Title of Invention	METHOD FOR CONTROLLING HYDRAULIC LINE PRESSURE FOR COMPONENT LUBRICATION IN AN ELECTROMECHANICAL TRANSMISSION
Abstract	A method for controlling hydraulic line pressure for component lubrication in a transmission includes monitoring a speed of an engine and an electric machine, determining a minimum line pressure required to lubricate the engine based upon the speed of the engine, determining a minimum line pressure required to lubricate the electric machine based upon the speed of the electric machine, controlling a minimum line pressure of a hydraulic control system to at least satisfy a larger value of the minimum line pressures.

Title of Invention

METHOD FOR CONTROLLING HYDRAULIC LINE PRESSURE FOR COMPONENT LUBRICATION IN AN ELECTROMECHANICAL TRANSMISSION

Abstract

A method for controlling hydraulic line pressure for component lubrication in a transmission includes monitoring a speed of an engine and an electric machine, determining a minimum line pressure required to lubricate the engine based upon the speed of the engine, determining a minimum line pressure required to lubricate the electric machine based upon the speed of the electric machine, controlling a minimum line pressure of a hydraulic control system to at least satisfy a larger value of the minimum line pressures.

Full Text	METHOD AND APPARATUS TO CONTROL HYDRAULIC PRESSURE FOR COMPONENT LUBRICATION IN AN ELECTRO-MECHANICAL TRANSMISSION CROSS REFERENCE TO RELATED APPLICATIONS [0001] This application claims the benefit of U.S. Provisional Application No. 60/982,863 filed on October 26, 2007 which is hereby incorporated herein by reference. TECHNICAL FIELD [0002] This disclosure pertains to control systems for electro-mechanical transmissions. BACKGROUND [0003] The statements in this section merely provide background information related to the present disclosure and may not constitute prior art. [0004] Devices transforming electrical energy into a torque or transforming a torque into electrical energy operate with some efficiency. Some measure of the input is transformed into the output. However, in either operation, some measure of the input is lost, primarily as heat rejected to the device. [0005] Known powertrain architectures include torque-generative devices, including internal combustion engines and electric machines, which transmit torque through a transmission device to an output member. One exemplary powertrain includes a two-mode, compound-split, electro-mechanical transmission which utilizes an input member for receiving motive torque from a prime mover power source, preferably an internal combustion engine, and an output member. The output member can be operatively connected to a driveline for a motor vehicle for transmitting tractive torque thereto. Electric machines, operative as motors or generators, generate a torque input to the transmission, independently of a torque input from the internal combustion engine. The electric machines may transform vehicle kinetic energy, transmitted through the vehicle driveline, to electrical energy that is storable in an electrical energy storage device. A control system monitors various inputs from the vehicle and the operator and provides operational control of the powertrain, including controlling transmission operating state and gear shifting, controlling the torque-generative devices, and regulating the electrical power interchange among the electrical energy storage device and the electric machines to manage outputs of the transmission, including torque and rotational speed. A hydraulic control system is known to provide pressurized hydraulic fluid for a number of functions throughout the powertrain. [0006] Operation of the above devices within a hybrid powertrain vehicle require management of numerous torque bearing shafts or devices representing connections to the above mentioned engine, electrical machines, and driveline. Input torque from the engine and input torque from the electric machine or electric machines can be applied individually or cooperatively to provide output torque. Various control schemes and operational connections between the various aforementioned components of the hybrid drive system are known, and the control system must be able to engage to and disengage the various components from the transmission in order to perform the functions of the hybrid powertrain system. Engagement and disengagement are known to be accomplished within the transmission by employing selectively operable clutches. [0007] Clutches are devices well known in the art for engaging and disengaging shafts including the management of rotational velocity and torque differences between the shafts. Clutches are known in a variety of designs and control methods. One known type of clutch is a mechanical clutch operating by separating or joining two connective surfaces, for instance, clutch plates, operating, when joined, to apply frictional torque to each other. One control method for operating such a mechanical clutch includes applying the hydraulic control system implementing fluidic pressures transmitted through hydraulic lines to exert or release clamping force between the two connective surfaces. Operated thusly, the clutch is not operated in a binary manner, but rather is capable of a range of engagement states, from fully disengaged, to synchronized but not engaged, to engaged but with only minimal clamping force, to engaged with some maximum clamping force. The clamping force available to be applied to the clutch determines how much reactive torque the clutch can carry before the clutch slips. [0008] The hydraulic control system, as described above, utilizes lines filled with hydraulic fluid to selectively activate clutches within the transmission. However, the hydraulic control system is also known to perform a number of other functions in a hybrid powertrain. For example, as described above, an electric machine utilized within a hybrid powertrain generates heat. Known embodiments utilize hydraulic fluid from the hydraulic control system to cool the electric machine in a machine cooling function. Additionally, known embodiments utilize hydraulic fluid to lubricate mechanical devices, such as bearings. Also, hydraulic circuits are known to include some level of internal leakage. [0009] Hydraulic fluid is known to be pressurized within a hydraulic control system with a pump. The pump can be electrically powered or preferably mechanically driven. In addition to this first main hydraulic pump, hydraulic control systems are known to also include an auxiliary hydraulic pump. The internal impelling mechanism rotates operates at some speed, drawing hydraulic fluid from a return line and pressurizing the hydraulic control system. The supply of hydraulic flow by the pump or pumps is affected by a number of factors, including but not limited to the speed of the pumps, the back pressure exerted by the hydraulic line pressure (PLINE), and the temperature of the hydraulic fluid (TOIL). [0010] The resulting or net PLINE within the hydraulic control system is impacted by a number of factors. FIG. 1 schematically illustrates a model of factors impacting hydraulic flow in an exemplary hydraulic control system, in accordance with the present disclosure. As one having ordinary skill in the art will appreciate, conservation of mass explains that, in steady state, flow entering a system must equal the flow exiting from that system. As applied to FIG. 1, a flow of hydraulic oil is supplied to the hydraulic control system by the pumps. The flow exits the hydraulic control system through the various functions served by the hydraulic control system. This exemplary embodiment includes the following functions: hydraulic oil fills clutch mechanisms in order to provide clamping force required to lock the clutch, as described above; hydraulic oil provides cooling of the electric machines and other components as required; hydraulic oil is used to lubricate portions of the transmission; and hydraulic oil flows through leakage internal to the hydraulic circuit. PLINE describes the resulting charge of hydraulic oil maintained in the system: for any flow through a system, the resulting pressure within the system depends upon the flow resistance within the system. Higher flow resistance in the system results in higher system pressures for a given flow. Conversely, lower flow resistance in the system results in lower system pressures for a given flow. Applied to FIG. 1, PLINE or the pressure within the hydraulic control system, changes depending upon usage of the hydraulic control system. For example, filling a previously unfilled transmission clutch consumes a significant amount of flow from the hydraulic control system. The orifice leading to the clutch includes low resistance in order to draw the significant amount of hydraulic oil over a short time span. As a result, during the clutch filling process, PLINE in an otherwise unchanged hydraulic control system will reduce. Conversely, for a given set of functions served by the hydraulic control system, PLINE varies based upon the flow supplied by the pumps. For any given set of flow restrictions associated with the functions served, increased flow from the pumps will result in higher PLINE. [0011] The lubrication function served by the hydraulic control system includes some flow of hydraulic oil to the electric machine or machines utilized by the hybrid powertrain, for example, to keep a bearing from failing due to frictional forces within the bearing. Such frictional forces and the resulting stresses and heat upon the bearing increase with the speed of the device driving the bearing. Bearings are designed to work with an adequate level of lubrication to reduce the frictional forces within the bearing. If such a bearing is starved of adequate lubrication, then forces, stresses, and heat within the bearing quickly deviate from designed levels. [0012] Known control methods to lubricate devices within the hybrid powertrain include utilizing the hydraulic control system to provide a flow through a fixed orifice loop. In such an exemplary arrangement, the resulting flow to the coolant loop will increase proportionally to an increase in PLINE. Additionally, a pressure-sensitive valve is known to be utilized, wherein increasing PLINE opens the valve, lowering the flow resistance of the orifice created by the valve. As a result, flow will increase non-linearly with increasing PLINE. with extra flow resulting from an incremental increase in PLINE Such mechanical valves are beneficial because no sensor is needed, and the primary sources of error in a pressure-sensitive valve, lag and hysteresis, generally will not significant deviation from flow levels required for lubrication. [0013] As is well known in the art and as described above, lubrication required for bearings associated with operation of an electric machine increase as the rotational speed of the electric machine increases. However, as described above, the rate of hydraulic oil and, therefore, the flow of the hydraulic oil flowing to the device through a lubrication loop equipped with either a fixed orifice or a pressure-sensitive valve only increase only with PLINE. Because PLINE is frequently directly driven by an engine, and because electric machine operation is not tied to engine operation, PLINE will not necessarily increase as an electric machine speed increases. As a result, situations can occur where high electric machine speeds and low PLINE result in the electric machine not receiving sufficient lubrication. Such a condition can be avoided by designing the flow restriction of the coolant loop to provide sufficient lubrication for all foreseeable operating conditions of the electric machine, but such a design requires an excessive flow of hydraulic oil during periods when the lubrication requirements of the electric machine do not warrant the design. Additionally, valves are known to modulate flow based upon a control signal. Such control signals however are based upon sensor readings; are reactive to changes, for example, in temperature and generally include a lag time; require expensive sensors; and are subject to sensor failure. A method to control lubrication flow in a hydraulic control system by modulating PLINE based upon speeds of torque generative devices would be beneficial. SUMMARY [0014] A method for controlling hydraulic line pressure for component lubrication in an electro-mechanical transmission mechanically-operatively coupled to an internal combustion engine and an electric machine, and adapted to selectively transmit mechanical power to an output member includes monitoring a speed of the engine, monitoring a speed of the electric machine, determining a minimum line pressure required to lubricate the engine based upon the speed of the