DE102006045122A1 - Electrically adjustable transmission for vehicle, has torque transmission mechanisms engageable for initializing electrically adjustable backward operating mode with input branching and electrically adjustable forward drive operating mode - Google Patents

Abstract

The transmission (14) has planetary gear sets (20, 30, 40) comprising corresponding elements, where a drive element (17) and an output element (19) are permanently connected with different elements of the gear sets. A motor/generator (80) is permanently connected with one of the elements, which is not connected with the drive element or is connected with the other gear set. Torque transmission mechanisms (50, 52, 54) are engageable for initializing an electrically adjustable backward operating mode with input branching and an electrically adjustable forward drive operating mode.

Description

TECHNICAL AREA

The The present invention relates to electrically variable transmissions with selective operation in both variable speed ratio ranges with power split as well as in fixed speed ratios, the three planetary gear sets, has two motor / generators and multiple torque-transmitting mechanisms, for an extended reverse performance and an efficient electric forward drive mode to reach, which improves the regenerative braking ability.

BACKGROUND OF THE INVENTION

Internal combustion engines, in particular those of the type with reciprocating piston, currently most drift Vehicles on. Such machines are relatively efficient, compact, lightweight and inexpensive mechanisms, through the highly concentrated energy in the form of fuel in usable mechanical power is converted. A novel transmission system, that are used with internal combustion engines and fuel consumption and reduce emissions can be of great benefit to the population be.

The wide fluctuation of the requirements, the vehicles typically put on internal combustion engines, increases fuel consumption and the emissions over the ideal case for such machines addition. Typically, a vehicle is a vehicle such machine driven out of a cold state started a small electric motor and relatively small electric storage batteries and then quickly under the loads of the drive and accessory unit is set. Such a machine is also by a wide Range of speeds and a wide range of loads and typically with an average of about one-fifth of their maximum output power operated.

One Vehicle transmission typically gives mechanical power of one Machine to the rest of a drive system, such as a fixed final drive, Axles and wheels, from. A typical mechanical transmission allows a certain freedom in the operation of the machine, usually by alternative selection of five or six different drive ratios, a neutral selection that allows that the machine operates auxiliary units when the vehicle is stationary and clutches or a torque converter for smooth transitions between drive ratios and to the vehicle from standstill with the machine rotating start. The transmission gear selection typically allows for that Power from the machine to the rest of the drive system with one ratio of Torque multiplication and speed reduction, with a ratio of Torque reduction and speed multiplication, as an overdrive is known, or delivered with a reverse gear ratio becomes.

One Electric generator can produce mechanical power from the machine convert into electrical power, and an electric motor can this electric Performance back in mechanical power with different torques and speeds for the Convert remainder of vehicle drive system. This arrangement allows a stepless adjustment in the ratio of torque and speed between the machine and the rest of the drive system within the limits of electrical machinery. An electric storage battery, which as a source of power for the drive is used, this arrangement can be added, whereby a series hybrid electric drive system is formed.

The Row hybrid system leaves to that the machine with a certain independence from the torque, the speed and power required to drive a vehicle can drive, work, so that the machine on improved emissions and an improved efficiency can be controlled. This System leaves to that the electric motor attached to the internal combustion engine is, as engine for starting the internal combustion engine can act. This system lets Also, that the electric motor attached to the rest of the powertrain attached, acts as a generator, taking energy from the slowing down of the vehicle in the battery recovered by regenerative braking becomes. A series electric drive has problems in terms of weight and the cost of a sufficient electrical machinery to the total power the internal combustion engine from mechanical to electrical in the generator and from electrical to mechanical in the drive motor, and regarding the useful energy loss in these conversions.

One Power split transmission may use a so-called "differential gear" to a continuously variable torque and speed ratio between Drive and output to achieve. An electrically adjustable transmission can use a differential gear set to a fraction his transferred To transmit power through a pair of electric motors / generators. Of the Rest of his power is flowing through another parallel path that is completely mechanical and direct with a fixed gear ratio or alternatively selectable is.

One As known to those skilled in the art, a planetary gear set may take the form of a Form differential gear. A planetary gear arrangement is usually the preferred one embodiment, which is used in inventions with differential gear, with the advantages of compactness and different torque and speed ratios between all elements of the planetary gear set. It is possible, however Invention without planet gears such as through the use of bevel gears or other gears in an arrangement in which the rotational speed of at least an element of a gear set always a weighted average of speeds of the other two elements is.

One Transmission system of a hybrid electric vehicle also includes one or a plurality of electrical energy storage devices. The typical device is a chemical storage battery, but it can also capacitive or mechanical devices, such as an electric powered flywheel, be included. An electrical energy store allows, that the mechanical output power from the transmission system to the vehicle from the mechanical input from the machine may differ to the transmission system. The battery or other device also allows starting the internal combustion engine with the transmission system and regenerative braking of the vehicle.

One electrically adjustable transmission in a vehicle can be easy transferring mechanical power from an engine input to an axle drive output. To do this, the electrical power produced by a motor / generator resembles is, the electrical losses and the electrical power that is consumed by the other engine / generator. By the Use of the above-mentioned electric storage battery can electrical power generated by a motor / generator bigger or less than the electrical power consumed by the other one becomes. Electric power from the battery can sometimes allow that both motors / generators act as motors, in particular to the internal combustion engine in accelerating the vehicle too support. Both engines can sometimes act as generators to recharge the battery, in particular during regenerative braking of the vehicle.

A successful replacement for the inline hybrid transmission is the electrically variable transmission with two sections, input split and compound split (two-range, input-split and compound-split electrically variable transmission), which is now manufactured for regular buses, as in U.S. Patent Number 5,931,757 , issued August 3, 1999 to Michael Roland Schmidt, which is commonly assigned to the present application, the disclosure of which is incorporated herein by reference in its entirety. Such a transmission uses a drive means to receive power from the vehicle engine, and a power output means to output power for driving the vehicle. A first and second motor / generator are connected to an energy storage device, such as a battery, so that the energy storage device can receive and supply power from the first and second motor / generators. A control unit regulates the power flow under the energy storage device and the motor / generators and between the first and second motor / generator.

One Operation in the first or second mode with variable speed ratio can selectively using couplings in the nature of a first and second torque transmitting device be achieved. In the first mode becomes a speed ratio range formed with input power branching by engagement of the first clutch, and the output speed of the transmission is proportional to the speed from a motor / generator. In the second mode becomes a speed ratio range formed with Verbundleistungszwezweigung by the engagement of the second clutch and the output speed of the transmission is not proportional to the speeds of one of the engines / generators but is one Algebraic linear combination of the speeds of the two motor / generators. An operation with a fixed transmission speed ratio can selectively by the engagement Both clutches are achieved. An operation of the transmission in one neutral mode of operation can be selectively achieved by both Clutches are loosened, the machine and both electric motors / generators of the Transmission output can be decoupled. The transmission includes at least a mechanical point in its first mode and at least two mechanical points in its second mode.

U.S. Patent No. 6,527,658 published on March 4, 2003, for Holmes et al. disclosed and incorporated herein by reference in its entirety, discloses an electrically variable transmission employing two planetary gear sets, two motor / generators, and two clutches to provide input-split modes; Provide composite-split and neutral and reverse modes of operation. Both planetary gear sets can be simple or one can be individually assembled. An electrical control regulates the power flow between an energy storage device and the two motor / generators. This transmission provides two ranges or modes of electrically variable transmission (EVT) operation by selectively providing an input-split speed range and a compound-split speed ratio range. It can also be selectively achieved a fixed speed ratio.

hybrid systems can the fuel economy of a vehicle on a variety of ways to improve. For example, the machine may be idling, while periods with delay and Brakes and while periods with operation at low speed or light load be switched off to efficiency losses due to the train to eliminate at the machine. Trapped braking energy (via regenerative braking) or energy stored by one of the engines that while Periods, in which the machine works, acts as a generator, during this periods used with the machine off. A temporary need for engine torque or engine power is provided by the motor / generators during the Operation in electrically adjustable modes with switched on Machine supplements, which allows a smaller dimensioning of the machine, without the outstanding performance of the vehicle. additionally The machine can be at or near the point with optimum Efficiency for operate a given power requirement. The engine / generator is capable of kinetic energy of the vehicle during the Brake to be used, which is used, the machine off longer to supplement and / or contribute engine torque or engine power to operate at a lower engine speed, or the accessory power supply to support. additionally the motor / generators are very powerful in power generation for the ancillaries efficient, and electrical power from the battery serves as an available torque reserve, what an operation at a numerically low speed ratio of Transmission allowed.

