Patent Application
20050116537
The present invention relates generally to hydraulic systems for vehicles and, more particularly, to a combination braking and traction control system adapted for use in motor vehicle driveline applications.
In view of an increased demand for vehicles having anti-lock braking systems and traction control systems, many controls are currently being incorporated in vehicular driveline applications for transferring braking torque and/or drive torque to the wheels. A modern trend in vehicle design includes equipping a driveline with a transfer case having an electronically controlled transfer clutch. The transfer clutch is operable to automatically direct drive torque to the primary and/or secondary drivelines without any input or action on the part of the vehicle operator. The transfer clutch is typically actuated by a power-operated clutch actuator which responds to control signals sent from a traction control module. The control signals are typically based on current operating conditions of the vehicle (i.e., vehicle speed, interaxle speed difference, acceleration, steering angle, etc.) as detected by various sensors. For example, if traction is lost at the primary wheels, the transfer clutch can be engaged to establish an “on-demand” four-wheel drive mode. Thus, such “on-demand” transfer cases can utilize adaptive control schemes for automatically controlling torque distribution during all types of driving and road conditions.
To assure vehicle stability is maintained during braking, many vehicles are also now equipped with an anti-lock braking system. The anti-lock braking system includes a hydraulic pressure source which supplies pressurized fluid to hydraulically-powered brake actuators for actuating the brakes located at each wheel end. The anti-lock braking system typically uses some or all of the sensor signals to control operation of the brake actuators. Specifically, a brake control mode receives sensor signals and functions to control coordinated actuation of the brakes. Typically, little to no interaction occurs between the control modules for the anti-lock braking system and the traction control system. However, some systems provide minimal communication to disable the traction control system so as to assure that the vehicle is not placed in a four-wheel drive mode when the anti-lock braking system is functioning.
While the present anti-lock braking systems and traction control systems have operated sufficiently in the past, a need exists to reduce the complexity and cost of implementing such systems on a motor vehicle. For example, the size, weight and electrical power requirements of electrical motors needed to provide the described clutch engagement loads may make such systems cost prohibitive.
Thus, it is an object of the present invention to provide a combination braking and traction control system having a source of pressurized fluid and an actuator adapted to selectively supply pressurized fluid to the vehicle wheel brakes and at least one transfer clutch. The transfer clutch is operable to selectively transfer drive torque from a first rotary member to a second rotary member. The anti-lock braking and traction control system also includes a controller in communication with the actuator to control the duration and magnitude of fluid pressure supplied to the wheel brakes and the transfer clutch.
Further areas of applicability of the present invention will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
The present invention will become more fully understood from the detailed description and the accompanying drawings, wherein:
The present invention is directed to a combination braking and traction control system for adaptively controlling the brakes of the vehicle as well as a mechanism that modulates the torque transferred from a first rotary member to a second rotary member. The torque transfer mechanism finds particular application in power transmission devices for use in motor vehicle drivelines such as, for example, an on-demand clutch in a transfer case or in-line torque coupling, a biasing clutch associated with a differential assembly in a transfer case or a drive axle assembly, or as a shift clutch in a multi-speed automatic transmission. Thus, while the present invention is hereinafter described in association with particular arrangements for use in specific driveline applications, it will be understood that the arrangements shown and described are merely intended to illustrate embodiments of the present invention.
With particular reference to
With continued reference to the drawings, drivetrain 10 is shown to further include an electronically-controlled brake and all wheel drive (AWD) system 44 for providing anti-locking braking functions as well as traction control functions. In this regard, driveline 10 is equipped with a pair of front brakes 46 and 48 for decelerating front wheels 34 and 35 as well as a pair of rear brakes 50 and 52 for decelerating rear wheels 24 and 25. Each brake includes a hydraulically-powered brake operator for applying the brakes. Additionally, brake and AWD system 44 includes one or more clutches that may be selectively actuated for transferring drive torque from engine 18 to one or more of the wheels. In one example, a transfer clutch 66 is positioned within transfer case 22 and may be selectively operated to transfer drive torque from rear output shaft 32 to front output shaft 42 for establishing part-time and on-demand four-wheel drive modes. Furthermore, front axle assembly 36 may be equipped with a front axle biasing clutch 68 for selectively varying the torque distribution delivered from front prop shaft 40 to front wheels 34 and 35. Similarly, rear axle assembly 26 may include a rear axle biasing clutch 70 for selectively varying the torque distribution delivered from rear prop shaft 30 to rear wheels 24 and 25. It should be appreciated that a vehicle may be equipped with one or more of these torque transfer clutches without departing from the scope of the present invention. Preferably, each of these torque transfer clutches includes at least one multi-plate friction clutch assembly and, as will be detailed, a hydraulically-powered actuator for controlling engagement of the friction clutch assemblies.
Brake and AWD system 44 preferably includes a common brake/AWD system actuator assembly 54. Pressurized hydraulic fluid is selectively supplied to each of the brake operators and/or the clutches by actuator assembly 54. In operation, a hydraulic pump 56 is driven by a motor 58 to supply fluid to actuator assembly 54 and an accumulator 60. Accumulator 60 stores pressurized fluid for use during peak demand situations. In addition vehicle sensors 62 detect certain dynamic and operational characteristics of the motor vehicle. Finally, a controller 64 controls the operation of components associated with actuator assembly 54 in response to signals provided by vehicle sensors 62.