engine, determining a minimum line pressure required to lubricate the electric machine based upon the speed of the electric machine, controlling a minimum line pressure of a hydraulic control system to at least satisfy a larger value of the minimum line pressure required to lubricate the engine and the minimum line pressure required to lubricate the electric machine. BRIEF DESCRIPTION OF THE DRAWINGS [0015] One or more embodiments will now be described, by way of example, with reference to the accompanying drawings, in which: [0016] FIG. 1 schematically illustrates a model of factors impacting hydraulic flow in an exemplary hydraulic control system, in accordance with the present disclosure; [0017] FIG. 2 is a schematic diagram of an exemplary powertrain, in accordance with the present disclosure; [0018] FIG. 3 is a schematic diagram of an exemplary architecture for a control system and powertrain, in accordance with the present disclosure; [0019] FIG. 4 is a schematic diagram of a hydraulic circuit, in accordance with the present disclosure; [0020] FIG. 5 illustrates an information flow diagram describing an exemplary determination of the minimum PLINE that will meet lubrication requirements based upon an engine speed and electric machine speeds, in accordance with the present disclosure; and [0021] FIG. 6 illustrates an information flow diagram describing an exemplary determination of the minimum PLINE that will meet requirements of functions served by a hydraulic control system, in accordance with the present disclosure. DETAILED DESCRIPTION [0022] Referring now to the drawings, wherein the showings are for the purpose of illustrating certain exemplary embodiments only and not for the purpose of limiting the same, FIGS. 2 and 3 depict an exemplary electro- mechanical hybrid powertrain. The exemplary electro-mechanical hybrid powertrain in accordance with the present disclosure is depicted in FIG. 2, comprising a two-mode, compound-split, electro-mechanical hybrid transmission 10 operatively connected to an engine 14 and first and second electric machines ('MG-A') 56 and ('MG-B') 72. The engine 14 and first and second electric machines 56 and 72 each generate power which can be transmitted to the transmission 10. The power generated by the engine 14 and the first and second electric machines 56 and 72 and transmitted to the transmission 10 is described in terms of input torques, referred to herein as TI, TA, and TB respectively, and speed, referred to herein as NI, NA, and NB, respectively. [0023] The exemplary engine 14 comprises a multi-cylinder internal combustion engine selectively operative in several states to transmit torque to the transmission 10 via an input shaft 12, and can be either a spark-ignition or a compression-ignition engine. The engine 14 includes a crankshaft (not shown) operatively coupled to the input shaft 12 of the transmission 10. A rotational speed sensor 11 monitors rotational speed of the input shaft 12. Power output from the engine 14, comprising rotational speed and output torque, can differ from the input speed, NI, and the input torque, TI, to the transmission 10 due to placement of torque-consuming components on the input shaft 12 between the engine 14 and the transmission 10, e.g., a hydraulic pump (not shown) and/or a torque management device (not shown). [0024] The exemplary transmission 10 comprises three planetary-gear sets 24,26 and 28, and four selectively engageable torque-transmitting devices, i.e., clutches Cl 70, C2 62, C3 73, and C4 75. As used herein, clutches refer to any type of friction torque transfer device including single or compound plate clutches or packs, band clutches, and brakes, for example. A hydraulic control circuit 42, preferably controlled by a transmission control module (hereafter TCM') 17, is operative to control clutch states. Clutches C2 62 and C4 75 preferably comprise hydraulically-applied rotating friction clutches. Clutches Cl 70 and C3 73 preferably comprise hydraulically-controlled stationary devices that can be selectively grounded to a transmission case 68. Each of the clutches Cl 70, C2 62, C3 73, and C4 75 is preferably hydraulically applied, selectively receiving pressurized hydraulic fluid via the hydraulic control circuit 42. [0025] The first and second electric machines 56 and 72 preferably comprise three-phase AC machines, each including a stator (not shown) and a rotor (not shown), and respective resolvers 80 and 82. The motor stator for each machine is grounded to an outer portion of the transmission case 68, and includes a stator core with coiled electrical windings extending therefrom. The rotor for the first electric machine 56 is supported on a hub plate gear that is operatively attached to shaft 60 via the second planetary gear set 26. The rotor for the second electric machine 72 is fixedly attached to a sleeve shaft hub 66. [0026] Each of the resolvers 80 and 82 preferably comprises a variable reluctance device including a resolver stator (not shown) and a resolver rotor (not shown). The resolvers 80 and 82 are appropriately positioned and assembled on respective ones of the first and second electric machines 56 and 72. Stators of respective ones of the resolvers 80 and 82 are operatively connected to one of the stators for the first and second electric machines 56 and 72. The resolver rotors are operatively connected to the rotor for the corresponding first and second electric machines 56 and 72. Each of the resolvers 80 and 82 is signally and operatively connected to a transmission power inverter control module (hereafter 'TPIM') 19, and each senses and monitors rotational position of the resolver rotor relative to the resolver stator, thus monitoring rotational position of respective ones of first and second electric machines 56 and 72. Additionally, the signals output from the resolvers 80 and 82 are interpreted to provide the rotational speeds for first and second electric machines 56 and 72, i.e., NA and NB, respectively. [0027] The transmission 10 includes an output member 64, e.g. a shaft, which is operably connected to a driveline 90 for a vehicle (not shown), to provide output power, e.g., to vehicle wheels 93, one of which is shown in FIG. 2. The output power is characterized in terms of an output rotational speed, No and an output torque, To. A transmission output speed sensor 84 monitors rotational speed and rotational direction of the output member 64. Each of the vehicle wheels 93, is preferably equipped with a sensor 94 adapted to monitor wheel speed, VSS-WHL, the output of which is monitored by a control module of a distributed control module system described with respect to FIG. 3, to determine vehicle speed, and absolute and relative wheel speeds for braking control, traction control, and vehicle acceleration management. [0028] The input torques from the engine 14 and the first and second electric machines 56 and 72 (TI, TA, and TB respectively) are generated as a result of energy conversion from fuel or electrical potential stored in an electrical energy storage device (hereafter 'ESD') 74. The ESD 74 is high voltage DC- coupled to the TPIM 19 via DC transfer conductors 27. The transfer conductors 27 include a contactor switch 38. When the contactor switch 38 is closed, under normal operation, electric current can flow between the ESD 74 and the TPIM 19. When the contactor switch 38 is opened electric current flow between the ESD 74 and the TPIM 19 is interrupted. The TPIM 19 transmits electrical power to and from the first electric machine 56 by transfer conductors 29, and the TPIM 19 similarly transmits electrical power to and from the second electric machine 72 by transfer conductors 31, in response to torque commands for the first and second electric machines 56 and 72 to achieve the input torques TA and TB. Electrical current is transmitted to and from the ESD 74 in accordance with whether the ESD 74 is being charged or discharged. [0029] The TPIM 19 includes the pair of power inverters (not shown) and respective motor control modules (not shown) configured to receive the torque commands and control inverter states therefrom for providing motor drive or regeneration functionality to meet the commanded motor torques TA and TB. The power inverters comprise known complementary three-phase power electronics devices, and each includes a plurality of insulated gate bipolar transistors (not shown) for converting DC power from the ESD 74 to AC power for powering respective ones of the first and second electric machines 56 and 72, by switching at high frequencies. The insulated gate bipolar transistors form a switch mode power supply configured to receive control commands. There is typically one pair of insulated gate bipolar transistors for each phase of each of the three-phase electric machines. States of the insulated gate bipolar transistors are controlled to provide motor drive mechanical power generation or electric power regeneration functionality. The three-phase inverters receive or supply DC electric power via DC transfer conductors 27 and transform it to or from three-phase AC power, which is conducted to or from the first and second electric machines 56 and 72 for operation as motors or generators via transfer conductors 29 and 31 respectively. [0030] FIG. 3 is a schematic block diagram of the distributed control module system. The elements described hereinafter comprise a subset of an overall vehicle control architecture, and provide coordinated system control of the exemplary powertrain described in FIG. 2. The distributed control module system synthesizes pertinent information and inputs, and executes algorithms to control various actuators to achieve control objectives, including objectives related to fuel economy, emissions, performance, drivability, and protection of hardware, including batteries of ESD 74 and the first and second electric machines 56 and 72. The distributed control module system includes an engine control module (hereafter 'ECM') 23, the TCM 17, a battery pack control module (hereafter 'BPCM') 21, and the TPIM 19. A hybrid control module (hereafter 'HCP') 5 provides supervisory control and coordination of the ECM 23, the TCM 17, the BPCM 21, and the TPIM 19. A user interface CUT) 13 is operatively connected to a plurality of devices through which a vehicle operator controls or directs operation of the electro-mechanical hybrid powertrain. The devices include an accelerator pedal 113 ('AP') from which an operator torque request is determined, an operator brake pedal 112 ('BP'), a transmission gear selector 114 ('PRNDL'), and a vehicle speed cruise control (not shown). The transmission gear selector 114 may have a discrete number of operator-selectable positions, including the rotational direction of the output member 64 to enable one of a forward and a reverse direction. [0031] The aforementioned control modules communicate with other control modules, sensors, and actuators via a local area network (hereafter 'LAN') bus 6. The LAN bus 6 allows for structured communication of states of operating parameters and actuator command signals between the various control modules. The specific communication protocol utilized is application-specific. The LAN bus 6 and appropriate protocols provide for robust messaging and multi-control module interfacing between the aforementioned control modules, and other control modules providing functionality such as antilock braking, traction control, and vehicle stability. Multiple communications buses may be used to improve communications speed and provide some level of signal redundancy and integrity. Communication between individual control modules can also be effected using a direct link, e.g., a serial peripheral interface ('SPI') bus (not shown). [0032] The HCP 5 provides supervisory control of the powertrain, serving to coordinate operation of the ECM 23, TCM 17, TPIM 19, and BPCM 21. Based upon various input signals from the user interface 13 and the powertrain, including the ESD 74, the HCP 5 generates various commands, including: the operator torque request ('TO_REQ') a commanded output torque ('TCMD') to the driveline 90, an engine input torque command, clutch torques for the torque-transfer clutches Cl 70, C2 62, C3 73, C4 75 of the transmission 10; and the torque commands for the first and second electric machines 56 and 72, respectively. The TCM 17 is operatively connected to the hydraulic control circuit 42 and provides various functions including monitoring various pressure sensing devices (not shown) and generating and communicating control signals to various solenoids (not shown) thereby controlling pressure switches and control valves contained within the hydraulic control circuit 42. [0033] The ECM 23 is operatively connected to the engine 14, and functions to acquire data