SUMMARY OF THE INVENTION

One Transmission is with a reverse mode with input branching and preferably with a low fixed one Provided reverse speed ratio, that provides sufficient backward climb performance, while it allows that the engine size and the Planetenrad- and gear ratios on fuel economy or other design criteria can be optimized. A key advantage opposite to this construction other EVT designs for backwards, that he electrical power flow in both forward and Reverse modes forward (not circulating). Circulating electrical power in an EVT refers to a condition in which the mechanical Way transported more than 100% of the output power. Under conditions of a normal electric power flow forward, will the machine power branches, with a certain amount of electrical and the rest mechanically transferred becomes. When a typical EVT works backwards, if the direction of electrical power flow is reversed, so that the mechanical way the full output power plus the electric Must transport power. Under this condition one says that the electrical power circulates in the system. That's why they have to Torque and the power of the electric path for more than 100% of the output torque and the output power. rated to absorb the circulating performance. The maximum output torque a typical EVT is obtained using battery power, when the machine is not generating torque.

The maximum output torque of the electrically variable transmission of the present invention is obtained with the machine on, which is a more robust performance results. Due to the improved reverse performance, are the typically recommended increase in engine size and / or the higher ones Transmission or planetary gear ratios not required to achieve sufficient backward climb performance.

Accordingly an electrically variable transmission comprises a drive element, to receive power from a machine, an output element, and a first and second motor / generator. A first, second and third planetary gear each have a first, second and third element, wherein the drive element and the output element constantly associated with a different element of the elements. A first connecting element connects an element of the first planetary gear set constantly with an element of either the second or the third planetary gear set, that constantly connected to the second motor / generator. A second and a third connecting element each connect a different Element of the elements of the second planetary gear constantly with each a different element of the elements of the third Planetary gear set.

With reference to the first, second and third gear sets in this specification and in the claims, these sentences may be numbered "first to third" in any order in the drawings (ie left to right, right to left, etc.). ). In addition, the first, second or third element of each gear set in the drawings may be arbitrary for each gear set Order from "first" to "third" (ie top to bottom, bottom to top, etc.).

It are at least three torque-transmitting mechanisms provided, which include a first torque-transmitting mechanism, the this serves to be an element of the first planetary gear that is constantly with is connected to the drive element, selectively with an element of the second planetary gear set, which selectively with a fixed Element over a second torque transmitting mechanism is connectable to connect. A third torque transmitting mechanism is used to an element of the second or third planetary gear, the not connected to any of the other planetary gear sets, selectively to connect with the fixed element. The first motor / generator is constantly with the element of the first planetary gear that does not match the Drive element or connected to the other planetary gear sets is connected. The third torque transmitting mechanism is selectively engageable, a first electrically adjustable forward mode with input branching and is the first torque-transmitting mechanism selectively engageable, to provide a second electrically variable forward mode with compound branching.

The Output element is preferably always with an element of the second or third planetary gear set that is not constantly is connected to the element of the first planetary gear set and not selectively connectable to the fixed element.

The Torque transmission mechanisms are engageable an electrically variable reverse mode with input branching and an electric forward drive mode provide. The electric forward drive mode, i. in the the machine is off, lets to that the engines at higher Speeds and lower torques work the same way To achieve output torque, resulting in egg nem improved efficiency leads. The regenerative braking is during the electric forward drive mode more efficient than while an electrically adjustable mode performed at the two motors supply torque have to and the speeds of the motors are low. In addition, train is on the machine (which further reduces the efficiency) in the electric forward drive mode eliminated.

The Electrically adjustable transmission can be determined by a lever diagram to be discribed. For example, the first, second and third element of the first planetary gear set by a first lever of a lever diagram showing a first, second and third node, each of the first, second and third element correspond. additionally two of the elements of the second planetary gear set are constantly with two the elements of the third planetary gear set (for example, via the above-described second and third connecting elements). That's why the second and third planetary gear set by a second composite Lever be represented in the lever diagram. The second lever has a fourth, fifth, sixth and seventh nodes on the second and third planetary gear sets correspond. The first node is constantly with the fourth node connected. The drive element is constantly with the second node connected. The first motor / generator is constantly connected to the third node connected, and the second motor / generator is constantly connected to the fourth node connected. The first torque-transmitting mechanism serves to selectively connect the first node to the fifth node, and the second torque transmitting mechanism serves to the fifth node selectively connect to the fixed element. The output element is constantly connected to the sixth node, and the third torque-transmitting mechanism serves to selectively connect the seventh node to the fixed element connect to.

According to one Aspect of the invention, the second torque transmitting mechanism is selective engageable around the electrically adjustable reverse mode with input branching, and the first and second Torque-transmitting mechanism are selectively engageable, around the electric forward driving mode provide. Torque of the first motor / generator becomes torque of the second motor / generator in the electric forward drive mode added. Furthermore the first and third torque-transmitting mechanisms are selective engageable to to provide a fixed forward speed ratio.

Optionally, a fourth torque-transmitting mechanism can be added to the transmission. The fourth torque-transmitting mechanism serves to selectively connect any two elements of the first planetary gear set, causing all of the elements of the first planetary gear to revolve at the same speed (thereby causing the first planetary gearset to be "locked" and inactive by increasing the tooth ratios of the first planetary gearset) first planetary gear set does not affect the overall transmission ratio of the transmission). The second and fourth torque transmitting mechanisms are engageable to provide a fixed reverse speed ratio. The fixed reverse speed ratio allows the efficiency of a purely mechanical power flow path in the Reverse direction to. The first torque transmitting mechanism and the fourth torque transmitting mechanism are engageable to provide a fixed forward speed ratio, and the third torque transmitting mechanism and the fourth torque transmitting mechanism are selectively engageable to provide a different fixed forward speed ratio. Thus, three fixed forward speed ratios are provided with the first, second, third and fourth torque transmitting mechanisms.

Regarding of the lever diagram described above is the fourth torque-transmitting mechanism in addition, any two of the first, second and third nodes selectively connect.

It can additional Torque transmitting mechanisms be applied to additional fixed forward speed ratios to reach. For example, a fifth torque-transmitting mechanism, which serves to selectively connect the second motor / generator to the stationary element to be applied. The first torque-transmitting mechanism and the fifth Torque-transmitting mechanism are selectively engageable, to provide a fixed forward speed ratio, whereby with the first, second, third and fourth torque-transmitting mechanism a sum of four fixed forward speed ratios is produced. additionally can a sixth torque-transmitting mechanism, which serves to selectively connect the first motor / generator with the fixed one Element to be applied. The first and sixth torque-transmitting mechanisms are selectively engageable, to provide a fixed forward speed ratio, and the third and sixth torque-transmitting mechanisms selectively engageable, to provide another fixed forward speed ratio. Accordingly, you can with all six torque-transmitting mechanisms six fixed forward speed ratios be achieved. additionally the second and sixth torque-transmitting mechanisms are selective engageable to provide a fixed reverse speed ratio.

specific embodiments of the gearbox with respect to the first, second and third elements of each gear set which are a ring gear, a planet carrier and a sun wheel are. For example, in some embodiments the first motor / generator constantly connected to the sun gear of the first planetary gear set, and the second connecting element connects the ring gear of the second planetary gear set constantly the carrier of the third planetary gear set. In some embodiments, the third connects Connecting element the carrier the second planetary gear set constantly with the ring gear of the third planetary gear set.

In some embodiments the first connecting element connects the ring gear of the first planetary gear set constantly with the sun gear of the second planetary gear set.

In some embodiments can an element of the first planetary gear set constantly with an element of the second or third planetary gear set via the first connecting element be connected where the first connecting element with the second Motor / generator is connected. The element of the second or third Planetary gear set is also constantly connected to the second motor / generator; That's why it connects first connecting element, the element of the first planetary gear constantly with the element of the second or third planetary gear via the second motor / generator.

The Transmission also offers the efficiency of regenerative braking. An energy storage device is provided which serves supplying power to the first and second motor / generators, or To receive power from these. Furthermore, a controller is provided, which serves to transmit the power between the energy storage device and the first and second To control motor / generator. The controller causes during the Braking at least one of the first and second motor / generators acts as a generator to the rotational energy of the output element into power stored in the energy storage device becomes. The regenerative braking preferably occurs during the electric forward drive mode on. This can be more efficient than regenerative braking during the second electrically adjustable forward mode, since the train on the machine is eliminated when the machine is switched off is, and both engines have to not necessarily perform torque at low speeds, such as do it while the second electrically adjustable forward mode must.

The Arrangement of the torque transmission mechanisms in the transmission and their engagement plan allows a numerically relative low upper fixed gear ratio in Relation to typical hybrid gearbox designs that fuel economy on the highway can improve.

The above features and advantages and other features and advantages of the present invention will become more apparent from the following detailed description of the best modes for carrying out the invention Connection made with the accompanying drawings easily apparent.

