vehicle having an engine for providing power, a transmission including multiple gear ratios and friction elements with associated actuators for engaging and disengaging the friction elements to shift the transmission between gear ratios, and a pump driven by the engine. The system improves vehicle efficiency by regulating a minimum transmission input speed based on automatic transmission fluid temperature. The system includes a temperature sensor for sensing a temperature of the automatic transmission fluid and a controller for setting a minimum engine speed of the engine based on the temperature of the automatic transmission fluid. With this arrangement, the size of the pump may be reduced while the pump is still able to supply enough automatic transmission fluid to the friction elements and gear ratios to provide lubrication and to the actuators to enable the actuators to engage and disengage the friction elements in a timely and effective manner. 
         [0010]    In accordance with a preferred embodiment of the invention, when the temperature of the automatic transmission fluid is below 210° F., the minimum engine speed is set to no greater than 900 revolutions per minute (rpm). When the temperature of the automatic transmission fluid is above 210° F., the minimum engine speed is set to no less than 1000 rpm. Therefore, the system operates by sensing a temperature of the automatic transmission fluid and setting a minimum engine speed of the engine based on the temperature of the automatic transmission fluid, whereby a size of the pump may be reduced as compared to known pump arrangements while still being able to supply the automatic transmission fluid to the friction elements and gear ratios to provide lubrication and to the actuators to enable the actuators to engage and disengage the friction elements in a timely and effective manner. 
         [0011]    Additional objects, features and advantages of the present invention will become more readily apparent from the following detailed description of a preferred embodiment when taken in conjunction with the drawings wherein like reference numerals refer to corresponding parts in the several views. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0012]      FIG. 1  is a diagram showing a vehicle incorporating a system for improving vehicle performance in accordance with the invention; 
           [0013]      FIG. 2  is a schematic diagram of the system in  FIG. 1 ; 
           [0014]      FIG. 3  is a basic flowchart showing a control routine employed in the system of  FIG. 1  according to a preferred embodiment of the invention; 
           [0015]      FIG. 3A  is a detailed flowchart showing another preferred embodiment of a control routine employed in the system of  FIG. 1 ; 
           [0016]      FIG. 4  is a graph showing a transmission upshift in accordance with the invention; and 
           [0017]      FIG. 5  is a graph showing a transmission downshift in accordance with the invention. 
       
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0018]    With initial reference to  FIG. 1 , there is shown an automotive vehicle  10  having a body  11  and an engine  12 . Power from engine  12  is transmitted to a transmission  18 , then to the other portions of a powertrain  20  and eventually to drive wheels  22 . Vehicle  10  is shown as a rear wheel drive vehicle but any type of powertrain arrangement, including front wheel or all wheel drive systems, could be employed. In addition, although engine  12  is shown as an internal combustion engine, but other types of drive arrangements, including hybrid drive systems, could be utilized. A controller  25  is connected to engine  12  and transmission  18  by communication lines  27  and  28  respectively. In accordance with the invention, controller  25  functions to set a minimum engine speed based on automatic fluid temperature as more fully discussed below. 
         [0019]    Transmission  18  is schematically illustrated in  FIG. 2  with controller  25 , wherein ratio changes are controlled by friction elements CL/A-CL/E acting on individual gear elements. Torque from engine  12  is distributed to torque input element  30  of hydrokinetic torque converter  32 . An impeller  34  of torque converter  32  develops turbine torque on a turbine  36  in a known fashion. Turbine torque is distributed to a turbine shaft, which is also transmission input shaft  38 . Impeller  34  is connected to a relatively small oil pump assembly  39 . 
         [0020]    Transmission  18  of  FIG. 2  includes a simple planetary gearset  40  and a compound planetary gearset  41 . Gearset  40  has a permanently fixed sun gear S 1 , a ring gear R 1  and planetary pinions P 1  rotatably supported on a carrier  42 . Transmission input shaft  38  is drivably connected to ring gear R 1 . Compound planetary gearset  41 , sometimes referred to as a Ravagineaux gearset, has a small pitch diameter sun gear S 3 , a torque output ring gear R 3 , a large pitch diameter sun gear S 2  and compound planetary pinions. The compound planetary pinions include long pinions P 2 / 3 , which drivably engage short planetary pinions P 3  and torque output ring gear R 3 . Long planetary pinions P 2 / 3  also drivably engage short planetary pinions P 3 , while short planetary pinions P 3  further engage sun gear S 3 . Planetary pinions P 2 / 3  and P 3  of gearset  41  are rotatably supported on compound carrier  46 . Ring gear R 3  is drivably connected to a torque output shaft  48 , which is drivably connected to vehicle traction wheels  22  through a differential and axle assembly  50  shown in  FIG. 1 . Gearset  40  is an underdrive ratio gearset arranged in series with respect to compound gearset  41 . Typically, transmission  18  preferably includes a lockup or torque converter bypass clutch, as shown at  58 , to directly connect transmission input shaft  30  to engine  12  after a torque converter torque multiplication mode is completed and a hydrokinetic coupling mode begins. 