from sensors and control actuators of the engine 14 over a plurality of discrete lines, shown for simplicity as an aggregate bi-directional interface cable 35. The ECM 23 receives the engine input torque command from the HCP 5. The ECM 23 determines the actual engine input torque, TI, provided to the transmission 10 at that point in time based upon monitored engine speed and load, which is communicated to the HCP 5. The ECM 23 monitors input from the rotational speed sensor 11 to determine the engine input speed to the input shaft 12, which translates to the transmission input speed, NI. The ECM 23 monitors inputs from sensors (not shown) to determine states of other engine operating parameters including, e.g., a manifold pressure, engine coolant temperature, ambient air temperature, and ambient pressure. The engine load can be determined, for example, from the manifold pressure, or alternatively, from monitoring operator input to the accelerator pedal 113. The ECM 23 generates and communicates command signals to control engine actuators, including, e.g., fuel injectors, ignition modules, and throttle control modules, none of which are shown. [0034] The TCM 17 is operatively connected to the transmission 10 and monitors inputs from sensors (not shown) to determine states of transmission operating parameters. The TCM 17 generates and communicates command signals to control the transmission 10, including controlling the hydraulic control circuit 42. Inputs from the TCM 17 to the HCP 5 include estimated clutch torques for each of the clutches, i.e., Cl 70, C2 62, C3 73, and C4 75, and rotational output speed, No, of the output member 64. Other actuators and sensors may be used to provide additional information from the TCM 17 to the HCP 5 for control purposes. The TCM 17 monitors inputs from pressure switches (not shown) and selectively actuates pressure control solenoids (not shown) and shift solenoids (not shown) of the hydraulic control circuit 42 to selectively actuate the various clutches Cl 70, C2 62, C3 73, and C4 75 to achieve various transmission operating range states, as described hereinbelow. [0035] The BPCM 21 is signally connected to sensors (not shown) to monitor the ESD 74, including states of electrical current and voltage parameters, to provide information indicative of parametric states of the batteries of the ESD 74 to the HCP 5. The parametric states of the batteries preferably include battery state-of-charge, battery voltage, battery temperature, and available battery power, referred to as a range PBAT_MIN to PBAT_MAX. [0036] Each of the control modules ECM 23, TCM 17, TPIM 19 and BPCM 21 is preferably a general-purpose digital computer comprising a microprocessor or central processing unit, storage mediums comprising read only memory ('ROM'), random access memory ('RAM'), electrically programmable read only memory ('EPROM'), a high speed clock, analog to digital ('A/D') and digital to analog ('D/A') circuitry, and input/output circuitry and devices ('I/O') and appropriate signal conditioning and buffer circuitry. Each of the control modules has a set of control algorithms, comprising resident program instructions and calibrations stored in one of the storage mediums and executed to provide the respective functions of each computer. Information transfer between the control modules is preferably accomplished using the LAN bus 6 and SPI buses. The control algorithms are executed during preset loop cycles such that each algorithm is executed at least once each loop cycle. Algorithms stored in the non-volatile memory devices are executed by one of the central processing units to monitor inputs from the sensing devices and execute control and diagnostic routines to control operation of the actuators, using preset calibrations. Loop cycles are executed at regular intervals, for example each 3.125, 6.25, 12.5, 25 and 100 milliseconds during ongoing operation of the powertrain. Alternatively, algorithms may be executed in response to the occurrence of an event. [0037] The exemplary powertrain selectively operates in one of several operating range states that can be described in terms of an engine state comprising one of an engine on state ('ON') and an engine off state ('OFF'), and a transmission state comprising a plurality of fixed gears and continuously variable operating modes, described with reference to Table 1, below. Table 1 Description Engine Transmission Operating Applied State Range State Clutches MI_Eng_Off OFF EVT Mode I Cl 70 MI_Eng_On ON EVT Mode I C1 70 FG1 ON Fixed Gear Ratio 1 Cl 70 C4 75 FG2 ON Fixed Gear Ratio 2 Cl 70 C2 62 MII_Eng_Off OFF EVT Mode 11 C2 62 MII_Eng_On ON EVT Mode II C2 62 FG3 ON Fixed Gear Ratio 3 C2 62 C4 75 FG4 ON Fixed Gear Ratio 4 C2 62 C3 73 [0038] Each of the transmission operating range states is described in the table and indicates which of the specific clutches Cl 70, C2 62, C3 73, and C4 75 are applied for each of the operating range states. A first continuously variable mode, i.e., EVT Mode I, or MI, is selected by applying clutch Cl 70 only in order to "ground" the outer gear member of the third planetary gear set 28. The engine state can be one of ON ('MI_Eng_On') or OFF ('MI_Eng_Off). A second continuously variable mode, i.e., EVT Mode II, or MII, is selected by applying clutch C2 62 only to connect the shaft 60 to the carrier of the third planetary gear set 28. The engine state can be one of ON ('MII_Eng_On') or OFF ('MII_Eng_Off). For purposes of this description, when the engine state is OFF, the engine input speed is equal to zero revolutions per minute ('RPM'), i.e., the engine crankshaft is not rotating. A fixed gear operation provides a fixed ratio operation of input-to-output speed of the transmission 10, i.e., NI/No, is achieved. A first fixed gear operation ('FG1') is selected by applying clutches Cl 70 and C4 75. A second fixed gear operation ('FG2') is selected by applying clutches Cl 70 and C2 62. A third fixed gear operation ('FG3') is selected by applying clutches C2 62 and C4 75. A fourth fixed gear operation ('FG4') is selected by applying clutches C2 62 and C3 73. The fixed ratio operation of input-to-output speed increases with increased fixed gear operation due to decreased gear ratios in the planetary gears 24, 26, and 28. The rotational speeds of the first and second electric machines 56 and 72, NA and NB respectively, are dependent on internal rotation of the mechanism as defined by the clutching and are proportional to the input speed measured at the input shaft 12. [0039] In response to operator input via the accelerator pedal 113 and brake pedal 112 as captured by the user interface 13, the HCP 5 and one or more of the other control modules determine the commanded output torque, TCMD, intended to meet the operator torque request, TO_REQ, to be executed at the output member 64 and transmitted to the driveline 90. Final vehicle acceleration is affected by other factors including, e.g., road load, road grade, and vehicle mass. The operating range state is determined for the transmission 10 based upon a variety of operating characteristics of the powertrain. This includes the operator torque request, communicated through the accelerator pedal 113 and brake pedal 112 to the user interface 13 as previously described. The operating range state may be predicated on a powertrain torque demand caused by a command to operate the first and second electric machines 56 and 72 in an electrical energy generating mode or in a torque generating mode. The operating range state can be determined by an optimization algorithm or routine which determines optimum system efficiency based upon operator demand for power, battery state of charge, and energy efficiencies of the engine 14 and the first and second electric machines 56 and 72. The control system manages torque inputs from the engine 14 and the first and second electric machines 56 and 72 based upon an outcome of the executed optimization routine, and system efficiencies are optimized thereby, to manage fuel economy and battery charging. Furthermore, operation can be determined based upon a fault in a component or system. The HCP 5 monitors the torque- generative devices, and determines the power output from the transmission 10 required to achieve the desired output torque to meet the operator torque request. As should be apparent from the description above, the ESD 74 and the first and second electric machines 56 and 72 are electrically-operatively coupled for power flow therebetween. Furthermore, the engine 14, the first and second electric machines 56 and 72, and the electro-mechanical transmission 10 are mechanically-operatively coupled to transmit power therebetween to generate a power flow to the output member 64. [0040] FIG. 4 depicts a schematic diagram of the hydraulic control circuit 42 for controlling flow of hydraulic fluid in the exemplary transmission. A main hydraulic pump 88 is driven off the input shaft 12 from the engine 14, and an auxiliary pump 110 controlled by the TPIM 19 to provide pressurized fluid to the hydraulic control circuit 42 through valve 140. The auxiliary pump 110 preferably comprises an electrically-powered pump of an appropriate size and capacity to provide sufficient flow of pressurized hydraulic fluid into the hydraulic control circuit 42 when operational. The hydraulic control circuit 42 selectively distributes hydraulic pressure to a plurality of devices, including the torque-transfer clutches Cl 70, C2 62, C3 73, and C4 75, active cooling circuits for the first and second electric machines 56 and 72 (not shown), and a base cooling circuit for cooling and lubricating the transmission 10 via passages 142, 144 (not depicted in detail). As previously stated, the TCM 17 actuates the various clutches to achieve one of the transmission operating range states through selective actuation of hydraulic circuit flow control devices comprising variable pressure control solenoids ('PCS') PCS1 108, PCS2 114, PCS3 112, PCS4 116 and solenoid-controlled flow management valves, X-valve 119 and Y-valve 121. The hydraulic control circuit 42 is fluidly connected to pressure switches PS1, PS2, PS3, and PS4 via passages 122, 124, 126, and 128, respectively. The pressure control solenoid PCS1 108 has a control position of normally high and is operative to modulate the magnitude of fluidic pressure in the hydraulic circuit through fluidic interaction with controllable pressure regulator 107 and spool valve 109. The controllable pressure regulator 107 and spool valve 109 interact with PCS1 108 to control hydraulic pressure in the hydraulic control circuit 42 over a range of pressures and may provide additional functionality for the hydraulic control circuit 42. Pressure control solenoid PCS3 112 has a control position of normally high, and is fluidly connected to spool valve 113 and operative to effect flow therethrough when actuated. Spool valve 113 is fluidly connected to pressure switch PS3 via passage 126. Pressure control solenoid PCS2 114 has a control position of normally high, and is fluidly connected to spool valve 115 and operative to effect flow therethrough when actuated. Spool valve 115 is fluidly connected to pressure switch PS2 via passage 124. Pressure control solenoid PCS4 116 has a control position of normally low, and is fluidly connected to spool valve 117 and operative to effect flow therethrough when actuated. Spool valve 117 is fluidly connected to pressure switch PS4 via passage 128. [0041] The X-Valve 119 and Y-Valve 121 each comprise flow management valves controlled by solenoids 118, 120, respectively, in the exemplary system, and have control states of High (' 1') and Low ('0'). The control states refer to positions of each valve to which control flow to different devices in the hydraulic control circuit 42 and the transmission 10. The X-valve 119 is operative to direct pressurized fluid to clutches C3 73 and C4 75 and cooling systems for stators of the first and second electric machines 56 and 72 via fluidic passages 136, 138, 144, 142 respectively, depending upon the source of the fluidic input, as is described hereinafter. The Y-valve 121 is operative to direct pressurized fluid to clutches Cl 70 and C2 62 via fluidic passages 132 and 134 respectively, depending upon the source of the fluidic input, as is described hereinafter. The Y-valve 121 is fluidly connected to pressure switch PS1 via passage 122. [0042] The hydraulic control circuit 42 includes a base cooling circuit for providing hydraulic fluid to cool the stators of the first and second electric machines 56 and 72. The base cooling circuit includes fluid conduits from the valve 140 flowing directly to a flow restrictor which leads to fluidic passage 144 leading to the base cooling circuit for the stator of the first electric machine 56, and