BRIEF DESCRIPTION OF THE DRAWINGS

1 Fig. 12 is a schematic lever diagram representation of an electrically variable transmission of the present invention;

2 is a schematic lever diagram representation of an embodiment of a transmission in the scope of the lever diagram of 1 ;

3 is a schematic lever diagram representation of a second embodiment of a transmission in the scope of the lever diagram of 1 ;

4 is a schematic lever diagram representation of a third embodiment of a transmission in the scope of the lever diagram of 1 ;

5 is a schematic diagram representation of a fourth embodiment of a transmission according to the lever diagram of 2 ;

6 is a schematic diagram representation of a fifth embodiment of a transmission according to the lever diagram of 2 ;

7 is a schematic diagram representation of a sixth embodiment of a transmission according to the lever diagram of 4 ; and

8th is a schematic diagram representation of a seventh embodiment of a transmission according to the lever diagram of 4 ,

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In the drawings, in which like reference numerals refer to similar components, shows 1 a drive train 10 who is a machine 12 which is associated with an embodiment of an electrically variable transmission (EVT), generally designated by the reference numeral 14 is designated. The gear 14 is designed to at least part of its drive power from the machine 12 to recieve. The machine 12 has an output shaft as the drive element 17 of the transmission 14 serves. An axle drive unit 16 is via an output element 19 with the gearbox 14 connected. The gear 14 includes three planetary gear sets in 1 in a lever diagram form, as those skilled in the art will readily understand. A lever or first planetary gear set 20 includes first, second and third nodes A, B and C, respectively. Nodes A, B and C represent first, second and third elements of the first planetary gear set 20 , preferably a ring gear, a carrier and a sun gear, but not necessarily in this order.

The gear 14 also includes a second lever 30 . 40 consisting of two compound planetary gear sets, namely a second planetary gear set 30 and a third planetary gear set 40 consists. The planetary gear sets 30 and 40 also have three elements, which may be a ring gear, a sun gear and a planet carrier. The planetary gear sets 30 and 40 are composed of two elements of the second planetary gear set 30 constantly with two elements of the planetary gear set 40 are connected. In some embodiments, an interconnected pair of elements may be replaced by a single element that is included in both planetary gear sets 30 as well as in planetary gear set 40 is working. In all cases, the compound planetary gear sets 30 . 40 are represented by the second four-node lever having a fourth node D, a fifth node E, a sixth node F and a seventh node G. As explained below on the basis of 2 to 4 illustrated and described, the compound planetary gear sets 30 . 40 through two separate lever diagrams for the gear sets 30 and 40 being represented; however, in any case, there are two elements of the planetary gear set 30 constantly with two elements of the planetary gear set 40 and those skilled in the art will recognize that such a compound planetary gear set may be shown schematically as a single lever or as two separate levers. The two connected pairs of elements of planetary gear sets 30 and 40 are represented by the fifth and sixth nodes E, F. In the lever diagram of 2 to 4 in which the compound planetary gear sets 30 . 40 with two separate levers, the connected nature of nodes E and F becomes apparent.

A first connection element 70 connects the first node A constantly with the fourth node D. The drive element 17 is constantly connected to the second node B. The second node B may also selectively communicate with the fifth node E via a first torque transmitting mechanism 50 get connected. A second torque transmitting mechanism 52 selectively connects the fifth node E to a fixed element 60 like the gearbox. The third node C is constantly with a first motor / generator 80 connected. A second motor / generator 82 is constantly connected to the fourth node D of the compound planetary gear sets 30 . 40 connected. The first and second motor / generator 80 . 82 may also be referred to herein as unit A and unit B, respectively. The sixth node F of the second lever 30 . 40 is constantly with the down drive element 19 connected. Finally, the seventh node G selectively with the transmission housing 60 via a third torque transmitting mechanism 54 get connected.

Three optional torque-transmitting mechanisms may also be used to achieve various operating conditions, as described below. For example, a fourth torque-transmitting mechanism connects 56 (shown in phantom) the second node B, ie the node which is constantly connected to the drive element 17 is connected, via the first connecting element 70 selectively with the first and fourth nodes A, D. In the scope of the invention, the fourth torque-transmitting mechanism 56 but always selectively connecting any two elements of the first planetary gear set to cause all three elements of the first planetary gear set to rotate at the same speed (ie, the fourth torque transmitting mechanism) 56 acts as a lock-up clutch). In addition, a fifth torque-transmitting mechanism connects 58 the second motor / generator 82 selectively with the gearbox 60 , Finally, a sixth torque transmitting mechanism connects 59 the first motor / generator 80 selectively with the gearbox 60 , As will be described below, the torque-transmitting mechanisms are selectively engageable to provide a variety of fixed forward speed ratios, first and second forward variable and composite branch forward modes, an input-split reverse mode, a reverse mechanical mode, and a forward-drive electrical mode. As will be understood by those skilled in the art, assign the first and second motor / generator 80 . 82 each a stator and a rotor (not shown), wherein the rotor is rotatable and the stator is constantly through the transmission housing 60 is fixed.

Each embodiment of the transmission within the scope of the invention includes an electrical power source connected to the motor / generators such that the motor / generators can transmit power to or receive power from the power source. A controller or ECU is connected to the electrical power source to control the distribution of power from or to the power source. An electrical power source may be one or more batteries. Other electrical power sources, such as fuel cells, have the ability to provide or store and deliver electrical power, and may be used in lieu of batteries without altering the concepts of the present invention. An electric power source and a controller will be described with reference to the embodiments of FIGS 5 to 8th shown and described. The embodiments of the 1 to 4 , which are each represented by lever diagrams, also include an electric power source and a controller, although not shown, which are connected to the motor / generators in a similar manner as shown in FIGS 5 to 8th is shown.

Description of the operation

Electrically adjustable reverse mode

The gear 14 FIG. 12 provides an electrically variable reverse mode (which is characterized by a range of reverse speed ratios) that is capable of driving a vehicle (not shown) with the engine off 12 or while the machine is running 12 to approach the vehicle with power backwards. The second torque transmitting mechanism 52 is engaged to establish the electrically-variable reverse mode. When the machine 12 is off, sets the torque transmitting mechanism 52 , which is a fixed torque-transmitting mechanism such as a brake, the node E to the transmission housing 60 determines what a reaction torque provides. The second motor / generator 82 is used to start the vehicle through a reverse reduction gear ratio provided by the compound second and third planetary gear sets, as through the second lever 30 . 40 is shown. For reverse electric operation with the machine off, the machine will remain 12 at zero speed, the second motor / generator 82 has a positive speed and the first motor / generator 80 has a negative speed. To start the machine, the first motor / generator is delayed 80 to a speed of zero while the second motor / generator 82 provides a reaction torque and a torque for driving the vehicle. This allows an acceleration of the machine 12 to a speed at which it can be supplied with fuel. Once the machine 12 running, the power of the machine is controlled by the first planetary gear set by the first lever 20 is shown, and the first motor / generator 80 which generates power while the second motor / generator 82 acts as a motor, split. Thus, power is transmitted to the output member through both a mechanical path and an electrical path 19 transfer. The electric power flow is in the forward direction as long as the first motor / generator 80 has a positive speed. When the first motor / generator 80 delayed to a negative speed, acts a second motor / generator 82 as a generator to the first motor / generator 80 To supply power and thus to provide a machine reaction torque.

Fixed reverse speed ratio

If the optional fourth torque-transmitting mechanism 56 is provided, it can be engaged synchronously when the machine 12 and the motor / generators 80 . 82 operate at speeds that have a transmission speed ratio (ie (speed of the drive element 17 ) / (Speed of output element 19 )), which is equal to a mechanical gear ratio, by engaging the torque-transmitting mechanism 56 provided. As used herein, the terms gear ratio and fixed speed ratio have the same meaning. Alternatively, if the optional sixth torque-transmitting mechanism 59 is provided, it can be engaged synchronously when the machine 12 and the motor / generators 80 . 82 operate at speeds that produce a gear ratio that is equal to a mechanical gear ratio, by engaging the torque-transmitting mechanism 59 provided. In the fixed reverse speed ratio, the motors / generators become 80 . 82 not needed to transfer torque, but you can for an acceleration gain to the machine 12 to be supported, or used as generators.

The electrically variable reverse mode and the fixed reverse speed ratio allow for a ring gear / sun gear tooth ratio of the planetary gear sets transmitted through the first and second levers 20 respectively. 30 . 40 is shown, and that the size of the first and second motor / generator 80 . 82 is optimized for efficient fuel economy or other design criteria. Because the machine 12 while the input-split electrically variable reverse mode is not sufficient, backward climb requirements can be met without the size of the second motor / generator 82 increase and / or use higher planetary gear ratios that would otherwise be required for optimal fuel economy.

