BACKGROUND OF THE INVENTION 1 Field of the Invention

The present invention relates, generally, to an automatic transmission and, more specifically, to an automatic transmission designed for use with a hybπd vehicle

2 Description of the Related Art Generally speaking, land vehicles require a powertrain consisting of three basic components These components include a power plant (such as an internal combustion engine), a power transmission, and wheels The power transmission component is typically referred to simply as the "transmission " Engine torque and speed are converted in the transmission in accordance with the tractive-power demand of the vehicle Hybnd vehicles employ two separate power plants One power plant is typically an internal combustion engine The other is an electric motor The electric motor is powered by electπcal energy stored in a bank of batteries that are typically also supported on the vehicle The batteries may be recharged by the internal combustion engine via an electrical generator that is driven by the internal combustion engine or from another external power source Controlling and regulating transmissions to achieve the desired vehicle occupant comfort goals in an efficient and cost effective manner is a complicated matter There are a large number of events to properly tune and execute within the transmission for each shift to occur smoothly and efficiently Furthermore, since the control of automatic transmissions is carried out by hydraulically actuating the various components within the transmission, it is important to provide a stable hydraulic pressure Since hydraulically actuated devices respond in a predetermined and a precise manner for the given pressure supplied to actuate them, inaccurate control of the hydraulic pressure causes inaccurate operation and control of the transmission Establishing and maintaining a stable hydraulic pressure in an automatic transmission can be problematic As previously mentioned, a pump is employed to provide pressurized hydraulic fluid for the control and actuation of the transmission In addition, the clutches and gear assemblies are lubricated and cooled by a secondary flow of hydraulic fluid With conventional vehicles, the pump is mechanically dπven by a power take-off from the engine Thus, the hydraulic pressure delivered from the pump increases as the pump speed increases in response to an increase in engine speed The challenges of maintaining hydraulic pressure delivered from the pump in a conventional vehicle are only complicated in a hybrid vehicle In a hybrid vehicle, the electπc motor is operable when the vehicle is driven short distances at slower speeds, such as in stop-and- go traffic and city driving However, even when the electric motor drives the vehicle, the clutches, as well as other components of the transmission, still need to have access to pressurized transmission fluid Accordingly, it is known to employ a separate pump that is driven by the electπc motor to ensure that the transmission has sufficient access to pressurized fluid when the electπc motor is operable Thus, transmissions used for hybrid vehicles typically employ two separate pumps that act independently of one another to provide pressurized fluid to the transmission under all operating conditions This essentially requires two redundant pumps of similar size and capacity that operate alternatively depending on whether the internal combustion or the electπc motor is dnving the vehicle This arrangement results in increased costs and complexity as the transmission must be configured to receive hydraulic fluid from two separate sources depending on which portion of the hybπd's power plant is operational In addition, there is a certain inefficiency in having two pumps that serve the same purpose but are alternatingly operable depending on the source of motive power used to drive the hybrid engine

One type of transmission known in the art has two clutches and is generally referred to simply as dual, or twin, clutch transmissions (DCTs) The dual clutch structure is most often coaxially and cooperatively configured to derive power input from a flywheel arrangement However, some designs have a dual clutch assembly that is coaxial, but with the clutches located on opposite sides of the transmissions body and having different input sources Regardless, dual clutch transmissions typically include one power transmission assembly on each of two input shafts concomitantly driving one output shaft Each clutch and associated gear sets can be shifted and clutched independently In this manner, uninterrupted power upshifting and downshifting between gears, along with the high mechanical efficiency of a manual transmission is available in an automatic transmission form Thus, significant increases in fuel economy and vehicle performance may be achieved through the effective use of certain dual clutch transmissions

These factors make the dual clutch transmissions an attractive component for a hybπd engine

While the automatic transmissions known in the related art have generally worked for their intended purposes, there remains a need in the art for a transmission for a hybrid engine having improved operational interaction between the power plants of a hybrid engine and the transmission In addition, there remains a need in the art for such a transmission used in connection with hybrid engmes that are less complex and costly to manufacture than current systems available in the market At the same time, there remains a need in the art for a transmission designed for use with a hybrid engine that is capable of quickly and efficiently providing pressurized hydraulic fluid for the control and actuation of the transmission as well as for cooling the various components of the transmission in a cost-effective manner