to a flow restrictor which leads to fluidic passage 142 leading to the base cooling circuit for the stator of the second electric machine 72. Active cooling of stators for the first and second electric machines 56 and 72 is effected by selective actuation of pressure control solenoids PCS2 114, PCS3 112 and PCS4 116 and solenoid-controlled flow management valves X- valve 119 and Y-valve 121, which leads to flow of hydraulic fluid around the selected stator and permits heat to be transferred therebetween, primarily through conduction. [0043] An exemplary logic table to accomplish control of the exemplary hydraulic control circuit 42 to control operation of the transmission 10 in one of the transmission operating range states is provided with reference to Table 2, below. Table 2 X- Y- PCS1 PCS2 PCS3 PCS4 Valve Valve Logic Logic Transmis No C2 Normal Normal Normal Normal -sion Latch Latch High High High Low Operating Range State EVT 0 0 Line MG-B Cl MG-A Model Modul- Stator Stator ation Cool Cool EVT 0 1 Line C2 MG-B MG-A Mode II Modul- Stator Stator ation Cool Cool Low 1 0 Line C2 Cl C4 Range Modul- ation High 1 1 Line C2 C3 C4 Range Modul- ation [0044] A Low Range is defined as a transmission operating range state comprising one of the first continuously variable mode and the first and second fixed gear operations. A High Range is defined as a transmission operating range state comprising one of the second continuously variable mode and the third and fourth fixed gear operations. Selective control of the X-valve 119 and the Y-valve 121 and actuation of the solenoids PCS2 112, PCS3 114, PCS4 116 facilitate flow of hydraulic fluid to actuate clutches Cl 70, C2 63, C3 73, and C4 75, and provide cooling for the stators the first and second electric machines 56 and 72. [0045] In operation, a transmission operating range state, i.e. one of the fixed gear and continuously variable mode operations, is selected for the exemplary correlation between PLINE, the determinative factor in flow through the coolant loop, and the cooling load or cooling capacity required by the operation of the electric machine or machines. As a result, it is preferable to control the flow through the coolant loop based upon the cooling requirements of the electric machine. A method is described to control electric machine cooling by modulating PLINE based upon electric machine cooling requirements predicted by electric machine speeds. [0047] FIG. 5 illustrates an information flow diagram describing an exemplary determination of the minimum PLINE that will meet lubrication requirements based upon an engine speed and electric machine speeds, in accordance with the present disclosure. Control system 200 is depicted including input speed to minimum pressure conversion blocks 210, 220, and 230 and max block 240. The pictured system is useful to monitor a hybrid powertrain consisting of an engine and a first and second electric machine, all requiring lubrication supplied by the hydraulic control system. However, it will be appreciated that the number of input can be modulated for a system utilizing a single electric machine or more than two electric machines, and the disclosure is not intended to be limited to the specific embodiments described herein. Minimum pressure conversion blocks 210, 220, and 230 monitor inputs NI, NA, and NB, respectively. Each conversion block utilizes a look-up table or an algorithm to determine a minimum PLINE or PMIN required to supply lubrication to each respective torque generative device. These PMIN values are provided as input to max block 240, and the maximum PMIN is utilized to provide the minimum PLINE required to provide adequate lubrication or PMIN LUBE. [0048] As described above, the hydraulic control system provides a flow of hydraulic oil to a number of functions. The method described above provides PMIN LUBE to a control system operating hydraulic pumps and modulating service of flow to the various functions in order to maintain a required PLINE. FIG. 6 illustrates an information flow diagram describing an exemplary determination of the minimum PLINE that will meet requirements of functions served by a hydraulic control system, in accordance with the present disclosure. In addition to PMIN LUBE, PMIN terms are provided for each of the other functions, including, in this exemplary embodiment, clutch operation, a base cooling loop, and an active cooling loop. Returning to FIG. 6, control system 300 includes max block 302 and max block 304. Max block 304 operates by methods described above and provides a PMIN LUBE. By other means known in the art, a PMIN CLUTCH, PMIN BASE COOLING, PMIN ACTIVE COOLING are additionally provided as inputs to max block 302. Among the various PMIN terms received as inputs to max block 302, the highest value is selected and is utilized to control the hydraulic control system and the included hydraulic pumps. [0049] The measurements and calculations required to determine the various terms described above are performed cyclically, with the operations occurring in a loop or a combination of loops. As will be appreciated by one having ordinary skill in the art, sample rates will vary and are influenced by speeds of the computerized processors involved, the required sample rates for accurate control of PLINE, and various other factors. [0050] It is understood that modifications are allowable within the scope of the disclosure. The disclosure has been described with specific reference to the preferred embodiments and modifications thereto. Further modifications and alterations may occur to others upon reading and understanding the specification. It is intended to include all such modifications and alterations insofar as they come within the scope of the disclosure. CLAIMS 1. Method for controlling hydraulic line pressure for component lubrication in an electro-mechanical transmission mechanically-operatively coupled to an internal combustion engine and an electric machine, and adapted to selectively transmit mechanical power to an output member, said method comprising: monitoring a speed of said engine; monitoring a speed of said electric machine; determining a minimum line pressure required to lubricate said engine based upon said speed of said engine; determining a minimum line pressure required to lubricate said electric machine based upon said speed of said electric machine; and controlling a minimum line pressure of a hydraulic control system to at least satisfy a larger value of said minimum line pressure required to lubricate said engine and said minimum line pressure required to lubricate said electric machine. 2. The method of claim 1, further comprising: monitoring a speed of a second electric machine; determining a minimum line pressure required to lubricate said second electric machine based upon said speed of said second electric machine; and controlling said minimum line pressure of a hydraulic control system to at least satisfy a largest value of said minimum line pressure required to lubricate said engine, said minimum line pressure required to lubricate said electric machine, and said minimum line pressure required to lubricate said second electric machine. 3. The method of claim 2, wherein controlling said minimum line pressure of a hydraulic control system comprises: monitoring a minimum line pressure required to operate clutches within said transmission; monitoring a minimum line pressure require to cool said electric machine and said second electric machine; and selecting said minimum line pressure of a hydraulic control system based upon a largest value of said minimum line pressure required to lubricate said engine, lubricate said electric machine, lubricate said second electric machine, operate clutches within said transmission, and cool said electric machine and said second electric machine. 4. The method of claim 1, wherein controlling said minimum line pressure of a hydraulic control system comprises: monitoring a minimum line pressure required to operate clutches within said transmission; monitoring a minimum line pressure required to cool said electric machine and said second electric machine; and selecting said minimum line pressure of a hydraulic control system based upon a largest value of said minimum line pressure required to lubricate said engine, lubricate said electric machine, operate clutches within said transmission, and cool said electric machine and said second electric machine. 5. A method for maintaining a minimum hydraulic line pressure for component lubrication in a hybrid powertrain comprising an internal combustion engine and an electric machine transmitting mechanical power to an output member, the method comprising: monitoring a speed of said engine; monitoring a speed of said electric machine; determining a minimum line pressure required to lubricate said engine based upon said speed of said engine; determining a minimum line pressure required to lubricate said electric machine based upon said speed of said electric machine; comparing said minimum line pressure required to lubricate said engine and said minimum line pressure required to lubricate said electric machine to find a greater of said minimum line pressures; selecting a minimum line pressure for lubrication based upon said comparing; and controlling a minimum line pressure of a hydraulic control system based upon said minimum line pressure for lubrication. 6. The method of claim 5, further comprising: monitoring a speed of a second electric machine; and determining a minimum line pressure required to lubricate said second electric machine based upon said speed of said second electric machine; and wherein said comparing further comprises comparing said minimum line pressures to find a greatest of said minimum line pressures required to lubricate said engine, lubricate said electric machine, and lubricate said second electric machine. 7. The method of claim 6, wherein controlling said minimum line pressure of a hydraulic control system comprises: monitoring a minimum line pressure required to operate other functions served by said hydraulic control system; and selecting said minimum line pressure of a hydraulic control system based upon a larger pressure of said minimum line pressure for lubrication and said minimum line pressure required to operate other functions served by said hydraulic control system. 8. The method of claim 5, wherein controlling said minimum line pressure of a hydraulic control system comprises: monitoring a minimum line pressure required to operate other functions served by said hydraulic control system; and selecting said minimum line pressure of a hydraulic control system based upon the larger pressure of said minimum line pressure for lubrication and said minimum line pressure required to operate other functions served by said hydraulic control system. 9. Apparatus for controlling hydraulic line pressure for component lubrication in an electro-mechanical transmission mechanically- operatively coupled to an internal combustion engine and first and second electric machines, and adapted to selectively transmit mechanical power to an output member, said apparatus comprising: a main hydraulic pump mechanically connected to said engine; an electrically powered auxiliary hydraulic pump; and a hydraulic control system operatively connected to said main hydraulic pump, said auxiliary hydraulic pump, and a lubrication circuit providing a flow of hydraulic oil to said engine, said first electric machine, and said second electric machine; wherein said hydraulic control system includes logic monitoring a speed of said engine, a speed of said first electric machine, and a speed of a second electric machine, determining a minimum line pressure required for lubrication based upon said speeds, and controlling said main hydraulic pump and said auxiliary hydraulic pump based upon said minimum line pressure required for lubrication. 10. The apparatus of claim 9, wherein hydraulic control system comprises a circuit providing a substantially fixed flow resistance at a connection to said lubrication circuit. 11. The apparatus of claim 9, wherein hydraulic control system further includes logic controlling functions served by said hydraulic control system based upon said minimum line pressure required for lubrication. A method for controlling hydraulic line pressure for component lubrication in a transmission includes monitoring a speed of an engine and an electric machine, determining a minimum line pressure required to lubricate the engine based upon the speed of the engine, determining a minimum line pressure required to lubricate the electric machine based upon the speed of the electric machine, controlling a minimum line pressure of a hydraulic control system to at least satisfy a larger value of the minimum line pressures.