         [0021]    During operation in the first four forward driving ratios, carrier P 1  is drivably connected to sun gear S 3  through shaft  58  and forward friction element CL/A. During operation in the third ratio, fifth ratio and reverse, direct friction element CL/B drivably Connects carrier  42  to shaft  59 , which is connected to large pitch diameter sun gear S 2  through shaft  60 . During operation in the fourth, fifth and sixth forward driving ratios, overdrive friction element CL/B connects turbine shaft  38  to compound carrier  46  through shaft  28 . Friction element CL/C acts as a reaction brake for sun gear  52  during operation in second and sixth forward driving ratios. During operation of the third forward driving ratio, direct friction element CL/B is applied together with forward friction element CL/A. The elements of gearset  41  then are locked together to effect a direct driving connection between shaft  58  and output shaft  48 . If friction element CL/B is applied during third ratio operation when clutch A is applied and friction element CL/C is released, a downshift from the third ratio to the second ratio would be affected as friction element CL/C is applied in synchronism with release of friction element CL/B. If friction element CL/B is applied during third ratio operation when friction element CL/A is applied and friction element CL/B is released, an upshift from the third ratio to the fourth ratio is effected as friction element CL/B is applied in synchronism with release of friction element CL/B. The torque output side of forward friction element CL/A is connected through torque transfer element  54  to the torque input side of direct friction element CL/B, during forward drive. The torque output side of direct clutch CL/B, during forward drive, is connected to shaft  60  through torque transfer element  59 . Reverse drive is established by applying low-and-reverse friction element CL/D and friction element CL/B. More details of this type of transmission arrangement are found in U.S. Pat. No. 7,216,025, which is hereby incorporated by reference. 
         [0022]    The friction elements CL (A-E) are powered by the automatic transmission fluid pumped by pump assembly  39  in accordance with instructions provided by controller  25  through communication lines  28 . Each friction element CL (A-E) has a corresponding communication channel A-E so that friction elements CL (A-E) may be controlled independently. Also, information from sensors on transmission  18 , such as an automatic fluid temperature sensor  62 , send information to controller  25  through communication lines  28 . More specifically, transmission control algorithms  70  are employed to control the shifting of gear ratios in transmission  18 , while engine control algorithms  72  operate in controller  25  in order to control engine  12 . Engine control algorithms  72  receive information from driver directed signals  75 , such as a desired speed and information from engine  12 , preferably engine speed in RPM from a speed sensor  77  and engine coolant temperature sensor, and communicate with transmission control algorithms  70 . 
         [0023]    The operation of controller  25  can be further understood with reference to the basic flow chart shown in  FIG. 3 . Initially, controller  25  determines minimum engine speeds at step  200  based on the temperature of the automatic transmission fluid. Preferably, the minimum engine speed is set to no greater than 900 rpm for temperatures below 210° F. and no less than 1000 rpm for temperatures above 210° F. However, it is desirable to prevent controller  25  from constraining the minimum engine speed unless absolutely necessary. Therefore, the minimum engine speed is preferably made a function of transmission oil temperature and engine coolant temperature, which may allow for a lower minimum engine speed as compared to a minimum engine speed determined based solely on automatic transmission fluid temperature. At step  210 , the temperature of the automatic transmission fluid is measured. Then, at step  220 , the temperature is compared to a predetermined temperature used to determine minimum engine speeds. With this information, the engine speed is altered by controller  25  during gear shifts to be at or above the minimum engine speed determined in step  200 . As a result of this method, the use of smaller oil pump assemblies with low drag is enabled. Additionally, the lower minimum engine speed results in improved fuel economy. Generally, a higher minimum engine speed required to protect transmission  18  will be invoked only when elevated transmission oil temperatures and their associated lower viscosity threaten to affect the operation of friction elements CL(AE) or provide too little lubrication as further explained below. 