SUMMARY OF THE INVENTION

The deficiencies of the related art are overcome in an automatic transmission for a hybrid vehicle of the present invention wherein the vehicle has a power plant including an internal combustion engine and an electric motor The transmission includes a hydraulic circuit having a source of pressurized fluid and further including an actuation circuit that delivers pressurized fluid used to actuate components of the transmission as well as a coohng circuit that delivers pressurized fluid used to cool components of the transmission The source of pressurized fluid includes a first pump that is operatively driven by the internal combustion engine of the hybnd vehicle and a second pump that is operatively driven by the electric motor A pair of check valves is disposed in seπes and in fluid communication with the second pump The first pump is operable to supply pressurized fluid to the actuator circuit and the cooling circuit when the vehicle is operatively driven by the internal combustion engine The second pump acts to supply pressurized fluid to the coohng circuit when the first pump is operatively driven by the internal combustion engine under certain predetermined conditions and the first check valve is open In addition, the second pump also acts to supply pressurized fluid to the actuation circuit and the cooling circuit when the internal combustion engine is no longer operatively driving the first pump and the first and second check valves are open

In this way, and under certain predetermined conditions, both the first and second pumps are operable to supply pressurized fluid to the hydraulic circuit when necessary This may occur, for example, when the pressure delivered to the cooling circuit drops below a predetermined value In this case, the second pump driven by the electric motor assists the first pump to provide cooling fluid to the coohng circuit when the first check valve is open This arrangement allows the use of a smaller capacity, mechanically driven first pump and thereby reduces the cost of the transmission BRIEF DESCRIPTION OF THE DRAWINGS

Other objects, features and advantages o f the present mvention will be readily appreciated, as the same becomes better understood after reading the subsequent description taken in connection with the accompanying drawings wherein Figure 1 is a schematic illustration of a representative example of a transmission of the type that may employ the hydraulic valves of the present invention,

Figure 2 is a schematic diagram of a representative hydraulic circuit for a dual clutch transmission,

DETAILED DESCRIPTION

A representative example of an automatic transmission that may be employed for a hybrid engine is generally indicated at 10 in Figure 1 In this case, the automatic transmission described and illustrated herein is a dual clutch transmission However, those having ordinary skill m the art will appreciate from the descπption that follows that the present invention may be employed in connection with any type of automatic transmission used for a hybrid engine Thus, those having ordinary skill in the art will understand that the present invention is defined by the claims set forth herein, rather than by the dual clutch transmission illustrated in Figure 1 and described below As illustrated in Figure 1 , the dual clutch transmission 10 may include a dual, coaxial clutch assembly generally indicated at 12, a first input shaft, generally indicated at 14, a second input shaft, generally indicated at 16, that is coaxial to the first, a counter shaft, generally indicated at 18, an output shaft 20, a reverse counter shaft 22, a plurality of synchronizers, generally indicated at 24

The dual clutch transmission 10 forms a portion of a vehicle powertrarn and is responsible for taking a torque input from the hybrid power plant, such as an internal combustion engine or electπcal motor, and transmitting the torque through selectable gear ratios to the vehicle drive wheels The dual clutch transmission 10 operatively routes the applied torque from the power plant through the dual, coaxial clutch assembly 12 to either the first input shaft 14 or the second input shaft 16 The input shafts 14 and 16 include a first series of gears, which are in constant mesh with a second series of gears disposed on the counter shaft 18 Each one of the first series of gears interacts with one of the second senes of gears to provide the different gear ratios sets used for transferring torque The counter shaft 18 also includes a first output gear that is in constant mesh with a second output gear disposed on the output shaft 20 The plurality of synchronizers 24 are disposed on the two mput shafts 14, 16 and on the counter shaft 18 and are operatively controlled by the plurality of shift actuators 26 (Figure 2) to selectively engage one of the gear ratio sets Thus, torque is transferred from the engine to the dual, coaxial clutch assembly 12, to one of the input shafts 14 or 16, to the counter shaft 18 through one of the gear ratio sets, and to the output shaft 20 The output shaft 20 further provides the output torque to the remainder of the powertrain Additionally, the reverse counter shaft 22 includes an intermediate gear that is disposed between one of the first series of gears and one of the second series of gears, which allows for a reverse rotation of the counter shaft 18 and the output shaft 20 Each of these components will be discussed in greater detail below