Full Text

METHOD AND APPARATUS TO CONTROL HYDRAULIC PRESSURE
FOR COMPONENT LUBRICATION IN AN ELECTRO-MECHANICAL
TRANSMISSION
CROSS REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of U.S. Provisional Application
No. 60/982,863 filed on October 26, 2007 which is hereby incorporated herein
by reference.
TECHNICAL FIELD
[0002] This disclosure pertains to control systems for electro-mechanical
transmissions.
BACKGROUND
[0003] The statements in this section merely provide background
information related to the present disclosure and may not constitute prior art.
[0004] Devices transforming electrical energy into a torque or transforming a
torque into electrical energy operate with some efficiency. Some measure of
the input is transformed into the output. However, in either operation, some
measure of the input is lost, primarily as heat rejected to the device.
[0005] Known powertrain architectures include torque-generative devices,
including internal combustion engines and electric machines, which transmit
torque through a transmission device to an output member. One exemplary
powertrain includes a two-mode, compound-split, electro-mechanical

transmission which utilizes an input member for receiving motive torque from
a prime mover power source, preferably an internal combustion engine, and an
output member. The output member can be operatively connected to a
driveline for a motor vehicle for transmitting tractive torque thereto. Electric
machines, operative as motors or generators, generate a torque input to the
transmission, independently of a torque input from the internal combustion
engine. The electric machines may transform vehicle kinetic energy,
transmitted through the vehicle driveline, to electrical energy that is storable in
an electrical energy storage device. A control system monitors various inputs
from the vehicle and the operator and provides operational control of the
powertrain, including controlling transmission operating state and gear
shifting, controlling the torque-generative devices, and regulating the electrical
power interchange among the electrical energy storage device and the electric
machines to manage outputs of the transmission, including torque and
rotational speed. A hydraulic control system is known to provide pressurized
hydraulic fluid for a number of functions throughout the powertrain.
[0006] Operation of the above devices within a hybrid powertrain vehicle
require management of numerous torque bearing shafts or devices
representing connections to the above mentioned engine, electrical machines,
and driveline. Input torque from the engine and input torque from the electric
machine or electric machines can be applied individually or cooperatively to
provide output torque. Various control schemes and operational connections
between the various aforementioned components of the hybrid drive system
are known, and the control system must be able to engage to and disengage the
various components from the transmission in order to perform the functions of

the hybrid powertrain system. Engagement and disengagement are known to
be accomplished within the transmission by employing selectively operable
clutches.
[0007] Clutches are devices well known in the art for engaging and
disengaging shafts including the management of rotational velocity and torque
differences between the shafts. Clutches are known in a variety of designs and
control methods. One known type of clutch is a mechanical clutch operating
by separating or joining two connective surfaces, for instance, clutch plates,
operating, when joined, to apply frictional torque to each other. One control
method for operating such a mechanical clutch includes applying the hydraulic
control system implementing fluidic pressures transmitted through hydraulic
lines to exert or release clamping force between the two connective surfaces.
Operated thusly, the clutch is not operated in a binary manner, but rather is
capable of a range of engagement states, from fully disengaged, to
synchronized but not engaged, to engaged but with only minimal clamping
force, to engaged with some maximum clamping force. The clamping force
available to be applied to the clutch determines how much reactive torque the
clutch can carry before the clutch slips.
[0008] The hydraulic control system, as described above, utilizes lines filled
with hydraulic fluid to selectively activate clutches within the transmission.
However, the hydraulic control system is also known to perform a number of
other functions in a hybrid powertrain. For example, as described above, an
electric machine utilized within a hybrid powertrain generates heat. Known
embodiments utilize hydraulic fluid from the hydraulic control system to cool
the electric machine in a machine cooling function. Additionally, known

embodiments utilize hydraulic fluid to lubricate mechanical devices, such as
bearings. Also, hydraulic circuits are known to include some level of internal
leakage.
[0009] Hydraulic fluid is known to be pressurized within a hydraulic control
system with a pump. The pump can be electrically powered or preferably
mechanically driven. In addition to this first main hydraulic pump, hydraulic
control systems are known to also include an auxiliary hydraulic pump. The
internal impelling mechanism rotates operates at some speed, drawing
hydraulic fluid from a return line and pressurizing the hydraulic control
system. The supply of hydraulic flow by the pump or pumps is affected by a
number of factors, including but not limited to the speed of the pumps, the
back pressure exerted by the hydraulic line pressure (PLINE), and the
temperature of the hydraulic fluid (TOIL).
[0010] The resulting or net PLINE within the hydraulic control system is
impacted by a number of factors. FIG. 1 schematically illustrates a model of
factors impacting hydraulic flow in an exemplary hydraulic control system, in
accordance with the present disclosure. As one having ordinary skill in the art
will appreciate, conservation of mass explains that, in steady state, flow
entering a system must equal the flow exiting from that system. As applied to
FIG. 1, a flow of hydraulic oil is supplied to the hydraulic control system by
the pumps. The flow exits the hydraulic control system through the various
functions served by the hydraulic control system. This exemplary
embodiment includes the following functions: hydraulic oil fills clutch
mechanisms in order to provide clamping force required to lock the clutch, as
described above; hydraulic oil provides cooling of the electric machines and

other components as required; hydraulic oil is used to lubricate portions of the
transmission; and hydraulic oil flows through leakage internal to the hydraulic
circuit. PLINE describes the resulting charge of hydraulic oil maintained in the
system: for any flow through a system, the resulting pressure within the
system depends upon the flow resistance within the system. Higher flow
resistance in the system results in higher system pressures for a given flow.
Conversely, lower flow resistance in the system results in lower system
pressures for a given flow. Applied to FIG. 1, PLINE or the pressure within the
hydraulic control system, changes depending upon usage of the hydraulic
control system. For example, filling a previously unfilled transmission clutch
consumes a significant amount of flow from the hydraulic control system.
The orifice leading to the clutch includes low resistance in order to draw the
significant amount of hydraulic oil over a short time span. As a result, during
the clutch filling process, PLINE in an otherwise unchanged hydraulic control
system will reduce. Conversely, for a given set of functions served by the
hydraulic control system, PLINE varies based upon the flow supplied by the
pumps. For any given set of flow restrictions associated with the functions
served, increased flow from the pumps will result in higher PLINE.
[0011] The lubrication function served by the hydraulic control system
includes some flow of hydraulic oil to the electric machine or machines
utilized by the hybrid powertrain, for example, to keep a bearing from failing
due to frictional forces within the bearing. Such frictional forces and the
resulting stresses and heat upon the bearing increase with the speed of the
device driving the bearing. Bearings are designed to work with an adequate
level of lubrication to reduce the frictional forces within the bearing. If such a

bearing is starved of adequate lubrication, then forces, stresses, and heat
within the bearing quickly deviate from designed levels.
[0012] Known control methods to lubricate devices within the hybrid
powertrain include utilizing the hydraulic control system to provide a flow
through a fixed orifice loop. In such an exemplary arrangement, the resulting
flow to the coolant loop will increase proportionally to an increase in PLINE.
Additionally, a pressure-sensitive valve is known to be utilized, wherein
increasing PLINE opens the valve, lowering the flow resistance of the orifice
created by the valve. As a result, flow will increase non-linearly with
increasing PLINE. with extra flow resulting from an incremental increase in
PLINE Such mechanical valves are beneficial because no sensor is needed, and
the primary sources of error in a pressure-sensitive valve, lag and hysteresis,
generally will not significant deviation from flow levels required for
lubrication.
[0013] As is well known in the art and as described above, lubrication
required for bearings associated with operation of an electric machine increase
as the rotational speed of the electric machine increases. However, as
described above, the rate of hydraulic oil and, therefore, the flow of the
hydraulic oil flowing to the device through a lubrication loop equipped with
either a fixed orifice or a pressure-sensitive valve only increase only with
PLINE. Because PLINE is frequently directly driven by an engine, and because
electric machine operation is not tied to engine operation, PLINE will not
necessarily increase as an electric machine speed increases. As a result,
situations can occur where high electric machine speeds and low PLINE result
in the electric machine not receiving sufficient lubrication. Such a condition

can be avoided by designing the flow restriction of the coolant loop to provide
sufficient lubrication for all foreseeable operating conditions of the electric
machine, but such a design requires an excessive flow of hydraulic oil during
periods when the lubrication requirements of the electric machine do not
warrant the design. Additionally, valves are known to modulate flow based
upon a control signal. Such control signals however are based upon sensor
readings; are reactive to changes, for example, in temperature and generally
include a lag time; require expensive sensors; and are subject to sensor failure.
A method to control lubrication flow in a hydraulic control system by
modulating PLINE based upon speeds of torque generative devices would be
beneficial.
SUMMARY
[0014] A method for controlling hydraulic line pressure for component
lubrication in an electro-mechanical transmission mechanically-operatively
coupled to an internal combustion engine and an electric machine, and adapted
to selectively transmit mechanical power to an output member includes
monitoring a speed of the engine, monitoring a speed of the electric machine,
determining a minimum line pressure required to lubricate the engine based
upon the speed of the engine, determining a minimum line pressure required to
lubricate the electric machine based upon the speed of the electric machine,
controlling a minimum line pressure of a hydraulic control system to at least
satisfy a larger value of the minimum line pressure required to lubricate the
engine and the minimum line pressure required to lubricate the electric
machine.

BRIEF DESCRIPTION OF THE DRAWINGS
[0015] One or more embodiments will now be described, by way of
example, with reference to the accompanying drawings, in which:
[0016] FIG. 1 schematically illustrates a model of factors impacting
hydraulic flow in an exemplary hydraulic control system, in accordance with
the present disclosure;
[0017] FIG. 2 is a schematic diagram of an exemplary powertrain, in
accordance with the present disclosure;
[0018] FIG. 3 is a schematic diagram of an exemplary architecture for a
control system and powertrain, in accordance with the present disclosure;
[0019] FIG. 4 is a schematic diagram of a hydraulic circuit, in accordance
with the present disclosure;
[0020] FIG. 5 illustrates an information flow diagram describing an
exemplary determination of the minimum PLINE that will meet lubrication
requirements based upon an engine speed and electric machine speeds, in
accordance with the present disclosure; and
[0021] FIG. 6 illustrates an information flow diagram describing an
exemplary determination of the minimum PLINE that will meet requirements of
functions served by a hydraulic control system, in accordance with the present
disclosure.
DETAILED DESCRIPTION
[0022] Referring now to the drawings, wherein the showings are for the
purpose of illustrating certain exemplary embodiments only and not for the