First forward mode

The transmission is capable of providing an electrically variable first forward mode characterized by a range of forward speed ratios. A vehicle can through the gear 14 when the machine is switched off 12 or with the machine running in the electrically-variable first forward mode 12 be approached. To produce the electrically variable first forward mode, the third torque transmitting mechanism becomes 54 indented to the node G of the second lever 30 . 40 on the gearbox 60 set. When the machine 12 is off, wherein the third torque transmitting mechanism 54 is engaged, becomes the second motor / generator 82 used to drive the vehicle through the reduction gear ratio caused by the composite second and third planetary gear sets passing through the second lever 30 . 40 are provided. At the beginning, the machine remains 12 at zero speed and the first motor / generator 80 runs in a reverse direction. To the machine 12 To start, the first engine / generator delays 80 to a speed of zero while the second motor / generator 82 provides a reaction torque and a torque for driving the vehicle. This allows an acceleration of the machine 12 to a speed at which it can be supplied with fuel. Once the machine 12 running, machine power is provided by the drive element 17 is delivered by the first planetary gear, passing through the first lever 20 is shown, and the first motor / genes rator 80 which generates power while the second motor / generator 82 acts as a motor, split. Power is transmitted both through a mechanical path (ie through the first planetary gear set 20 and the connecting element 70 ) as well as by an electrical path (ie by the first motor / generator 80 to the second motor / generator 82 ) on the output element 19 transfer. Power flows in the forward direction as long as the first motor / generator 80 has a positive speed. When the speed of the first motor / generator 80 becomes negative, acts the second motor / generator 82 as a generator around the first motor / generator 80 Supply power. Regenerative braking is accomplished using the second motor / generator 82 accomplished and characterized by a direct speed ratio for the output element 19 out.

Electrically adjustable second forward mode

For operation in a second electrically variable forward mode, which is characterized by a numerically lower range of speed ratios, offers the transmission 14 a compound-split mode in which the first torque-transmitting mechanism 50 is engaged and the third torque transmitting mechanism 54 is solved. In this lower range of forward speed ratios, power flows in the forward direction as long as the first and second motor / generators 80 . 82 each have a positive speed. In this lower range acts the second motor / generator 82 as a generator and the first motor / generator 80 acts as an engine. When the speed of the second motor / generator 82 is negative, acts the first motor / generator 80 as a generator to the second motor / generator 82 Supply power. When the speed of the first motor / generator 80 becomes negative, becomes the second Motor / generator 82 a generator to the first motor / generator 80 Supply power.

Regenerative braking can be accomplished in the electrically variable second forward mode by adjusting the torque of the engine 12 and the first and second motor / generator 80 respectively. 82 is brought to equilibrium to the desired deceleration rate of the output element 19 provide.

Fixed forward speed ratios

In both the first and second forward electrically-variable modes, the torque-transmitting mechanisms of the transmission 14 used to provide several fixed forward speed ratios. When the transmission gear ratio reaches a gear ratio equal to that which can be mechanically provided by engagement of two of the torque transmitting mechanisms, the appropriate torque transmitting mechanisms are engaged to provide the fixed gear ratio. If the transmission 14 operating at a fixed forward speed ratio, the motors / generators become 80 . 82 not used to torque from the machine 12 but can be used for acceleration amplification or for regenerative braking. If the optional fourth, fifth and sixth torque-transmitting mechanisms 56 . 58 and 59 are provided, through the gearbox 14 up to six forward speed ratios are provided. There are three fixed forward speed ratios available during the electrically variable first forward mode when the third torque transmitting mechanism 54 is indented. By engaging the fourth torque transmitting mechanism 56 a first fixed speed ratio is provided. At a lower speed ratio, the sixth torque transmitting mechanism 59 be engaged to establish a second fixed forward speed ratio. The sixth torque-transmitting mechanism 59 is then disengaged to allow for an increase in gear ratio in the electrically-variable first forward mode. At an even lower speed ratio, the first torque transmitting mechanism becomes 50 engaged while the third torque transmitting mechanism 54 remains engaged to provide a third fixed forward speed ratio. The first torque-transmitting mechanism 50 is then disengaged to allow the electrically variable first forward mode to be resumed and lower speed ratios to be provided. In order to achieve gear ratios in the electrically-variable second forward mode, the third torque-transmitting mechanism 54 disengaged while the first torque-transmitting mechanism 50 is indented. During the electrically variable second forward mode, three additional fixed forward speed ratios can be achieved. First, the sixth torque transmitting mechanism 59 are engaged to provide a fourth fixed forward speed ratio. At a lower speed ratio, the fourth torque transmitting mechanism 56 be engaged to establish a fifth forward speed ratio. At an even lower speed ratio, the fifth torque transmitting mechanism 58 to establish a sixth forward speed ratio. The sixth fixed forward speed ratio achieved by engagement of the first torque-transmitting mechanism 50 and the fifth torque transmitting mechanism 58 allows an upper gear ratio of only 0.66 (tooth ratios of the example planetary gear set according to paragraph [0078] achieve a sixth fixed gear ratio of 0.661) that is substantially lower than that achieved in overdrive by typical hybrid electrically variable transmissions, and fuel economy the motorway of an automatic transmission with a numerically lower gear ratio closely simulates. The availability of several fixed forward speed ratios allows for the transmission 14 can be operated in a mechanical mode at a variety of speed ratios, as those skilled in the art will readily appreciate, and increase the efficiency of the system.

Electric forward drive mode (regenerative braking) During the electrically variable second forward mode, the transmission stops 14 an electrically forward drive mode. The electric forward drive mode is established by the second torque-transmitting mechanism 52 is engaged while the first torque-transmitting mechanism 50 remains engaged and the fuel to the machine is cut off so that the machine is stopped. In this arrangement, the motors / generators drive 80 . 82 the output element 19 with high ratios of engine speeds to output speed. In addition, the torque is from the first and second motor / generators 80 . 82 additive. In this operating mode, both motors / generators are running 80 . 82 at a high speed relative to the output member 19 around and both delay to the machine 12 to start. Accordingly, the energy of a battery comes with the motor / generators 80 . 82 is connected (the battery is not shown, but is with the motor / generator 80 . 82 connected in a similar way as they are in terms of batteries and the engine / generator of 5 to 8th shown and described) during the start of the machine 12 with stored kinetic energy of the motors / generators 80 . 82 elevated. The kinetic energy of both engines / generators 80 . 82 is higher in the electric driving mode than in the electrically variable second forward mode. Therefore, during the transition, some of this kinetic energy is available at the discretion of the control strategy to either help drive the vehicle or the speed of the engine 12 to increase. The net effect is that less battery power is required than would otherwise be required if the speed of both motors / generators 80 . 82 do not take off.

The gear 14 improves the efficiency of regenerative braking in a medium speed ratio range. In numerically relatively high transmission speed ratios, the transmission offers 14 an efficient regenerative braking, since the second motor / generator 82 directly with the output element 19 is coupled. Likewise, the transmission can 14 operate at numerically low transmission speed ratios in the sixth fixed forward speed ratio described above, thereby providing efficient regenerative braking since the first motor / generator 80 directly with the output element 19 is coupled. However, when the vehicle speed drops below a point at which the sixth fixed forward speed ratio can be used, the transmission operates 14 in the electrically variable second forward mode, which is not as efficient for regenerative braking as the sixth fixed forward speed ratio, since both motor / generators 80 . 82 Must supply torque and the speeds of the motor / generators are relatively low. When the machine 12 is off, the torque of the second motor / generator must be 82 be negative to the torque of regenerative braking acting on the output element 19 is applied, and the negative torque of the first motor / generator 80 compensate. The second motor / generator 82 however, will also have a negative speed, resulting in a positive power flow; wherein there is circulating electric power thereby that the generating power of the first motor / generator 80 will exceed the power flow to the battery. Ideally, each of the motors / generators should 80 . 82 transport a fraction of the regenerative braking power between zero and one, the sum of the fractions being one. Even if the machine 12 is not out and the second motor / generator 82 has a positive speed, are the speeds of the motor / generators 80 . 82 relatively low, and there is a relatively low mechanical benefit, since the torque of the motor / generators 80 . 82 (neglecting the train on the machine) must add to the transmission output torque. When the first motor / generator 80 has a large mechanical benefit, therefore becomes the second motor / generator 82 have a small mechanical benefit or vice versa. By incorporating an additional torque reaction point to set the lever at node E, the mechanical benefit of both motor / generators becomes apparent 80 . 82 elevated. If in addition the machine 12 During the electrically variable second forward mode of operation, the efficiency is further reduced by train on the engine and lower engine speeds. By providing the electric driving mode with the machine off 12 work the motors / generators 80 . 82 at higher speeds and lower torques to the same torque on the output element 19 reach, which leads to an improved efficiency.

First preferred embodiment

In 2 is a first complete preferred embodiment of a powertrain 110 with a gear 114 in the scope of the invention in lever diagram form. The gear 114 uses three differential gear sets, preferably in the nature of planetary gear sets 120 . 130 and 140 , The planetary gear set 120 , which is shown in lever diagram form, uses a ring gear 124 , a planet carrier 129 and a sun wheel 122 at. The ring gear 124 surrounds the sun wheel 122 , The planet carrier 129 rotatably supports a plurality of planet gears, which mesh with both the ring gear 124 as well as the sun wheel 122 engage. The drive element 17 is on the carrier 129 attached. A first motor / generator 180 is constantly with the sun gear 122 connected. The planetary gear set 120 can through the lever 20 from 1 being represented.