Specifically, the dual, coaxial clutch assembly 12 includes a first clutch mechanism 32 and a second clutch mechanism 34 The first clutch mechanism 32 is, in part, physically connected to a portion of a flywheel (not shown) and is, in part, physically attached to the first input shaft 14, such that the first clutch mechanism 32 can operatively and selectively engage or disengage the first input shaft 14 to and from the flywheel Similarly, the second clutch mechanism 34 is, in part, physically connected to a portion of the flywheel and is, in part, physically attached to the second input shaft 16, such that the second clutch mechanism 34 can operatively and selectively engage or disengage the second input shaft 16 to and from the flywheel As shown in one embodiment illustrated in Figure 1, the first and second clutch mechanisms 32, 34 are coaxial such that the outer case 28 of the first clutch mechanism 32 fits inside of the outer case 36 of the second clutch mechanism 34 Similarly, the first and second input shafts 14, 16 are also coaxial such that the second input shaft 16 is hollow having an inside diameter sufficient to allow the first input shaft 14 to pass through and be partially supported by the second input shaft 16 Notwithstanding the embodiment illustrated in Figure 1, those having ordinary skill in the art will appreciate that the first and second clutch mechanisms 32, 34 may be physically arranged concentrically within the transmission, rather than the parallel structure illustrated in Figure 1 Similarly, the first and second input shafts may be arranged in parallel relative to one another

The first input shaft 14 includes a first input gear 38 and a third input gear 42 The first input shaft 14 is longer in length than the second input shaft 16 so that the first input gear 38 and a third input gear 42 are disposed adjacent to each other on the portion of the first input shaft 14 that extends beyond the second input shaft 16 The second input shaft 16 includes a second input gear 40, a fourth input gear 44, a sixth input gear 46, and a reverse input gear 48 As shown in Figure 1, the second input gear 40 and the reverse input gear 48 are fixedly supported on the second input shaft 16 and the fourth input gear 44 and sixth input gear 46 are rotatably supported about the second mput shaft 16 upon bearmg assemblies 50 so that then" rotation is unrestrained unless the accompanying synchronizer is engaged, as will be discussed in greater detail bebw

The counter shaft 18 includes the opposing, or counter, gears to those on the inputs shafts 14, 16 As shown in Figure 1, the counter shaft 18 includes a first counter gear 52, a second counter gear 54, a third counter gear 56, a fourth counter gear 58, a sixth counter gear 60, and a reverse counter gear 62 The counter shaft 18 fixedly retains the fourth counter gear 58 and sixth counter gear 60, while first, second, third, and reverse counter gears 52, 54, 56, 62 are supported about the counter shaft 18 by bearing assemblies 50 so that their rotation is unrestrained unless the accompanying synchronizer is engaged as will be discussed in greater detail below The counter shaft 18 also fixedly retains a first drive gear 64 that meshingly engages the corresponding second driven gear 66 on the output shaft 20 The second driven gear 66 is fixedly mounted on the output shaft 20 The output shaft 20 extends outward from the transmission 10 to provide an attachment for the remainder of the powertrain

The reverse counter shaft 22 is a relatively short shaft having a single reverse intermediate gear 72 that is disposed between, and meshingly engaged with, the reverse input gear 48 on the second input shaft 16 and the reverse counter gear 62 on the counter shaft 18 Thus, when the reverse gears 48, 62, and 72 are engaged, the reverse intermediate gear 72 on the reverse counter shaft 22 causes the counter shaft 18 to turn in the opposite rotational direction from the forward gears thereby providing a reverse rotation of the output shaft 20 It should be appreciated that all of the shafts of the dual clutch transmission 10 are disposed and rotationally secured within the transmission 10 by some manner of bearing assembly such as roller bearings, for example, shown at 68 in Figure 1