purpose of limiting the same, FIGS. 2 and 3 depict an exemplary electro-
mechanical hybrid powertrain. The exemplary electro-mechanical hybrid
powertrain in accordance with the present disclosure is depicted in FIG. 2,
comprising a two-mode, compound-split, electro-mechanical hybrid
transmission 10 operatively connected to an engine 14 and first and second
electric machines ('MG-A') 56 and ('MG-B') 72. The engine 14 and first and
second electric machines 56 and 72 each generate power which can be
transmitted to the transmission 10. The power generated by the engine 14 and
the first and second electric machines 56 and 72 and transmitted to the
transmission 10 is described in terms of input torques, referred to herein as TI,
TA, and TB respectively, and speed, referred to herein as NI, NA, and NB,
respectively.
[0023] The exemplary engine 14 comprises a multi-cylinder internal
combustion engine selectively operative in several states to transmit torque to
the transmission 10 via an input shaft 12, and can be either a spark-ignition or
a compression-ignition engine. The engine 14 includes a crankshaft (not
shown) operatively coupled to the input shaft 12 of the transmission 10. A
rotational speed sensor 11 monitors rotational speed of the input shaft 12.
Power output from the engine 14, comprising rotational speed and output
torque, can differ from the input speed, NI, and the input torque, TI, to the
transmission 10 due to placement of torque-consuming components on the
input shaft 12 between the engine 14 and the transmission 10, e.g., a hydraulic
pump (not shown) and/or a torque management device (not shown).
[0024] The exemplary transmission 10 comprises three planetary-gear sets
24,26 and 28, and four selectively engageable torque-transmitting devices,

i.e., clutches Cl 70, C2 62, C3 73, and C4 75. As used herein, clutches refer
to any type of friction torque transfer device including single or compound
plate clutches or packs, band clutches, and brakes, for example. A hydraulic
control circuit 42, preferably controlled by a transmission control module
(hereafter TCM') 17, is operative to control clutch states. Clutches C2 62 and
C4 75 preferably comprise hydraulically-applied rotating friction clutches.
Clutches Cl 70 and C3 73 preferably comprise hydraulically-controlled
stationary devices that can be selectively grounded to a transmission case 68.
Each of the clutches Cl 70, C2 62, C3 73, and C4 75 is preferably
hydraulically applied, selectively receiving pressurized hydraulic fluid via the
hydraulic control circuit 42.
[0025] The first and second electric machines 56 and 72 preferably comprise
three-phase AC machines, each including a stator (not shown) and a rotor (not
shown), and respective resolvers 80 and 82. The motor stator for each
machine is grounded to an outer portion of the transmission case 68, and
includes a stator core with coiled electrical windings extending therefrom.
The rotor for the first electric machine 56 is supported on a hub plate gear that
is operatively attached to shaft 60 via the second planetary gear set 26. The
rotor for the second electric machine 72 is fixedly attached to a sleeve shaft
hub 66.
[0026] Each of the resolvers 80 and 82 preferably comprises a variable
reluctance device including a resolver stator (not shown) and a resolver rotor
(not shown). The resolvers 80 and 82 are appropriately positioned and
assembled on respective ones of the first and second electric machines 56 and
72. Stators of respective ones of the resolvers 80 and 82 are operatively

connected to one of the stators for the first and second electric machines 56
and 72. The resolver rotors are operatively connected to the rotor for the
corresponding first and second electric machines 56 and 72. Each of the
resolvers 80 and 82 is signally and operatively connected to a transmission
power inverter control module (hereafter 'TPIM') 19, and each senses and
monitors rotational position of the resolver rotor relative to the resolver stator,
thus monitoring rotational position of respective ones of first and second
electric machines 56 and 72. Additionally, the signals output from the
resolvers 80 and 82 are interpreted to provide the rotational speeds for first
and second electric machines 56 and 72, i.e., NA and NB, respectively.
[0027] The transmission 10 includes an output member 64, e.g. a shaft,
which is operably connected to a driveline 90 for a vehicle (not shown), to
provide output power, e.g., to vehicle wheels 93, one of which is shown in
FIG. 2. The output power is characterized in terms of an output rotational
speed, No and an output torque, To. A transmission output speed sensor 84
monitors rotational speed and rotational direction of the output member 64.
Each of the vehicle wheels 93, is preferably equipped with a sensor 94 adapted
to monitor wheel speed, VSS-WHL, the output of which is monitored by a
control module of a distributed control module system described with respect
to FIG. 3, to determine vehicle speed, and absolute and relative wheel speeds
for braking control, traction control, and vehicle acceleration management.
[0028] The input torques from the engine 14 and the first and second electric
machines 56 and 72 (TI, TA, and TB respectively) are generated as a result of
energy conversion from fuel or electrical potential stored in an electrical
energy storage device (hereafter 'ESD') 74. The ESD 74 is high voltage DC-

coupled to the TPIM 19 via DC transfer conductors 27. The transfer
conductors 27 include a contactor switch 38. When the contactor switch 38 is
closed, under normal operation, electric current can flow between the ESD 74
and the TPIM 19. When the contactor switch 38 is opened electric current
flow between the ESD 74 and the TPIM 19 is interrupted. The TPIM 19
transmits electrical power to and from the first electric machine 56 by transfer
conductors 29, and the TPIM 19 similarly transmits electrical power to and
from the second electric machine 72 by transfer conductors 31, in response to
torque commands for the first and second electric machines 56 and 72 to
achieve the input torques TA and TB. Electrical current is transmitted to and
from the ESD 74 in accordance with whether the ESD 74 is being charged or
discharged.
[0029] The TPIM 19 includes the pair of power inverters (not shown) and
respective motor control modules (not shown) configured to receive the torque
commands and control inverter states therefrom for providing motor drive or
regeneration functionality to meet the commanded motor torques TA and TB.
The power inverters comprise known complementary three-phase power
electronics devices, and each includes a plurality of insulated gate bipolar
transistors (not shown) for converting DC power from the ESD 74 to AC
power for powering respective ones of the first and second electric machines
56 and 72, by switching at high frequencies. The insulated gate bipolar
transistors form a switch mode power supply configured to receive control
commands. There is typically one pair of insulated gate bipolar transistors for
each phase of each of the three-phase electric machines. States of the
insulated gate bipolar transistors are controlled to provide motor drive

mechanical power generation or electric power regeneration functionality.
The three-phase inverters receive or supply DC electric power via DC transfer
conductors 27 and transform it to or from three-phase AC power, which is
conducted to or from the first and second electric machines 56 and 72 for
operation as motors or generators via transfer conductors 29 and 31
respectively.
[0030] FIG. 3 is a schematic block diagram of the distributed control module
system. The elements described hereinafter comprise a subset of an overall
vehicle control architecture, and provide coordinated system control of the
exemplary powertrain described in FIG. 2. The distributed control module
system synthesizes pertinent information and inputs, and executes algorithms
to control various actuators to achieve control objectives, including objectives
related to fuel economy, emissions, performance, drivability, and protection of
hardware, including batteries of ESD 74 and the first and second electric
machines 56 and 72. The distributed control module system includes an
engine control module (hereafter 'ECM') 23, the TCM 17, a battery pack
control module (hereafter 'BPCM') 21, and the TPIM 19. A hybrid control
module (hereafter 'HCP') 5 provides supervisory control and coordination of
the ECM 23, the TCM 17, the BPCM 21, and the TPIM 19. A user interface
CUT) 13 is operatively connected to a plurality of devices through which a
vehicle operator controls or directs operation of the electro-mechanical hybrid
powertrain. The devices include an accelerator pedal 113 ('AP') from which
an operator torque request is determined, an operator brake pedal 112 ('BP'), a
transmission gear selector 114 ('PRNDL'), and a vehicle speed cruise control
(not shown). The transmission gear selector 114 may have a discrete number

of operator-selectable positions, including the rotational direction of the output
member 64 to enable one of a forward and a reverse direction.
[0031] The aforementioned control modules communicate with other control
modules, sensors, and actuators via a local area network (hereafter 'LAN') bus
6. The LAN bus 6 allows for structured communication of states of operating
parameters and actuator command signals between the various control
modules. The specific communication protocol utilized is application-specific.
The LAN bus 6 and appropriate protocols provide for robust messaging and
multi-control module interfacing between the aforementioned control
modules, and other control modules providing functionality such as antilock
braking, traction control, and vehicle stability. Multiple communications
buses may be used to improve communications speed and provide some level
of signal redundancy and integrity. Communication between individual
control modules can also be effected using a direct link, e.g., a serial
peripheral interface ('SPI') bus (not shown).
[0032] The HCP 5 provides supervisory control of the powertrain, serving to
coordinate operation of the ECM 23, TCM 17, TPIM 19, and BPCM 21.
Based upon various input signals from the user interface 13 and the
powertrain, including the ESD 74, the HCP 5 generates various commands,
including: the operator torque request ('TO_REQ') a commanded output torque
('TCMD') to the driveline 90, an engine input torque command, clutch torques
for the torque-transfer clutches Cl 70, C2 62, C3 73, C4 75 of the
transmission 10; and the torque commands for the first and second electric
machines 56 and 72, respectively. The TCM 17 is operatively connected to the
hydraulic control circuit 42 and provides various functions including

monitoring various pressure sensing devices (not shown) and generating and
communicating control signals to various solenoids (not shown) thereby
controlling pressure switches and control valves contained within the
hydraulic control circuit 42.
[0033] The ECM 23 is operatively connected to the engine 14, and functions
to acquire data from sensors and control actuators of the engine 14 over a
plurality of discrete lines, shown for simplicity as an aggregate bi-directional
interface cable 35. The ECM 23 receives the engine input torque command
from the HCP 5. The ECM 23 determines the actual engine input torque, TI,
provided to the transmission 10 at that point in time based upon monitored
engine speed and load, which is communicated to the HCP 5. The ECM 23
monitors input from the rotational speed sensor 11 to determine the engine
input speed to the input shaft 12, which translates to the transmission input
speed, NI. The ECM 23 monitors inputs from sensors (not shown) to
determine states of other engine operating parameters including, e.g., a
manifold pressure, engine coolant temperature, ambient air temperature, and
ambient pressure. The engine load can be determined, for example, from the
manifold pressure, or alternatively, from monitoring operator input to the
accelerator pedal 113. The ECM 23 generates and communicates command
signals to control engine actuators, including, e.g., fuel injectors, ignition
modules, and throttle control modules, none of which are shown.
[0034] The TCM 17 is operatively connected to the transmission 10 and
monitors inputs from sensors (not shown) to determine states of transmission
operating parameters. The TCM 17 generates and communicates command
signals to control the transmission 10, including controlling the hydraulic