The second planetary gear set 130 , which is shown in lever diagram form, uses a ring gear 134 that's a sun gear 132 surrounds. A planet carrier 139 rotatably supports a plurality of planet gears, which mesh with both the ring gear 134 as well as the sun wheel 132 engage.

The planetary gear set 140 applies a ring gear 144 that's a sun gear 142 surrounds. A planet carrier 149 rotatably supports a plurality of planet gears, which mesh with both the ring gear 144 as well as the sun wheel 142 engage. The output element 19 is constantly with the carrier 149 connected.

The ring gear 124 is constantly with the sun gear 132 through a connecting element 170 connected. The sun wheel 132 is constantly with the sun gear 142 and a second motor / generator 182 via a connecting element 172 connected, as shown one or more components can. The ring gear 134 is constantly with the carrier 149 via a connecting element 174 connected.

The ring gear 124 corresponds to the first node A of 1 , The carrier 129 corresponds to the second node B of 1 , The sun wheel 122 corresponds to the third node C of 1 , Because the second and third planetary gear set 130 . 140 two pairs of elements that have two separate fasteners 172 and 174 are composed, are the planetary gear sets 130 and 140 put together and be through the second lever 30 . 40 from 1 shown. The connected sun gear 132 and sun gear 142 are shared by a corresponding fourth node D of 1 shown. The carrier 139 corresponds to the fifth node E of 1 , The ring gear 134 and the carrier 139 correspond to the sixth node F of 1 , The ring gear 144 corresponds to the seventh node G of 1 ,

The first torque-transmitting mechanism 150 is selectively engageable to the wearer 129 with the carrier 139 connect to. The second torque transmitting mechanism 152 is selectively engageable to the wearer 139 on the gearbox 160 set. The third torque-transmitting mechanism 154 is selectively engageable to the ring gear 144 on the gearbox 160 set. The torque transmission mechanisms 150 . 152 and 154 are engageable in a similar manner as corresponding torque-transmitting mechanisms 50 . 52 respectively. 54 from 1 to set first and second forward electrically variable modes, a fixed forward speed ratio (corresponding to the third fixed forward speed ratio discussed with reference to FIG 1 has been described), an electric driving mode and an electrically adjustable backward mode with input branching produce.

Second alternative preferred embodiment

In 3 is a second specific preferred embodiment of a powertrain 210 with a gear 214 within the scope of the invention. The gear 214 uses three differential gear sets, preferably in the nature of planetary gear sets 220 . 230 and 240 , which are shown in lever diagram form. The planetary gear set 220 applies a ring gear 224 that's the sun gear 222 surrounds. A carrier 229 rotatably supports a plurality of planet gears, which mesh with both the ring gear 224 as well as the sun wheel 222 engage. The drive element 17 is on the carrier 229 attached. A first motor / generator 280 is constantly with the sun gear 222 connected.

The planetary gear set 230 has a ring gear 234 on, the sun wheel 232 surrounds. A carrier 239 includes several planet gears that mesh with both the sun gear 232 as well as the ring gear 234 engage. A second motor / generator 282 is constantly with the sun gear 232 connected.

The planetary gear set 240 includes a ring gear 244 that is a sun wheel 242 surrounds. A carrier 249 includes several planet gears that mesh with the sun gear 244 engage.

A connecting element 270 connects the ring gear 224 constantly with the sun wheel 232 , A connecting element 272 connects the carrier 239 constantly with the ring gear 244 , A connecting element 274 connects the ring gear 234 constantly with the carrier 249 ,

The ring gear 224 corresponds to the first node A of 1 , The carrier 229 corresponds to the second node B. The sun gear 222 corresponds to the third node C. The sun gear 232 corresponds to the fourth node D. The interconnected carriers 239 and ring gear 244 correspond to the fifth node E. The interconnected ring gear 234 and carriers 249 correspond to the sixth node F. The sun gear 242 corresponds to the seventh node G. Since the planetary gear sets 230 and 240 two connections with each other via connecting elements 272 and 274 they can pass through the single second lever 30 . 40 in 1 being represented. The planetary gear set 220 can through the lever 20 from 1 being represented.

A first torque transmitting mechanism 250 connects the carrier 229 selectively with the carrier 239 , A second torque transmitting mechanism 252 connects the ring gear 244 selectively with the gearbox 260 , A third torque transmitting mechanism 254 connects the sun wheel 242 selectively with the gearbox 260 , The torque transmission mechanisms 250 . 252 and 254 are engageable in a similar manner as corresponding torque-transmitting mechanisms 50 . 52 respectively. 54 as stated above by 1 to produce first and second forward electrically variable modes, forward electric mode, fixed forward speed ratio, and input split electrical reverse mode.

Third preferred alternative embodiment

In 4 is a third specific preferred embodiment of a powertrain 310 with a gear 314 within the scope of the invention. The gear 314 uses three differential gear sets, preferably in the nature of planetary gear sets 320 . 330 and 340 who are in Hebeldi are shown agrammform. The planetary gear set 320 applies a ring gear 324 that's the sun gear 322 surrounds. The carrier 329 rotatably supports a plurality of planet gears, which mesh with both the ring gear 324 as well as the sun wheel 322 engage. The drive element 17 is constantly with the carrier 329 connected. A first motor / generator 380 is constantly with the sun gear 322 connected.

The planetary gear set 330 has a ring gear 334 on, the sun wheel 332 surrounds. A carrier 339 includes multiple planet gears that mesh with both the ring gear 334 as well as the sun wheel 332 engage. A second motor / generator 382 is constantly with the sun gear 332 connected.

The planetary gear set 340 has a ring gear 344 on, the sun wheel 342 surrounds. A carrier 349 rotatably supports a plurality of planet gears, which mesh with both the ring gear 344 as well as the sun wheel 342 engage. The output element 19 is constantly with the carrier 349 connected.

A connecting element 370 connects the ring gear 324 constantly with the sun wheel 332 , A connecting element 372 connects the carrier 339 constantly with the ring gear 344 , A connecting element 374 connects the ring gear 334 constantly with the carrier 349 ,

Because the planetary gear sets 330 and 340 two pairs of over the fasteners 372 and 374 Having interconnected elements, they can by the single lever 30 . 40 from 1 being represented. The planetary gear set 320 can through the lever 20 from 1 being represented. The ring gear 324 corresponds to the first node A of 1 , The carrier 329 corresponds to the second node B. The sun gear 322 corresponds to the third node C. The sun gear 332 corresponds to the fourth node D. The interconnected carriers 339 and ring gear 344 correspond to the fifth node E. The interconnected ring gear 334 and carriers 349 correspond to the sixth node F. The sun gear 342 corresponds to the seventh node G.

A first torque transmitting mechanism 350 is selectively engageable to the wearer 329 with the carrier 339 connect to. A second torque transmitting mechanism 352 is selectively engageable to the ring gear 344 on the gearbox 360 set. A third torque transmitting mechanism 354 is selectively engageable to the sun gear 342 on the gearbox 360 set. A fourth torque-transmitting mechanism 356 is selectively engageable to the wearer 329 with the interconnected ring gear 324 and sun gear 332 connect to. A fifth torque-transmitting mechanism 358 is selectively engageable to the sun gear 332 and the second motor / generator 382 on the gearbox 360 set.

The torque transmission mechanisms 350 . 352 and 354 are engageable in a similar manner as corresponding torque-transmitting mechanisms 50 . 52 respectively. 54 from 1 to establish first and second forward electrically variable modes, a fixed forward speed ratio, an electrical forward mode, and an input-split electrically variable reverse mode. The additional torque transmission mechanisms 356 and 358 As described above, they are selectively engageable in a manner similar to corresponding torque-transmitting mechanisms 56 and 58 to produce three additional fixed forward speed ratios and one fixed reverse speed ratio. Although it is in the specific embodiments of the 2 to 8th not shown, a sixth torque-transmitting mechanism may be added to the first motor / generator 80 (Unit A) to the transmission housing and thus establish two additional fixed forward speed ratios for a sum of six fixed forward speed ratios as determined by the torque-transmitting mechanism 59 from 1 has been described.

Fourth alternative preferred embodiment

In 5 is a fourth specific preferred embodiment of a powertrain 410 with a gear 414 within the scope of the invention. The gear 414 uses three differential gear sets, preferably in the nature of planetary gear sets 420 . 430 and 440 , The gear 414 is shown in a schematic diagram instead of a lever diagram form. The planetary gear set 420 applies a ring gear 424 that's a sun gear 422 surrounds. A carrier 429 rotatably supports a plurality of planet gears, which mesh with both the ring gear 424 as well as the sun wheel 422 engage. The drive element 17 is constantly with the carrier 429 connected. A first motor / generator 480 is constantly with the sun gear 422 connected.