The engagement and disengagement of the various forward and reverse gears is accomplished by the actuation of the synchronizers 24 within the transmission As shown in Figure 1 in this example of a dual clutch transmission 10, there are four synchronizers 74, 76, 78, and 80 that are utilized to shift through the six forward gears and reverse It should be appreciated that there are a variety of known types of synchronizers that are capable of engaging a gear to a shaft and that the particular type employed for the purposes of this discussion is beyond the scope of the present invention Generally speaking, any type of synchronizer that is movable by a shift fork or like device may be employed As shown in the representative example of Figure 1, the synchronizers are two sided, dual actuated synchronizers, such that they engage one gear to its respective shaft when moved off of a center neutralized position to the right and engage another gear to its respective shaft when moved to the left Specifically with reference to the example illustrated in Figure 1 , synchronizer 78 can be actuated to the left to engage the first counter gear 52 on the counter shaft 18 or actuated to the right to engage the third counter gear 56 Synchronizer 80 can be actuated to the left to engage the reverse counter gear 62 or actuated to the right to engage the second counter gear 54 Likewise, synchronizer 74 can be actuated to the left to engage the fourth input gear 44 or actuated to the right to engage the sixth input gear 46 Synchronizer 76 is actuated to the right to directly engage the end of the first input shaft 14 to the output shaft 20 thereby providing a direct 1 1 (one to one) drive ratio for fifth gear There is no gear set to engage to the left of synchronizer 76 It should be appreciated that this example of the dual clutch transmission is representative and that other gear set, synchronizer, and shift actuator arrangements are possible for the dual clutch transmission 10 without departing from the scope of the present invention

It should be further appreciated that the operation of the dual clutch transmission 10 is managed by some type of control device such as an electronic control unit (ECU) that oversees the functioning of the transmission 10, or by an electronic control unit for the vehicle in which the dual clutch transmission 10 may be installed In any event, there exists a control device, beyond the scope of this invention, that controls and operates the dual clutch transmission through a stored control scheme or seπes of control schemes of which the present invention is merely a part The control device having the capability of providing the proper voltages, signals, and/or hydraulic pressures to operate the transmission 10 and particularly the clutch engagement functions

The first and second clutch mechanisms 32 and 34 of the dual clutch assembly 12 are operatively engaged and disengaged in a coordinated manner relative to the actuator of the various gear sets by the synchronizer 24 to selectively transfer torque to the output shaft 20 By way of example, if torque is being transferred to the drive wheels of the vehicle to initiate movement from a standing start, the lowest, or first, gear ratio of the dual clutch transmission 10 will likely be engaged Therefore, as shown in Figure 1 , synchronizer 78 will be driven to the left to engage the first counter gear 52 to the counter shaft 18 and the first clutch mechanism 32 will be engaged to transfer torque from the engine to the output shaft 20 through the first gear set When vehicle speed increases and the ECU determines that the conditions require a shift to the second gear set, synchronizer 80 will first be driven to the right to engage the second counter gear 54 to the counter shaft 18 Then the second clutch mechanism 34 will be engaged as the first clutch mechanism 32 is disengaged In this manner, a powershift, where no power interruption occurs, is affected This powershift changeover of the clutches 32 and 34 occurs for each shift change of the dual clutch transmission 10 As the inactive clutch (now the on-coming clutch) is engaged, the load applied causes a surge of power to be transferred across the clutch with an accompanying generation of heat from the slip that occurs across the clutch The temperature of the on-coming clutch rapidly increases, or spikes, to a point where the clutch plates or the friction material could be damaged if proper cooling is not provided Additionally, the heat build-up, if not properly dissipated, will greatly increase the overall temperature of the dual clutch transmission 10 and may cause the damaging effects mentioned above Simultaneously, while the temperature of the on-coming clutch is sharply rising, the disengaging, or off-going, clutch will cease transmitting torque With the removal of the load, the disengaged clutch will stop generating heat, thus sharply lowering its cooling requirement

A hydraulic circuit for controlling and cooling the clutches 32, 34 of the dual clutch transmission is generally indicated at 110 in Figure 2, where like numerals are used to designate like components throughout the figures The hydraulic circuit 110 includes a source of pressurized cooling, generally indicated at 112 In addition, the hydraulic circuit 110 includes an actuation circuit, generally indicated at 114, that delivers pressurized fluid used to actuate components of the dual clutch transmission, such as the clutches 32, 34 as well as similar components Moreover, the hydraulic circuit 110 also includes a cooling circuit, generally indicated at 116, that delivers pressurized fluid used to lubπcate and cool components of the dual clutch transmission such as the clutches 32, 34 and the gears descπbed above