         [0024]      FIG. 3A  shows a more detailed flowchart showing the operation of controller  25  according to a second preferred embodiment of the invention. Initially, at step  300 , controller  25  determines the minimum vehicle speed at which an upshift into a higher gear or gear ratio may normally occur. The minimum vehicle speed is assigned a variable name such as “minimum_upshift —— vehicle_speed”. The value determined to be the minimum vehicle speed is then stored as the variable “minimum_upshift_vehicle_speed”. Then controller  25  determines, at step  310 , whether or not the temperature of the automatic transmission fluid is high enough to require some type of shift modification. If the temperature is high enough, controller  25  proceeds to step  320  and calculates the minimum acceptable acceptable speed at which an upshift may occur in view of the measured temperature. As noted above, the variable “hot_minimum_upshift_vehicle_speed” could also be based on measuring the temperature of the automatic transmission fluid in combination with engine coolant temperature. Furthermore, the temperature used does not have to be directly measured but could also be estimated, modeled or projected. The resulting value is stored as the variable “hot_minimum_upshift_vehicle_speed”. At step  330 , controller  25  determines if “hot_minimum_upshift_vehicle_speed” is greater than “minimum_upshift_vehicle_speed” and, if so, the value for “minimum_upshift_vehicle_speed” is overwritten with the value for “hot_minimum_upshift_vehicle_speed”, which is the value that controller  25  uses for high temperature operation. The process then continues to step  350  where controller  25  determines if the current vehicle speed is greater than the “minimum_upshift_vehicle_speed” and, if so, an upshift is performed at step  360 . If not, the system does not perform an upshift and the process ends. if the transmission temperature is not high enough to require shift modification in step  310 , the process goes directly to step  350 . Likewise, if the “hot_minimum_upshift_vehicle_speed” is not greater than the “minimum_upshift_vehicle_speed” in step  330 , the process also goes directly to step  350 . Preferably, this process is conducted on a continuous basis, thus constantly monitoring the shifting process to adjust for temperature changes of the automatic transmission fluid. The process for a downshift is essentially a mirror image of the upshift strategy and therefore will not be discussed separately. 
         [0025]      FIG. 4  is a graph representing an upshift from a lower gear ratio X to a higher gear ratio Y conducted while using the method shown in  FIG. 3 . The vertical axis represents an average filtered vehicle speed before the shift, while the horizontal axis represents driver demand as derived from the position of an accelerator pedal or some other driver directed signal. A shift curve is shown that represents the transition where controller  25  will shift gears. For example, at a given driver demand, controller  25  will shift gears when the averaged filtered vehicle speed increased to above the shift curve. At a higher driver demand, the vehicle speed will be relatively higher before a shift occurs. The shift curve in accordance with the invention is significantly lower at low driver demand values than prior art shift curves, thereby enabling a lower minimum engine speed at normal automatic fluid temperatures. The prior art minimum is shown by a dashed line PA, the high temperature line H is shown just below the dashed line and the normal temperature line L is the lowest line in the graph. At high temperatures, the curve is clipped to maintain an engine speed that allows pump  42  to provide sufficient pressure to the friction elements CL (A-E) and lubrication to the transmission  18 . 
         [0026]      FIG. 5  is a graph representing a downshift from a higher gear ratio X to a lower gear ratio Y conducted while using the method shown in  FIG. 3 . The vertical axis represents driver demand as derived from the position of an accelerator pedal or some other driver detected signal, while the horizontal axis represents a predicted engine transmission speed after the gear shift. A shift curve is shown that represents the transition where controller  25  will shift gears. For example, at a given predicted engine speed after shift, controller  25  will shift gears when the driver demand increases to above the shift curve. At a higher predicted engine speed after the shift, the driver demand will be relatively higher before a shift occurs. The shift curve in accordance with the invention will always request downshifts at a minimum engine speed as represented by the dashed lines. At normal temperatures, the minimum speed is represented by dashed line L. That minimum engine speed will be higher shown by dashed lined H at higher transmission fluid temperatures to allow the pump to provide sufficient pressure to the friction elements and lubrication to the transmission. 
         [0027]    Based on the above, it should be apparent that the present invention provides for a system that regulates a minimum engine speed based on automatic transmission fluid temperature to enable a smaller sized pump to be utilized and increases fuel economy. Although described with reference to a preferred embodiment of the invention, it should be readily understood that various changes and/or modifications can be made to the invention without departing from the spirit thereof. For instance, the way the minimum engine speed is enforced may be a change in shift points depending on measured temperature of the automatic transmission fluid or the controller may simply switch gear ratios when a certain engine speed is reached, regardless of what other inputs to the controller may suggest. In general, the invention is only intended to be limited by the scope of the following claims