The planetary gear set 430 includes a ring gear 434 that is a sun wheel 432 surrounds. A carrier 439 includes multiple planet gears that mesh with both the ring gear 434 as well as the sun wheel 432 engage. The output element 19 is constantly with the ring gear 434 connected. As experts will understand, this is the transmission 414 suitable for a front-wheel drive application because the output member 19 is located at a location that is well suited for use in a lateral position.

The planetary gear set 440 includes a hollow wheel 444 that is a sun wheel 442 surrounds. The carrier 449 includes multiple planet gears that mesh with both the ring gear 444 as well as the sun wheel 442 engage. The second motor / generator 482 is constantly with the sun gear 422 connected.

A connecting element 470 connects the ring gear 424 constantly with the sun wheel 442 , The second motor / generator 482 is thus constantly with the ring gear 424 connected. The connecting element 470 may be a component or separate components. A connecting element 472 connects the ring gear 434 constantly with the carrier 449 , A connecting element 474 connects the sun wheel 432 constantly with the sun wheel 442 , Thus, two elements of the planetary gear set 430 constantly with the two elements of the planetary gear set 440 over two connecting elements 472 and 474 connected. Accordingly, the planetary gear sets 430 and 440 in the through the compound lever 30 . 40 from 1 lever diagram formed. The planetary gear set 420 can through the lever 20 from 1 being represented.

The ring gear 424 corresponds to the first node A of 1 , The carrier 429 corresponds to the second node B of 1 , The sun wheel 422 corresponds to the third node C of 1 , The constantly connected sun gears 432 and 442 correspond to the fourth node D of 1 , The carrier 439 corresponds to the fifth node E of 1 , The constantly connected ring gear 434 and carriers 449 correspond to the sixth node F of 1 , The ring gear 444 corresponds to the seventh node G of 1 ,

The first torque-transmitting mechanism 450 is selectively engageable to the wearer 429 with the carrier 439 to connect and also the drive element 17 with the carrier 439 connect to. The second torque transmitting mechanism 452 is selectively engageable to the wearer 439 on the gearbox 460 set. The third torque-transmitting mechanism 454 is selectively engageable to the ring gear 444 on the gearbox 460 set. The torque transmission mechanisms 450 . 452 and 454 are engageable in a similar way as corresponding torque-transmitting mechanisms 50 . 52 respectively. 54 from 1 to establish first and second forward electrically variable modes, forward electrical mode, fixed forward speed ratio, and input split electrical reverse mode.

[0078] Each of the planetary gear sets 420 . 430 and 440 preferably has a ring gear / sun gear tooth ratio (NR / SR) of 1.954, although other tooth ratios may be employed within the scope of the invention. When the optional fourth, fifth and sixth torque-transmitting mechanisms are applied, as shown in FIG 1 is indicated (ie, a fourth torque-transmitting mechanism, such as torque-transmitting mechanism 56 from 1 , connects the ring gear 424 selectively with the carrier 429 ; a fifth torque-transmitting mechanism, such as torque-transmitting mechanism 58 from 1 , sets the second motor / generator 482 selectively on the transmission housing 460 firmly; and a sixth torque transmitting mechanism, such as a torque transmitting mechanism 59 from 1 , puts the first motor / generator 480 selectively on the transmission housing 460 fixed), six fixed forward speed ratios and a fixed reverse speed ratio are achieved as follows. A first fixed forward gear ratio of 2.954 is achieved by engagement of the third and fourth torque-transmitting mechanisms 454 . 56 reached. A second fixed forward gear ratio of 1.954 is achieved by engagement of the third and sixth torque-transmitting mechanisms 454 . 59 reached. A third fixed forward gear ratio of 1.661 is achieved by engagement of the third and first torque-transmitting mechanisms 454 . 50 reached. A fourth fixed forward gear ratio of 1.355 is achieved by engagement of the first and sixth torque-transmitting mechanisms 450 . 59 reached.

A fifth fixed forward gear ratio of 1.0 is obtained by engagement of the first and fourth torque-transmitting mechanisms 450 . 56 reached. A sixth fixed forward gear ratio of 0.661 is obtained by engagement of the first and fifth torque-transmitting mechanisms 450 . 58 reached. Finally, a fixed reverse gear ratio of -1.954 is obtained by engagement of the second and fourth torque transmitting mechanisms 452 . 56 reached.

Out 5 The above description will clearly show that the transmission 414 selectively power from the machine 12 receives. The hybrid transmission 414 also receives power from an electrical power source 486 that with a controller or an ECU 488 connected or transfers power to them. The electric power source 486 is with the motor / generator 480 . 482 over the controller 488 connected. The electric power source 486 can be one or more batteries. Other electrical power sources, such as fuel cells, have the ability to provide or store and deliver electrical power, and may be used in lieu of batteries without altering the concepts of the present invention.

Fifth alternative preferred embodiment

In 6 is a fifth specific preferred embodiment of a powertrain 510 a gearbox 514 within the scope of the invention. The gear 514 uses three differential gear sets, preferably in the nature of planetary gear sets 520 . 530 and 540 , The gear 514 is illustrated in schematic form rather than in lever diagram form. The planetary gear set 520 applies a ring gear 524 that's the sun gear 522 surrounds. A carrier 529 rotatably supports a first set of planetary gears 527 and a second set of planet wheels 528 , The first set of planet wheels 527 is combing with the sun gear 522 and the second set of planet gears 528 engaged. The second set of planet wheels 528 is combing with the first set of planetary gears 527 and with the ring gear 524 engaged. The drive element 17 is constantly with the ring gear 524 connected. A first motor / generator 580 is constantly with the sun gear 522 connected.

The second planetary gear set 530 has a ring gear 534 on, the sun wheel 532 surrounds. A carrier 539 rotatably supports a plurality of planet gears that mesh with both the sun gear 532 as well as the ring gear 534 engage. The output element 19 is constantly on the ring gear 534 attached. As experts will understand, this is the transmission 514 suitable for an application with front-wheel drive, since the output element 19 located at a location that is well suited for use in a transverse position.

The planetary gear set 540 includes a ring gear 544 that is a sun wheel 542 surrounds. A carrier 549 includes several planet gears that mesh with both the sun gear 542 as well as the ring gear 544 engage. The second motor / generator 582 is constantly with the sun gear 542 connected.

A first connection element 570 connects the carrier 529 constantly with the sun wheel 542 , The connecting element 570 may be one component or separate components and also connects the second motor / generator 582 constantly with the carrier 529 , A second connecting element 572 connects the ring gear 534 constantly with the carrier 549 , A connecting element 574 connects the sun wheel 532 constantly with the sun wheel 542 ,

The carrier 529 corresponds to the first node A of 1 , The ring gear 524 corresponds to the second node B. The sun gear 522 corresponds to the third node C. The interconnected sun gears 532 and 542 correspond to the fourth node D. The carrier 539 corresponds to the fifth node E. The interconnected ring gear 534 and carriers 549 correspond to the sixth node F. The ring gear 544 corresponds to the seventh node G. Since the planetary gear sets 530 and 540 two pairs of over the fasteners 572 and 574 Having interconnected elements, they can through the second lever 30 . 40 from 1 being represented. The planetary gear set 520 gets through the first lever 20 from 1 shown.

The torque transmission mechanism 550 is selectively engageable to the ring gear 524 with the carrier 539 connect to. The carrier 539 is thus also constantly with the drive element 17 connected. The second torque transmitting mechanism 552 is selectively engageable to the wearer 539 on the gearbox 560 set. The third torque-transmitting mechanism 554 is selectively engageable to the ring gear 544 on the gearbox 560 set. The torque transmission mechanisms 550 . 552 and 554 are engageable in a similar manner to corresponding torque-transmitting mechanisms 50 . 52 respectively. 54 from 1 to establish first and second forward electrically variable modes, a fixed forward speed ratio, an electrical forward mode, and an input split electrical reverse mode.

Out 6A and from the foregoing description it can be seen that the transmission 514 selectively power from the machine 12 receives. The hybrid transmission 514 also receives power from an electrical power source 586 that with a controller or ECE 588 connected is.

The electric power source 586 can be one or more batteries. Other electrical power sources, such as fuel cells, may also be used. The battery 586 and the controller 588 are with the first and second motor / generator 580 . 582 connected to the motor / generators 580 . 582 Supply power or receive power from it.

Sixth alternative preferred embodiment

In 7 is a sixth specific preferred embodiment of a powertrain 610 with a gear 614 within the scope of the invention. The gear 614 uses three differential gear sets, preferably in the nature of planetary gear sets 620 . 630 and 640 , The planetary gear set 620 applies a ring gear 624 that's a sun gear 622 surrounds. A carrier 629 includes multiple planet gears that mesh with both the ring gear 624 as well as the sun wheel 622 engage. The drive element 17 is constantly with the carrier 629 connected, and a first motor / generator 680 is constantly with the sun gear 622 verbun the.