With reference to
In the example depicted in
Similarly, a second fluid passageway 76B interconnects brake operator 48A associated with right front brake 48 to the high fluid pressure generated by pump 56. A second electro-hydraulic pressure modulator 72B provides metered pressurized fluid to hydraulic brake operator 46B for controlling engagement of right front brake 48. A pressure sensor 74B outputs a signal indicative of the fluid pressure within passageway 78 to controller 64. With continued reference to
The brake/AWD system depicted in
Transfer clutch 66 is operably arranged to transfer rotary power (i.e., drive torque) from rear output shaft 32 to front output shaft 42 through a transfer assembly 90. Transfer assembly 90 includes a first gear 92, a second gear 94, and a third gear 96 that is in meshed engagement with first gear 92 and second gear 94. First gear 92 is shown to be rotatably supported on rear output shaft 32 via a bearing assembly 98 and likewise be rotatably supported from housing 85 via a pair of laterally spaced bearing assemblies 100. Second gear 94 is coupled via a spline connection 102 to front output shaft 42 and is rotatably supported from housing 85 by a pair of laterally spaced bearing assemblies 104. Finally, third gear 96 is rotatably supported by bearing assemblies 106 on a stub shaft 108 that is non-rotatably secured to housing 85. It is contemplated that geared transfer assembly 90 could be replaced with a well-known chain and sprocket type transfer system if desired.
Transfer clutch 66 includes a multi-plate friction clutch assembly 110 and clutch operator 66A, hereinafter referred to as clutch actuator assembly 112. Clutch assembly 110 is shown to include a clutch drum 114 fixed via a spline connection 116 to a tubular segment 118 of first gear 92, a clutch hub 120 fixed via a spline connection 122 to rear output shaft 32, and a multi-plate clutch pack 124 operably disposed between drum 114 and hub 120. Clutch pack 124 includes a set of outer clutch plates that are splined for rotation with and axial movement on an outer cylindrical rim segment 126 of drum 114. Clutch pack 124 also includes a set of inner clutch plates that are splined for rotation with and axial movement on clutch hub 120. Clutch assembly 110 further includes an apply plate 128 splined for rotation with rim segment 126 of drum 114, and a pressure plate 132 splined to a fixed support 134. A thrust bearing 135 is provided between apply plate 128 and pressure plate 132 to accommodate relative rotation therebetween during concurrent axial movement. Clutch actuator assembly 112 includes a piston 136 positioned within a pressure chamber 138 formed in support 134. A passageway 140 extends through support 134 and housing 85 to allow pressurized fluid supplied from pressure modulator 72E to enter chamber 138 and act on piston 136. Apply plate 128 is arranged to exert a compressive clutch engagement force on clutch pack 124 in response to translational movement of pressure plate 132 and piston 136.
Apply plate 128 is axially moveable relative to clutch pack 124 between a first or “released” position and a second or “locked” position. With apply plate 128 in its released position, a minimum clutch engagement force is exerted on clutch pack 124 such that virtually no drive torque is transferred from rear output shaft 32 through clutch assembly 110 and transfer assembly 90 to front output shaft 42 so as to establish the two-wheel drive mode. In contrast, location of apply plate 128 in its locked position causes a maximum clutch engagement force to be applied to clutch pack 124 such that front output shaft 42 is, in effect, coupled for common rotation with rear output shaft 32 so as to establish the part-time four-wheel drive mode. Therefore, accurate control of the position of apply plate 128 between its released and locked positions permits adaptive regulation of the amount of drive torque transferred from rear output shaft 32 to front output shaft 42, thereby establishing the on-demand four-wheel drive mode.
One skilled in the art will appreciate that brake system actuator 202 and AWD actuator 206 are both controlled by controller 64. Preferably, controller 64 is the main vehicle controller. However, controller 64 may be separate from and in addition to a main vehicle controller.
Brake supply circuit 204 includes a motor 210 drive a pump 212. The output from pump 212 supplies an accumulator 214 and brake system actuator 202. Accumulator 214 functions to provide pressurized fluid to brake system actuator 202 if pump 212 is unable to provide the requested demand. Brake system actuator 202 is substantially similar to the brake and AWD actuator previously described. As such, brake system actuator 202 selectively supplies pressurized fluid to each of the hydraulically-powered brake operators to control engagement of the wheel brakes based on signals provided by controller 64.
AWD supply circuit 208 includes a motor 216 driving a pump 218. The output from pump 218 supplies an accumulator 220 as well as AWD actuator 206. AWD actuator 206 selectively provides pressurized fluid to transfer clutch 66, front axle clutch 68 and/or rear axle clutch 70. As previously mentioned, the number and location of clutches implemented within the vehicle at
Based on the description of brake and AWD system 200 previously provided, one skilled in the art will appreciate that brake system actuator 202 and AWD actuator 206 may be controlled to operate simultaneously, alternately or entirely independently from one another. Separate supply circuits 204 and 208 provide further support for independent control of brake system actuator 202 and AWD actuator 206. However, a single supply circuit may be used to provide fluid to both brake system actuator 202 and AWD actuator 206 without departing from the scope of the present invention. Depending on the volume requirements of brake system actuator and AWD actuator 206, it may be more efficient to construct a single slightly larger supply circuit than two individual smaller supply circuits.
Furthermore, the foregoing discussion discloses and describes merely exemplary embodiments of the present invention. One skilled in the art will readily recognize from such discussion, and from the accompanying drawings and claims, that various changes, modifications and variations may be made therein without department from the spirit and scope of the invention as defined in the following claims.