control circuit 42. Inputs from the TCM 17 to the HCP 5 include estimated
clutch torques for each of the clutches, i.e., Cl 70, C2 62, C3 73, and C4 75,
and rotational output speed, No, of the output member 64. Other actuators and
sensors may be used to provide additional information from the TCM 17 to the
HCP 5 for control purposes. The TCM 17 monitors inputs from pressure
switches (not shown) and selectively actuates pressure control solenoids (not
shown) and shift solenoids (not shown) of the hydraulic control circuit 42 to
selectively actuate the various clutches Cl 70, C2 62, C3 73, and C4 75 to
achieve various transmission operating range states, as described hereinbelow.
[0035] The BPCM 21 is signally connected to sensors (not shown) to
monitor the ESD 74, including states of electrical current and voltage
parameters, to provide information indicative of parametric states of the
batteries of the ESD 74 to the HCP 5. The parametric states of the batteries
preferably include battery state-of-charge, battery voltage, battery temperature,
and available battery power, referred to as a range PBAT_MIN to PBAT_MAX.
[0036] Each of the control modules ECM 23, TCM 17, TPIM 19 and BPCM
21 is preferably a general-purpose digital computer comprising a
microprocessor or central processing unit, storage mediums comprising read
only memory ('ROM'), random access memory ('RAM'), electrically
programmable read only memory ('EPROM'), a high speed clock, analog to
digital ('A/D') and digital to analog ('D/A') circuitry, and input/output
circuitry and devices ('I/O') and appropriate signal conditioning and buffer
circuitry. Each of the control modules has a set of control algorithms,
comprising resident program instructions and calibrations stored in one of the
storage mediums and executed to provide the respective functions of each

computer. Information transfer between the control modules is preferably
accomplished using the LAN bus 6 and SPI buses. The control algorithms are
executed during preset loop cycles such that each algorithm is executed at
least once each loop cycle. Algorithms stored in the non-volatile memory
devices are executed by one of the central processing units to monitor inputs
from the sensing devices and execute control and diagnostic routines to
control operation of the actuators, using preset calibrations. Loop cycles are
executed at regular intervals, for example each 3.125, 6.25, 12.5, 25 and 100
milliseconds during ongoing operation of the powertrain. Alternatively,
algorithms may be executed in response to the occurrence of an event.
[0037] The exemplary powertrain selectively operates in one of several
operating range states that can be described in terms of an engine state
comprising one of an engine on state ('ON') and an engine off state ('OFF'),
and a transmission state comprising a plurality of fixed gears and continuously
variable operating modes, described with reference to Table 1, below.

Table 1
Description Engine Transmission Operating Applied
State Range State Clutches
MI_Eng_Off OFF EVT Mode I Cl 70
MI_Eng_On ON EVT Mode I C1 70
FG1 ON Fixed Gear Ratio 1 Cl 70 C4 75
FG2 ON Fixed Gear Ratio 2 Cl 70 C2 62
MII_Eng_Off OFF EVT Mode 11 C2 62
MII_Eng_On ON EVT Mode II C2 62
FG3 ON Fixed Gear Ratio 3 C2 62 C4 75
FG4 ON Fixed Gear Ratio 4 C2 62 C3 73

[0038] Each of the transmission operating range states is described in the
table and indicates which of the specific clutches Cl 70, C2 62, C3 73, and C4
75 are applied for each of the operating range states. A first continuously
variable mode, i.e., EVT Mode I, or MI, is selected by applying clutch Cl 70
only in order to "ground" the outer gear member of the third planetary gear set
28. The engine state can be one of ON ('MI_Eng_On') or OFF
('MI_Eng_Off). A second continuously variable mode, i.e., EVT Mode II, or
MII, is selected by applying clutch C2 62 only to connect the shaft 60 to the
carrier of the third planetary gear set 28. The engine state can be one of ON
('MII_Eng_On') or OFF ('MII_Eng_Off). For purposes of this description,
when the engine state is OFF, the engine input speed is equal to zero
revolutions per minute ('RPM'), i.e., the engine crankshaft is not rotating. A
fixed gear operation provides a fixed ratio operation of input-to-output speed
of the transmission 10, i.e., NI/No, is achieved. A first fixed gear operation
('FG1') is selected by applying clutches Cl 70 and C4 75. A second fixed
gear operation ('FG2') is selected by applying clutches Cl 70 and C2 62. A
third fixed gear operation ('FG3') is selected by applying clutches C2 62 and
C4 75. A fourth fixed gear operation ('FG4') is selected by applying clutches
C2 62 and C3 73. The fixed ratio operation of input-to-output speed increases
with increased fixed gear operation due to decreased gear ratios in the
planetary gears 24, 26, and 28. The rotational speeds of the first and second
electric machines 56 and 72, NA and NB respectively, are dependent on internal
rotation of the mechanism as defined by the clutching and are proportional to
the input speed measured at the input shaft 12.

[0039] In response to operator input via the accelerator pedal 113 and brake
pedal 112 as captured by the user interface 13, the HCP 5 and one or more of
the other control modules determine the commanded output torque, TCMD,
intended to meet the operator torque request, TO_REQ, to be executed at the
output member 64 and transmitted to the driveline 90. Final vehicle
acceleration is affected by other factors including, e.g., road load, road grade,
and vehicle mass. The operating range state is determined for the transmission
10 based upon a variety of operating characteristics of the powertrain. This
includes the operator torque request, communicated through the accelerator
pedal 113 and brake pedal 112 to the user interface 13 as previously described.
The operating range state may be predicated on a powertrain torque demand
caused by a command to operate the first and second electric machines 56 and
72 in an electrical energy generating mode or in a torque generating mode.
The operating range state can be determined by an optimization algorithm or
routine which determines optimum system efficiency based upon operator
demand for power, battery state of charge, and energy efficiencies of the
engine 14 and the first and second electric machines 56 and 72. The control
system manages torque inputs from the engine 14 and the first and second
electric machines 56 and 72 based upon an outcome of the executed
optimization routine, and system efficiencies are optimized thereby, to manage
fuel economy and battery charging. Furthermore, operation can be determined
based upon a fault in a component or system. The HCP 5 monitors the torque-
generative devices, and determines the power output from the transmission 10
required to achieve the desired output torque to meet the operator torque
request. As should be apparent from the description above, the ESD 74 and

the first and second electric machines 56 and 72 are electrically-operatively
coupled for power flow therebetween. Furthermore, the engine 14, the first
and second electric machines 56 and 72, and the electro-mechanical
transmission 10 are mechanically-operatively coupled to transmit power
therebetween to generate a power flow to the output member 64.
[0040] FIG. 4 depicts a schematic diagram of the hydraulic control circuit 42
for controlling flow of hydraulic fluid in the exemplary transmission. A main
hydraulic pump 88 is driven off the input shaft 12 from the engine 14, and an
auxiliary pump 110 controlled by the TPIM 19 to provide pressurized fluid to
the hydraulic control circuit 42 through valve 140. The auxiliary pump 110
preferably comprises an electrically-powered pump of an appropriate size and
capacity to provide sufficient flow of pressurized hydraulic fluid into the
hydraulic control circuit 42 when operational. The hydraulic control circuit 42
selectively distributes hydraulic pressure to a plurality of devices, including
the torque-transfer clutches Cl 70, C2 62, C3 73, and C4 75, active cooling
circuits for the first and second electric machines 56 and 72 (not shown), and a
base cooling circuit for cooling and lubricating the transmission 10 via
passages 142, 144 (not depicted in detail). As previously stated, the TCM 17
actuates the various clutches to achieve one of the transmission operating
range states through selective actuation of hydraulic circuit flow control
devices comprising variable pressure control solenoids ('PCS') PCS1 108,
PCS2 114, PCS3 112, PCS4 116 and solenoid-controlled flow management
valves, X-valve 119 and Y-valve 121. The hydraulic control circuit 42 is
fluidly connected to pressure switches PS1, PS2, PS3, and PS4 via passages
122, 124, 126, and 128, respectively. The pressure control solenoid PCS1 108

has a control position of normally high and is operative to modulate the
magnitude of fluidic pressure in the hydraulic circuit through fluidic
interaction with controllable pressure regulator 107 and spool valve 109. The
controllable pressure regulator 107 and spool valve 109 interact with PCS1
108 to control hydraulic pressure in the hydraulic control circuit 42 over a
range of pressures and may provide additional functionality for the hydraulic
control circuit 42. Pressure control solenoid PCS3 112 has a control position
of normally high, and is fluidly connected to spool valve 113 and operative to
effect flow therethrough when actuated. Spool valve 113 is fluidly connected
to pressure switch PS3 via passage 126. Pressure control solenoid PCS2 114
has a control position of normally high, and is fluidly connected to spool valve
115 and operative to effect flow therethrough when actuated. Spool valve 115
is fluidly connected to pressure switch PS2 via passage 124. Pressure control
solenoid PCS4 116 has a control position of normally low, and is fluidly
connected to spool valve 117 and operative to effect flow therethrough when
actuated. Spool valve 117 is fluidly connected to pressure switch PS4 via
passage 128.
[0041] The X-Valve 119 and Y-Valve 121 each comprise flow management
valves controlled by solenoids 118, 120, respectively, in the exemplary
system, and have control states of High (' 1') and Low ('0'). The control states
refer to positions of each valve to which control flow to different devices in
the hydraulic control circuit 42 and the transmission 10. The X-valve 119 is
operative to direct pressurized fluid to clutches C3 73 and C4 75 and cooling
systems for stators of the first and second electric machines 56 and 72 via
fluidic passages 136, 138, 144, 142 respectively, depending upon the source of

the fluidic input, as is described hereinafter. The Y-valve 121 is operative to
direct pressurized fluid to clutches Cl 70 and C2 62 via fluidic passages 132
and 134 respectively, depending upon the source of the fluidic input, as is
described hereinafter. The Y-valve 121 is fluidly connected to pressure switch
PS1 via passage 122.
[0042] The hydraulic control circuit 42 includes a base cooling circuit for
providing hydraulic fluid to cool the stators of the first and second electric
machines 56 and 72. The base cooling circuit includes fluid conduits from the
valve 140 flowing directly to a flow restrictor which leads to fluidic passage
144 leading to the base cooling circuit for the stator of the first electric
machine 56, and to a flow restrictor which leads to fluidic passage 142 leading
to the base cooling circuit for the stator of the second electric machine 72.
Active cooling of stators for the first and second electric machines 56 and 72
is effected by selective actuation of pressure control solenoids PCS2 114,
PCS3 112 and PCS4 116 and solenoid-controlled flow management valves X-
valve 119 and Y-valve 121, which leads to flow of hydraulic fluid around the
selected stator and permits heat to be transferred therebetween, primarily
through conduction.
[0043] An exemplary logic table to accomplish control of the exemplary
hydraulic control circuit 42 to control operation of the transmission 10 in one
of the transmission operating range states is provided with reference to Table
2, below.