The planetary gear set 630 has a ring gear 634 on, the sun wheel 632 surrounds. A carrier 639 includes multiple planet gears that mesh with both the ring gear 634 as well as the sun wheel 632 engage. A second motor / generator 682 is constantly with the sun gear 632 connected.

The planetary gear set 640 also has a ring gear 644 on, that is a sun wheel 642 surrounds. A carrier 649 includes multiple planet gears that mesh with both the ring gear 644 as well as the sun wheel 642 engage. The output element 19 is constantly with the carrier 649 connected.

A connecting element 670 connects the ring gear 624 constantly with the second motor / generator 682 , whereby the ring gear 624 constantly with the sun wheel 632 is connected because the sun gear 632 also constantly with the second motor / generator 682 connected is. A second connecting element 672 connects the ring gear 634 constantly with the carrier 649 , A third connecting element 674 connects the carrier 639 constantly with the ring gear 644 ,

Although the transmission 614 in 7 Shown in schematic form, those skilled in the art will recognize that the planetary gear set 620 through the lever 20 from 1 can be represented. The ring gear 624 corresponds to the first node A of 1 , The carrier 629 corresponds to the second node B, and the sun gear 622 corresponds to the third node C. Since the planetary gear sets 630 and 640 two pairs of over the fasteners 672 and 674 Having interconnected elements, they can through the composite lever 30 . 40 from 1 being represented. The sun wheel 632 corresponds to the fourth node D. The interconnected carriers 639 and ring gear 644 correspond to the fifth node E. The interconnected ring gear 634 and carriers 649 correspond to the sixth node F. The sun gear 642 corresponds to the seventh node G.

The first torque-transmitting mechanism 650 connects the carrier 629 selectively with the carrier 639 , The second torque transmitting mechanism 652 puts the carrier 639 and the connected ring gear 644 selectively on the transmission housing 660 firmly. The torque transmission mechanism 654 puts the sun gear 642 selectively on the gearbox begehäuse 660 firmly. The fourth torque-transmitting mechanism 656 connects the carrier 629 selectively with the first motor / generator 680 and thereby with the sun wheel 622 that constantly with the first motor / generator 680 connected is. The fifth torque-transmitting mechanism 658 puts the sun gear 632 selectively on the transmission housing 660 fixed, which also makes the second motor / generator 682 and the ring gear 624 be determined.

The torque transmission mechanisms 650 . 652 . 654 . 656 and 658 are engageable in a similar manner as corresponding torque-transmitting mechanisms 50 . 52 . 54 . 56 respectively. 58 from 1 to establish first and second forward electrically-variable modes, four forward-forward speed ratios, a forward-drive electric mode, an input-reverse electrically-variable reverse mode, and a fixed reverse-speed ratio.

Each of the planetary gear sets 620 and 640 preferably has a ring gear / sun gear tooth ratio (NR / SR) of 1.954, and the planetary gear set 630 preferably has a ring gear / sun gear tooth ratio (NR / SR) of 2.333, although other tooth ratios may be used within the scope of the invention. When the optional fourth, fifth and sixth torque-transmitting mechanisms are applied, as shown in FIG 1 is indicated (ie, a fourth torque-transmitting mechanism, such as torque-transmitting mechanism 56 from 1 , connects the ring gear 624 selectively with the carrier 629 ; a fifth torque-transmitting mechanism, such as torque-transmitting mechanism 58 from 1 , connects the second motor / generator 682 selectively with the gearbox 660 ; and a sixth torque transmitting mechanism, such as a torque transmitting mechanism 59 from 1 , connects the first motor / generator 680 selectively with the gearbox 660 ), six fixed forward speed ratios and a fixed reverse speed ratio are achieved as follows. A first fixed forward gear ratio of 2.71 is achieved by engagement of the third and fourth torque-transmitting mechanisms 654 . 56 reached. A second fixed forward ratio of 1.79 is achieved by engagement of the third and sixth torque-transmitting mechanisms 654 . 59 reached. A third fixed forward speed ratio of 1.51 is achieved by engagement of the third and first torque-transmitting mechanisms 654 . 50 reached. A fourth fixed forward gear ratio of 1.28 is achieved by engagement of the first and sixth torque-transmitting mechanisms 650 . 59 reached. A fifth fixed forward gear ratio of 1.0 is obtained by engagement of the first and fourth torque-transmitting mechanisms 650 . 56 reached. A sixth fixed forward speed ratio of 0.70 is achieved by engagement of the first and fifth torque-transmitting mechanisms 650 . 58 reached. Finally, a fixed backward gear ratio of -2.33 is established by engagement of the second and fourth torque transmissions transmitting mechanism 652 . 56 reached.

Out 7 and from the foregoing description it can be seen that the transmission 614 selectively power from the machine 12 receives. The hybrid transmission 614 also receives power from an electrical power source 686 that with a controller or an ECU 688 connected is 688 , The electric power source 686 may be one or more batteries or may be fuel cells or other electrical power sources that have the ability to provide or store and deliver electrical power without altering the concepts of the present invention. The battery 686 and the controller 688 are with the first and second motor / generator 680 and 682 connected to power on the motors / generators 680 . 682 to transmit or receive from this service. The arrangement of the gearbox 614 from 7 is suitable for rear-wheel drive application and longitudinal installation.

Seventh preferred alternative embodiment

In 8th is a seventh specific preferred embodiment of a powertrain 710 with a gear 714 within the scope of the present invention. The gear 714 uses three differential gear sets, preferably in the nature of planetary gear sets 720 . 730 and 740 , The planetary gear set 720 applies a ring gear 724 that's the sun gear 722 surrounds. A carrier 729 includes a first and a second set of planetary gears 727 respectively. 728 , The first set of planet wheels 727 is combing with the sun gear 722 and with the second set of planet wheels 728 engaged. The second set of planet wheels 728 is combing with the first set of planetary gears 727 and the ring gear 724 engaged. The drive element 17 is constantly with the ring gear 724 connected. The first motor / generator 780 is constantly with the sun gear 722 connected.

The planetary gear set 730 has a ring gear 734 on, the sun wheel 732 surrounds. A carrier 739 includes multiple planet gears that mesh with both the ring gear 734 as well as the sun wheel 732 engage. The second motor / generator 782 is constantly with the sun gear 732 connected.

The planetary gear set 740 has a ring gear 744 on, the sun wheel 742 surrounds. A carrier 749 includes multiple planet gears that mesh with both the ring gear 744 as well as the sun wheel 742 to get in touch. The output element 19 is constantly with the carrier 749 connected.

A connecting element 770 connects the carrier 729 constantly with the second motor / generator 782 and therefore with the sun wheel 732 that also constantly with the second motor / generator 782 connected is. A carrier 772 connects the ring gear 734 constantly with the carrier 749 and thereby with the output element 19 , A connecting element 774 connects the carrier 739 constantly with the ring gear 744 ,

Although the transmission 714 from 8th In schematic form, those skilled in the art will readily recognize that the planetary gear set 720 through the first lever 20 from 1 is shown and the compound planetary gear sets 730 and 740 through the second lever diagram 30 . 40 from 1 are shown. The carrier 729 corresponds to the first node A of 1 , The ring gear 724 corresponds to the second node B. The sun gear 722 corresponds to the third node C. The sun gear 732 corresponds to the fourth node D. The interconnected carriers 739 and ring gear 744 correspond to the fifth node E. The interconnected ring gear 734 and carriers 749 correspond to the sixth node F. The sun gear 742 corresponds to the seventh node G.

A first torque transmitting mechanism 750 connects the ring gear 724 selectively with the carrier 739 , A second torque transmitting mechanism 752 puts the carrier 739 and the ring gear 744 selectively on the transmission housing 760 firmly. A third torque transmitting mechanism 754 puts the sun gear 742 selectively on the transmission housing 760 firmly. A fourth torque-transmitting mechanism 756 connects the ring gear 724 selectively with the carrier 729 and with the second motor / generator 782 and thereby with the sun wheel 732 that constantly with the second motor / generator 782 connected is. A fifth torque-transmitting mechanism 758 connects the sun wheel 732 selectively with the gearbox 760 which also makes the second motor / generator 782 and the carrier 729 are fixed. The torque transmission mechanisms 750 . 752 . 754 . 756 and 758 are engageable in a similar manner as corresponding torque-transmitting mechanisms 50 . 52 . 54 . 56 respectively. 58 from 1 to establish first and second forward electrically-variable modes, four forward-forward speed ratios, a forward-drive electric mode, an input-reverse electrically-variable reverse mode, and a fixed reverse-speed ratio. If the gearbox 714 from 8th a sixth torque-transmitting mechanism would be added to the first motor / generator 780 on the gearbox 760 determine two additional fixed forward speed ratios for a sum of six fixed forward speed ratios.