The actuation circuit 114 includes first and second clutch actuation valves, generally indicated at 118, 120 that are similarly in fluid communication with the source of pressurized cooling fluid 112 Each of the first and second clutch actuation valves 118, 120 correspond to one of the two clutches 32, 34 of the dual clutch transmission and are adapted to provide pressurized fluid to each of the corresponding ones of the clutches 32, 34 of the dual clutch transmission to actuate the clutches The actuator circuit 114 also includes a shift actuation system, generally indicated at 122, that is in fluid communication with the source of pressurized fluid 112 and acts to selectively provide fluid power to the shift actuators 26 so as to actuate the synchronizers 24 and select a designated gear among the plurality of gears

The cooling circuit 116 includes a lube valve, generally indicated at 124, that is similarly disposed in fluid communication with the source of pressurized fluid 112 and acts to provide fluid for purposes of lubπcatmg and coohng each of the clutches of the dual clutch transmission via clutch lube line 125 A lube control actuator, generally indicated at 126 is in fluid communication with the lube valve 124 and is adapted to selectively contro 1 the lube valve, as will be described in greater detail below The coohng circuit 116 also includes a clutch support lube delivery line 128 that is in fluid communication with the source of pressurized fluid 112 and is adapted to provide pressurized cooling fluid to the clutches 32, 34 of the dual clutch transmission The clutch support lube delivery line 128 is employed to provide pressurized fluid to bearings and other inner workings of the clutches to keep them cool In addition, the cooling circuit 116 includes a gear lube delivery line 130 that is in fluid communication with the source of pressurized fluid 112 and acts to provide pressurized cooling fluid to the gears of the dual clutch transmission Each of these components of the hydraulic circuit 110 illustrated in Figure 2 will be described in greater detail below

A main pressure regulator, generally indicated at 132, is disposed in fluid communication with the source of pressurized fluid 112 and adapted to provide a predetermined set system pressure for the hydraulic circuit 110 The source of pressurized fluid 112 includes a first pump 134 that is operatively driven by the internal combustion engine of the hybrid vehicle In addition, the source of pressurized fluid 112 also includes a second pump 136 that is operatively driven by the electric motor 138 Each of the first and second pumps 134, 136 draws coohng fluid from a sump 140 through a filter 142 and supplies the pressurized coohng fluid through a main pressure line 144 to the main pressure regulator 132 A coohng unit 146 is in fluid communication with the source of pressurized fluid through line 148 and is adapted to exchange heat from the cooling fluid with other media The heated cooling fluid flows past a restπctor 150 through the coohng unit 146 and is then distributed throughout the coohng circuit 116 A pair of check valves 152, 154 is disposed in series and in fluid communication with the second pump 136 The first pump 134 operates to supply pressurized fluid to the actuator circuit 114 and the cooling circuit 116 when the first pump 134 is operatively driven by the internal combustion engine The second pump 136 acts to supply pressurized fluid to the coohng circuit 116 when the first pump 134 is operatively driven by the internal combustion engine under certain predetermined conditions as will be explained in greater detail below and the first check valve is open In addition, the second pump also acts to supply pressurized fluid to both the actuation circuit 114 and the cooling circuit 116 when the internal combustion engine is no longer operatively driving the first pump 134 and the first and second check valves 152, 154 are open The interaction of the first and second pumps 134, 136 as well as the check valves 152, 154 with the internal combustion engine and electric motor 138 of the hybrid engine will be described in greater detail below

The main pressure regulator 132 maintains the pressure in the regulated line 156 at a predetermined operating pressure, or set point as will be described in greater detail below The main pressure regulator 132 is schematically shown in Figure 2 in its closed position and includes a valve body 158 with a valve member 160 movably supported within the valve body 158 The main pressure regulator 132 also includes internal flow passages, generally indicated at 162 and a biasing member 164 which acts on the valve member 160 to bias it to the right as illustrated in this figure Pressure in the main pressure line 144 is supplied to the right side of the main regulator valve 132 through a flow restπctor 166 that reduces the flow volume but maintains the applied pressure Fluid pressure is delivered to the right side of the main pressure regulator 132 and overcomes the spring force of the biasing member 164 and moves the valve member 160 of the main pressure regulator 132 to the left from the closed position to the middle operating position. A regulating control line 168, shown as a dotted line in Figure 2, provides a controllable biasing force to the left side o f the main pressure regulator 132 The regulating control line 168 delivers a portion of the system pressure to the left side of the main pressure regulator 132 under the control of the line pressure control valve 170