Table 2
X- Y- PCS1 PCS2 PCS3 PCS4
Valve Valve
Logic Logic
Transmis No C2 Normal Normal Normal Normal
-sion Latch Latch High High High Low
Operating
Range
State
EVT 0 0 Line MG-B Cl MG-A
Model Modul- Stator Stator
ation Cool Cool
EVT 0 1 Line C2 MG-B MG-A
Mode II Modul- Stator Stator
ation Cool Cool
Low 1 0 Line C2 Cl C4
Range Modul-
ation
High 1 1 Line C2 C3 C4
Range Modul-
ation
[0044] A Low Range is defined as a transmission operating range state
comprising one of the first continuously variable mode and the first and
second fixed gear operations. A High Range is defined as a transmission
operating range state comprising one of the second continuously variable
mode and the third and fourth fixed gear operations. Selective control of the
X-valve 119 and the Y-valve 121 and actuation of the solenoids PCS2 112,
PCS3 114, PCS4 116 facilitate flow of hydraulic fluid to actuate clutches Cl
70, C2 63, C3 73, and C4 75, and provide cooling for the stators the first and
second electric machines 56 and 72.
[0045] In operation, a transmission operating range state, i.e. one of the fixed
gear and continuously variable mode operations, is selected for the exemplary

correlation between PLINE, the determinative factor in flow through the coolant
loop, and the cooling load or cooling capacity required by the operation of the
electric machine or machines. As a result, it is preferable to control the flow
through the coolant loop based upon the cooling requirements of the electric
machine. A method is described to control electric machine cooling by
modulating PLINE based upon electric machine cooling requirements predicted
by electric machine speeds.
[0047] FIG. 5 illustrates an information flow diagram describing an
exemplary determination of the minimum PLINE that will meet lubrication
requirements based upon an engine speed and electric machine speeds, in
accordance with the present disclosure. Control system 200 is depicted
including input speed to minimum pressure conversion blocks 210, 220, and
230 and max block 240. The pictured system is useful to monitor a hybrid
powertrain consisting of an engine and a first and second electric machine, all
requiring lubrication supplied by the hydraulic control system. However, it
will be appreciated that the number of input can be modulated for a system
utilizing a single electric machine or more than two electric machines, and the
disclosure is not intended to be limited to the specific embodiments described
herein. Minimum pressure conversion blocks 210, 220, and 230 monitor
inputs NI, NA, and NB, respectively. Each conversion block utilizes a look-up
table or an algorithm to determine a minimum PLINE or PMIN required to supply
lubrication to each respective torque generative device. These PMIN values are
provided as input to max block 240, and the maximum PMIN is utilized to
provide the minimum PLINE required to provide adequate lubrication or PMIN
LUBE.

[0048] As described above, the hydraulic control system provides a flow of
hydraulic oil to a number of functions. The method described above provides
PMIN LUBE to a control system operating hydraulic pumps and modulating
service of flow to the various functions in order to maintain a required PLINE.
FIG. 6 illustrates an information flow diagram describing an exemplary
determination of the minimum PLINE that will meet requirements of functions
served by a hydraulic control system, in accordance with the present
disclosure. In addition to PMIN LUBE, PMIN terms are provided for each of the
other functions, including, in this exemplary embodiment, clutch operation, a
base cooling loop, and an active cooling loop. Returning to FIG. 6, control
system 300 includes max block 302 and max block 304. Max block 304
operates by methods described above and provides a PMIN LUBE. By other
means known in the art, a PMIN CLUTCH, PMIN BASE COOLING, PMIN ACTIVE COOLING
are additionally provided as inputs to max block 302. Among the various PMIN
terms received as inputs to max block 302, the highest value is selected and is
utilized to control the hydraulic control system and the included hydraulic
pumps.
[0049] The measurements and calculations required to determine the various
terms described above are performed cyclically, with the operations occurring
in a loop or a combination of loops. As will be appreciated by one having
ordinary skill in the art, sample rates will vary and are influenced by speeds of
the computerized processors involved, the required sample rates for accurate
control of PLINE, and various other factors.
[0050] It is understood that modifications are allowable within the scope of
the disclosure. The disclosure has been described with specific reference to

the preferred embodiments and modifications thereto. Further modifications
and alterations may occur to others upon reading and understanding the
specification. It is intended to include all such modifications and alterations
insofar as they come within the scope of the disclosure.

CLAIMS
1. Method for controlling hydraulic line pressure for component lubrication
in an electro-mechanical transmission mechanically-operatively coupled
to an internal combustion engine and an electric machine, and adapted to
selectively transmit mechanical power to an output member, said method
comprising:
monitoring a speed of said engine;
monitoring a speed of said electric machine;
determining a minimum line pressure required to lubricate said engine
based upon said speed of said engine;
determining a minimum line pressure required to lubricate said electric
machine based upon said speed of said electric machine; and
controlling a minimum line pressure of a hydraulic control system to at
least satisfy a larger value of said minimum line pressure required to
lubricate said engine and said minimum line pressure required to
lubricate said electric machine.
2. The method of claim 1, further comprising:
monitoring a speed of a second electric machine;
determining a minimum line pressure required to lubricate said second
electric machine based upon said speed of said second electric
machine; and
controlling said minimum line pressure of a hydraulic control system to
at least satisfy a largest value of said minimum line pressure required

to lubricate said engine, said minimum line pressure required to
lubricate said electric machine, and said minimum line pressure
required to lubricate said second electric machine.
3. The method of claim 2, wherein controlling said minimum line pressure
of a hydraulic control system comprises:
monitoring a minimum line pressure required to operate clutches within
said transmission;
monitoring a minimum line pressure require to cool said electric
machine and said second electric machine; and
selecting said minimum line pressure of a hydraulic control system based
upon a largest value of said minimum line pressure required to
lubricate said engine,
lubricate said electric machine,
lubricate said second electric machine,
operate clutches within said transmission, and
cool said electric machine and said second electric machine.
4. The method of claim 1, wherein controlling said minimum line pressure
of a hydraulic control system comprises:
monitoring a minimum line pressure required to operate clutches within
said transmission;
monitoring a minimum line pressure required to cool said electric
machine and said second electric machine; and
selecting said minimum line pressure of a hydraulic control system based
upon a largest value of said minimum line pressure required to

lubricate said engine,
lubricate said electric machine,
operate clutches within said transmission, and
cool said electric machine and said second electric machine.
5. A method for maintaining a minimum hydraulic line pressure for
component lubrication in a hybrid powertrain comprising an internal
combustion engine and an electric machine transmitting mechanical
power to an output member, the method comprising:
monitoring a speed of said engine;
monitoring a speed of said electric machine;
determining a minimum line pressure required to lubricate said engine
based upon said speed of said engine;
determining a minimum line pressure required to lubricate said electric
machine based upon said speed of said electric machine;
comparing said minimum line pressure required to lubricate said engine
and said minimum line pressure required to lubricate said electric
machine to find a greater of said minimum line pressures;
selecting a minimum line pressure for lubrication based upon said
comparing; and
controlling a minimum line pressure of a hydraulic control system based
upon said minimum line pressure for lubrication.
6. The method of claim 5, further comprising:
monitoring a speed of a second electric machine; and

determining a minimum line pressure required to lubricate said second
electric machine based upon said speed of said second electric
machine; and
wherein said comparing further comprises comparing said minimum line
pressures to find a greatest of said minimum line pressures required
to
lubricate said engine,
lubricate said electric machine, and
lubricate said second electric machine.
7. The method of claim 6, wherein controlling said minimum line pressure
of a hydraulic control system comprises:
monitoring a minimum line pressure required to operate other functions
served by said hydraulic control system; and
selecting said minimum line pressure of a hydraulic control system based
upon a larger pressure of said minimum line pressure for lubrication
and said minimum line pressure required to operate other functions
served by said hydraulic control system.
8. The method of claim 5, wherein controlling said minimum line pressure
of a hydraulic control system comprises:
monitoring a minimum line pressure required to operate other functions
served by said hydraulic control system; and
selecting said minimum line pressure of a hydraulic control system based
upon the larger pressure of said minimum line pressure for

lubrication and said minimum line pressure required to operate other
functions served by said hydraulic control system.
9. Apparatus for controlling hydraulic line pressure for component
lubrication in an electro-mechanical transmission mechanically-
operatively coupled to an internal combustion engine and first and
second electric machines, and adapted to selectively transmit mechanical
power to an output member, said apparatus comprising:
a main hydraulic pump mechanically connected to said engine;
an electrically powered auxiliary hydraulic pump; and
a hydraulic control system operatively connected to said main hydraulic
pump, said auxiliary hydraulic pump, and a lubrication circuit
providing a flow of hydraulic oil to said engine, said first electric
machine, and said second electric machine;
wherein said hydraulic control system includes logic monitoring a speed
of said engine, a speed of said first electric machine, and a speed of a
second electric machine, determining a minimum line pressure
required for lubrication based upon said speeds, and controlling said
main hydraulic pump and said auxiliary hydraulic pump based upon
said minimum line pressure required for lubrication.
10. The apparatus of claim 9, wherein hydraulic control system comprises a
circuit providing a substantially fixed flow resistance at a connection to
said lubrication circuit.

11. The apparatus of claim 9, wherein hydraulic control system further
includes logic controlling functions served by said hydraulic control
system based upon said minimum line pressure required for lubrication.

A method for controlling hydraulic line pressure for component lubrication in a transmission includes monitoring a speed of an engine and an electric machine, determining a minimum line pressure required to lubricate the engine based upon the speed of the engine, determining a minimum line pressure required to lubricate the electric machine based upon the speed of the electric machine, controlling a minimum line pressure of a hydraulic control system to at least satisfy a larger value of the minimum line pressures.

Documents:

http://ipindiaonline.gov.in/patentsearch/GrantedSearch/viewdoc.aspx?id=2SdhB+pQGk7XryvTtXd4ww==&loc=wDBSZCsAt7zoiVrqcFJsRw==

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Patent Number

279127

Indian Patent Application Number

1818/KOL/2008

PG Journal Number

02/2017

Publication Date

13-Jan-2017

Grant Date

11-Jan-2017

Date of Filing

24-Oct-2008

Name of Patentee

BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT,

Applicant Address

PETUELRING 130, 80788 MUNCHEN, GERMANY ,

Inventors:

#	Inventor's Name	Inventor's Address
1	JY-JEN F. SAH	1915 BLOOMFIELD OAKS DRIVE WEST BLOOMFIELD, MICHIGAN 48324
2	KRISTIN L. DAY	2201 TRAIL WAY CT. COMMERCE TOWNSHIP, MI 48390

PCT International Classification Number

F16H61/00

PCT International Application Number

N/A

PCT International Filing date

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	60/982,863	2007-10-26	U.S.A.