The line pressure control valve 170 is electrically operated by an electronic control unit (ECU) to set the regulated pressure set point within the hydraulic circuit 110 and then to maintain the desired pressure by regulating the output pressure to the set point The line pressure control valve 170 supplies a varying portion of the available main pressure through the regulating line 168 to the main pressure regulator 132 by bleeding off some portion of the main pressure that is supplied through the filter 172 to the valve 170 More specifically, the line pressure control valve 170 is schematically illustrated in Figure 2 and includes a valve body 174, a valve member 176 movably supported by the valve body 174, and a solenoid 178 The solenoid 178 is adapted to move the valve member 176 of the line pressure control valve 170 to produce a flow area through the valve that is a function of the current delivered to the solenoid 178 and to deliver a predetermined amount of pressurized fluid to the left side of the main pressure regulator 132 through a flow restπctor 180 to assist m moving the valve member 160 of the main pressure regulator 132 to the closed position and against the force generated by the cooling fluid acting on the right side of the valve member 160 through the flow restnctor 166 In this manner, the line pressure control valve 170 sets the desired output pressure set point for the main pressure regulator 132 The line pressure control valve 170 then varies the pressure in the regulating control line 168 to maintain the output pressure delivered from the main pressure regulator 132 about the desired output pressure set point while accounting for fluctuations in the output pressure due to downstream pressure changes The main pressure regulator 132 also provides control over rapid increases, or surges, in the main pressure line 144 that exceeds the immediate correctability of the line pressure control valve 170 The main regulator valve member 132 opens additional flow passages that not only allow for the continued flow of fluid through the main pressure regulator 132 to the regulated line 156, but also allow a portion of the increased flow to pass to the cooling circuit 116 via cooling fluid line 180 as well as the suction line 182 The suction line 182 normally remains closed off by the main pressure regulator valve member 132 However, when a sharp or rapid increase of pressure in the main pressure line 134 drives the main pressure regulator valve member 160 all the way to the left, a corrective portion of the flow is fed back to the suction side of the first pump 134 As the suction line 182 bleeds off the surge of excessive pressure flow, the main regulator valve member 132 moves back to the middle position

The regulated line 156 supplies pressurized fluid to the actuation circuit 114 The actuation circuit 114 supplies the first and second clutch actuation valves 118, 120 via filtered line 184 and associated branches 186, 188 Before reaching each of the first and second clutch actuation valves, the fluid is filtered at 190 Each of the first and second clutch actuation valves 118, 120 includes a valve body 192, a valve member 194 movably supported within the valve body 192 and a solenoid 196 The solenoid 196 is adapted to move the valve member 194 to produce a flow area through the clutch actuation valves 118, 120 to deliver a predetermined amount of pressurized fluid to each of the clutches 32, 34 through delivery lines 198, 200, respectively, thereby selectively actuating same The first and second clutch actuation valves 118, 120 are controlled by the ECU to selectively engage and disengage the respective clutch A valve return line 202 provides a biasing force through a flow restπctor 204 in a direction opposite to the actuation of the solenoid 196 Similarly, a valve balance line 206 provides additional force through a flow restπctor 208 on the solenoid side of the valve member 194 Each of the first and second clutch actuation valves 118, 120 also includes an output filter 210 and a relief valve 212 downstream of the clutch actuation valves and in advance of the clutches to provide a maximum upper limit for the pressure supplied to actuate the clutches In their non-operative mode, each of the first and second clutch actuation valves 118, 120 returns any pressurized fluid to the sump 140 As shown in Figure 2, each of the first and second clutch actuation valves 118, 120 is shown in its non-operative position

As noted above, the actuator circuit 114 also includes a shift actuation system, generally indicated at 122, that is in fluid communication with the source of pressurized fluid 112 and acts to selectively provide fluid power to the shift actuators 26 so as to actuate the synchronizers 24 and select a designated gear among the plurality of gears More specifically, the shift actuation system 122 includes first and second multiplex valves 214, 216 as well as first and second actuator regulator valves 218, 220 that are in fluid communication with the source of pressurized fluid 12 The first and second regulator valves 218, 220 include a valve member 221 and operate to direct pressurized fluid to opposite sides of the shift actuators 26 The first and second multiplex valves

214, 216 are operable to select a predetermined pair of adjacent gears among the plurality of gears to which the pressurized fluid is delivered from the first and second actuator regulators 218, 220

First and second regulator control valves 222, 224 are in fluid communication with the first and second actuator regulator valves 218, 220 through control lines 226, 228, respectively Thus, the first and second regulator control valves 222, 224 are adapted to selectively control the first and second actuator regulator valves 218, 220 To this end, each of the first and second regulator control valves 222, 224 is in fluid communication with the source of pressurized cooling fluid 112 and includes a valve body 230, a valve member 232 movably supported in the valve body 230, and a solenoid 234 The solenoid 234 is adapted to move the valve member 232 of the associated first and second regulator control valves 222, 224 to produce a control signal pressure to the valve member 221 of the respective one of the first and second actuator regulator valves 218, 220 to move the valve member 221 against the bias of the biasing member 223 to open a respective one of the first and second actuator regulator valves 218, 220 In this way, the first and second actuator regulator valves 218, 220 deliver a controlled, predetermined amount of pressurized fluid through the first and second multiplex valves 214, 216 to move a predetermined shift actuator 26 and an associated synchronizer 24 to select a predetermined gear among the plurality of gears of the dual clutch transmission In a similar way, each of the first and second multiplex valves 214, 216 is controlled by an on/off solenoid valve 236, 238 In turn, each of the on/off solenoid valves 236, 238 are controlled by the ECU As noted above, the cooling circuit 116 includes a lube valve 124 that is in fluid communication with the source of pressurized fluid 112 and adapted to control the flow of pressurized fluid to the clutches of the dual clutch transmission More specifically, the main pressure regulator 132 is disposed in fluid communication between the pumps 134, 136 and the lube valve 124 via delivery line 240 A cooler limit valve 242 is operatively connected in fluid communication with the lube valve 124 to provide a maximum upper limit for the positive pressure provided through the main pressure regulator 132 to the lube valve 124 via line 240 and branch 244 The lube valve 124 includes a valve body 246 and a valve member 248 movably supported in the valve body 246 to selectively and independently provide a flow of cooling fluid to each of the clutches 32, 34 of the dual clutch transmission through clutch lube line 125 To this end, the lube valve 124 includes a biasing member 247that acts on the valve member to bias it to a normally closed position As noted above, a lube control actuator 126 is in fluid communication with the lube valve

124 and is adapted to selectively control the lube valve Accordingly, the control actuator 126 is in fluid communication with the source of pressurized cooling fluid 112 through the line 249 via the filter 250 The control actuator 126 includes a valve body 252, a valve member 254 movably supported by the valve body 252 and a solenoid 256 The solenoid 256 is adapted to move the valve member 254 of the lube control actuator 126 to produce a flow area through the control actuator that is a function of the current delivered to the solenoid 256 and to deliver a predetermined amount of pressurized fluid through line 258 (shown as dotted lines) to the right side of the valve member 248 of the lube valve 124 (as illustrated in Figure 2) through a flow restπctor 260 A feedback line 262 bleeds pressure from the pressurized fluid line 258 and delivers it to the left side of the control actuator 126 as illustrated in Figure 2 to assist in returning the valve members 254 to its closed positions In this way, a controlled amount of cooling fluid is provided to the right hand side of the lube valve 124 to move its valve member 248 against the bias of the biasing member 248 to selectively open the lube valve, thereby delivering a controlled, predetermined amount of cooling fluid to the clutches of the dual clutch transmission In operation, pressurized cooling fluid is provided to the actuation circuit 114 and the cooling circuit 116 by the first and second pumps 134, 136 When the internal combustion engine of the hybrid vehicle is operable, it drives the first pump 134 Under this operating condition, pressurized fluid is provided to the main pressure regulator 132 via main pressure line 144 The main pressure regulator 132 sets the system pressure in the hydraulic circuit 110 Pressurized fluid is provided to the actuation circuit 114 through the regulated line 156 via the branch 264 taken off the main pressure line 144 at a point schematically illustrated at 266 The pressurized fluid flows through the regulated line 156 to the filtered line 184 The filtered line 184 supplies pressurized fluid to the first and second clutch actuation valves 118, 120 as well as the shift actuation system 122 as described above

When the internal combustion engine is operable, the first pump 134 also supplies pressurized fluid to the cooling circuit 116 Thus, pressurized fluid flows fromthe main pressure regulator 132 and into the cooling circuit 116 via cooling fluid line 180 More specifically, pressurized cooling fluid flows through the cooling fluid line 180 to the clutch lube support line 128 as well as the gear lube 130 via branch 268 Branch 268 also supplies pressurized fluid to the lube valve 124 via line 240

The output of the first pump 134 is a function of the RPM's of the internal combustion engine Under conditions of low speed, but high heat, the pressure in the cooling circuit 116 may drop below a predetermined value, such as five bars When the internal combustion engine is operatively driving the first pump 134 and the fluid pressure in the cooling circuit 116 drops below a predetermined value, the hydraulic circuit 110 of the present invention is designed to use the second pump 136 to assist the first pump to provide pressurized fluid to the cooling circuit 116 More specifically, when so commanded, the second pump 136 may be driven by the electric motor 138 (even when the internal combustion engine is operating) to supply pressurized fluid to the cooling circuit 116 Thus, when the pressure in the cooling circuit 116 is below a predetermined value, the first check valve 152 will unseat in response to fluid pressure delivered by the second pump 136 Cooling fluid will then flow through the branch 270 to the lube valve 124 via line 240 via the joint schematically illustrated at 272 Cooling fluid will also flowintothe cooler bypass 274 and then to the gear lube line 130 via the joint 272

When the internal combustion engine is no longer operable, the second pump 136 assumes full responsibility for supplying pressurized fluid to both the actuation circuit 114 and the cooling circuit 116 More specifically, when the first pump 134 is off and the second pump 136 is operable, both first and second check valves 152, 154 will unseat to provide pressurized fluid to the actuation circuit 114 via regulated line 156 and the cooling circuit 116 via branch 270, line 240 and cooler bypass 274 Pressurized cooling fluid will also be supplied from the main pressure regulator 132 to the cooling circuit 116 via line 180 and clutch lube support line 128

The pressure in the hydraulic circuit 110 is regulated by the main pressure regulator 132 The main pressure regulator 132 is controlled by the pressure control valve 170, which in turn is controlled by the ECU to establish a system pressure Similarly, first and second clutch actuation valves 118, 120 are controlled by the ECU to selectively provide pressurized fluid to the clutches 32, 34 through delivery hnes 198, 200, thereby actuating same The lube control actuator 126 is similarly controlled by the ECU to provide a predetermined amount of pressurized fluid which acts on the right hand side of the lube valve 124 More specifically, the solenoid 256 of the lube control actuator 126 is adapted to move its valve member 254 to produce a flow area through the lube control actuator 126 that is a function of the current delivered to the solenoid 256 and to deliver a predetermined amount of pressurized fluid through line 258 to the πght side of the valve member 248 of the lube valve 124 This in turn controls the actuation of the lube valve 124 to provide a selected, predetermined amount of cooling fluid to each of the clutches 32, 34 of the dual clutch transmission Similarly, the shift actuation system 122 is controlled by the ECU to provide pressurized fluid delivered via regulated line 156 and filtered line 184 through the first and second actuator regulator valves 218, 220 and first and second multiplex valves 214, 216 to control shifts between the gears of the dual clutch transmission

Thus, the dual clutch transmission used for a hybrid vehicle of the present invention is configured such that both the first and second pumps 134, 136 may be operable to supply pressurized fluid to the hydraulic circuit when necessary This may occur, as explained in greater detail above, when the pressure delivered to the cooling circuit 116 drops below a predetermined value In this case, the second pump 136 driven by the electπc motor 138 assists the first pump 134 to provide cooling fluid to the cooling circuit 116 when the first check valve 152 is open This arrangement allows for the use of a smaller capacity mechanically driven first pump 134 and thereby reduces the cost of the transmission

It should also be appreciated that other routing arrangements may also be employed without departing from the scope of the present invention

The invention has been described in an illustrative manner It is to be understood that the terminology that has been used is intended to be in the nature of words of descnption rather than of limitation Many modifications and variations of the invention are possible in light of the above teachings Therefore, within the scope of the claims, the invention may be practiced other than as specifically described