Out 8th and from the foregoing description it can be seen that the transmission 714 selectively Power from the machine 12 receives. The hybrid transmission 714 also receives power from an electrical power source 786 that with a controller or an ECU 788 connected is. The electric power source 786 may be one or more batteries or may be fuel cells or other electrical power sources that have the ability to provide or store and deliver electrical power without altering the concepts of the present invention. The battery 786 and the controller 788 are with the first and second motor / generator 780 and 782 connected to power to the motors / generators 780 . 782 to transmit or receive from this service. The arrangement of the gearbox 714 from 8th is suitable for rear-wheel drive application and longitudinal installation.

Although the best ways to carry out the Invention in detail those skilled in the art to which this invention pertains, various alternative constructions and practical embodiments execution of the invention within the scope of the appended claims.

Claims (20)

Electrically adjustable transmission, comprising: one Drive element for receiving power from a machine; one Output element; a first and second motor / generator; one first, second and third planetary gear sets, each having a first, second and third element, wherein the drive and driven element respectively constantly connected to a different element of the elements; one first connecting element, which is an element of the first planetary gear set constantly with an element of the second or third planetary gear set, which constantly with the second motor / generator is connected, connects; a second one and a third connecting element, each one different Element of the elements of the second planetary gear set with a different Connect element of the elements of the third planetary gear set; one first torque transmitting mechanism, which serves as an element of the first planetary gear set, which constantly with is connected to the drive element, selectively with an element of the second planetary gear set, which selectively with a fixed Element over a second torque transmitting mechanism connectable to connect; a third torque-transmitting mechanism, serving to, an element of the second or third planetary gear, the not connected to any of the other planetary gear sets, selectively to connect with the fixed element; the first one Motor / generator constantly with an element of the first planetary gear that does not match the Drive element or connected to the other planetary gear sets is, is connected; and wherein the torque-transmitting mechanisms are engageable, an electrically variable reverse mode with input branching and an electric forward drive mode provide. Electrically variable transmission according to claim 1, in which the second torque transmitting mechanism selectively engageable is to the electrically adjustable backward mode with input branching provide; wherein the first and second torque-transmitting mechanisms selectively engageable are to the electric forward drive mode provide; and wherein the first and third torque-transmitting mechanisms selectively engageable are to provide a first fixed forward speed ratio. Electrically variable transmission according to claim 2, wherein torque of the first motor / generator to torque of second motor / generator in the electric forward drive mode added becomes. Electrically variable transmission according to claim 1, further comprising: a fourth torque transmitting mechanism, the to serve any of the elements of the first planetary gear set selectively with any other element of the elements of the first Connect planetary gear set; the second and fourth Torque transmitting mechanisms engageable are to provide a fixed reverse speed ratio; in which the first torque-transmitting mechanism and the fourth torque transmitting mechanism engageable are to provide a second fixed forward speed ratio; and wherein the third torque transmitting mechanism and the fourth torque-transmitting mechanism selectively engageable are to provide a third fixed forward speed ratio. Electrically variable transmission according to claim 1, further comprising: a fifth Torque-transmitting mechanism, which serves to selectively connect the second motor / generator with the fixed one Element to connect; wherein the first torque-transmitting mechanism and the fifth Torque-transmitting mechanism selectively engageable are to provide another fixed forward speed ratio. Electrically variable transmission according to claim 1, further comprising: a sixth torque transmitting mechanism, the this is done by selectively connecting the first motor / generator with the stationary one Element to connect; wherein the first torque transmission mechanism and the sixth torque transmitting mechanism selectively engageable are to provide a different fixed forward speed ratio; wherein the third torque transmitting mechanism and the sixth torque transmitting mechanism selectively engageable are to provide a different forward different forward speed ratio; and wherein the second torque transmitting mechanism and the sixth torque transmitting mechanism selectively engageable are to provide a fixed reverse speed ratio. Electrically variable transmission according to claim 1, wherein the third torque transmitting mechanism selectively engageable is a first input electrically-variable forward mode and wherein the first torque-transmitting mechanism selectively engageable to provide a second composite electrically-forward mode. Electrically variable transmission according to claim 7, further comprising: an energy storage device that serves to supply power to the first and second motor / generator, or to receive from this power; a controller to do that serves, the power transmission between the energy storage device and the first and second To control motor / generator; and whereby the controller causes that at least one of the first and second motor / generator as a generator works to during of braking to convert rotational energy of the output element into power, which is stored in the energy storage device. Electrically variable transmission according to claim 1, the output element is constantly with an element of the second or third planetary gear set, the not all the time is connected to an element of the first planetary gear set and not selectively connectable to the fixed element is. Electrically adjustable transmission according to claim 1, wherein the first, second and third planetary gear sets a ring gear, a planet carrier and a sun gear; being the first motor / generator constantly is connected to the sun gear of the first planetary gear set; and in which the second connecting element the ring gear of the second planetary gear set constantly with the carrier connects the third planetary gear set. Electrically adjustable transmission according to claim 10, wherein the third connecting element, the carrier of the second planetary gear set constantly connects to the ring gear of the third planetary gear set. Electrically adjustable transmission according to claim 10, wherein the first connecting element, the ring gear of the first planetary gear set constantly connects to the sun gear of the second planetary gear set. Electrically adjustable transmission according to claim 1, wherein the first connecting element, the element of the first planetary gear set constantly connects to the second motor / generator; wherein the first connecting element thereby the element of the first planetary gear set with the element connects the second or third planetary gear set. An electrically variable transmission comprising: a drive element for receiving power from a machine; an output element; a first and second motor / generator; a first, second and third planetary gear set, each having a ring gear, a carrier and a sun gear, wherein the input and output elements are each permanently connected to a different element of the elements; a first connecting member continuously connecting the ring gear or the carrier of the first planetary gear set to the sun gear of the second planetary gear set, the sun gear of the second planetary gear set also being continuously connected to the second motor / generator; a second and a third connecting element, each connecting a different element of the elements of the second planetary gear set with a different element of the elements of the third planetary gear set, wherein one of the second and third connecting element connects the ring gear of the second planetary gear set constantly with the carrier of the third planetary gear set ; a first torque transmitting mechanism operable to selectively connect the member of the first planetary gear set continuously connected to the input member to a member of the second planetary gear set selectively connectable to a stationary member via a second torque transmitting mechanism; and a third torque transmitting mechanism serving to connect an element of the second or third third planetary gear set, which is not constantly constantly connected to any of the other planetary gear sets, selectively connect to the fixed member; wherein the first motor / generator is continuously connected to a member of the first planetary gear set which is not connected to the drive member or to the other planetary gear sets; and wherein the torque-transmitting mechanisms are engageable alone or in pairs to provide an input-split electrically variable reverse mode, a forward forward speed ratio, an electrical forward drive mode, an input first-range electrically-variable forward mode, and an interconnect-mode, electrically variable forward second mode. Electrically adjustable transmission according to claim 14, further comprising: a fourth torque transmitting mechanism, serving for any of the elements of the first planetary gear set selectively with any other element of the elements of the first Connect planetary gear set; the second and fourth Torque transmitting mechanisms engageable are to provide a fixed reverse speed ratio; in which the first torque-transmitting mechanism and the fourth torque transmitting mechanism engageable are to provide a second fixed forward speed ratio; and wherein the third torque transmitting mechanism and the fourth torque-transmitting mechanism selectively engageable are to provide a third fixed forward speed ratio. Electrically adjustable transmission according to claim 14, further comprising: at least a fifth torque-transmitting mechanism and a sixth torque transmitting mechanism; in which the fifth Torque-transmitting mechanism this serves to selectively connect the second motor / generator to the fixed one Element to connect, and with the first torque-transmitting mechanism engageable is to provide another fixed forward speed ratio; in which the sixth torque transmitting mechanism this is done by selectively connecting the first motor / generator with the stationary one Element to connect, and with the first torque-transmitting mechanism engageable is to provide a different fixed forward speed ratio; in which the third torque transmitting mechanism and the sixth torque transmitting mechanism selectively engageable are to provide a different forward different forward speed ratio; and wherein the second torque transmitting mechanism and the sixth Drehmomentübertragungsmechanis mechanism are selectively engageable, to provide a fixed reverse speed ratio. Electrically adjustable transmission, comprising: one first planetary gear set, which is a first, second and third element and represented by a first lever of a lever diagram is having a first, second and third node, the correspond to first, second and third elements; a second and a third planetary gear set, each a first, a second and a third element, wherein two of the elements of the second planetary gear set constantly are connected to two elements of the third planetary gear set, wherein the interconnected second and third planetary gear sets a second lever of the lever diagram can be displayed, the one fourth, fifth, sixth and seventh nodes that are the elements of the second and third Planetary gear set correspond, the first node constantly with connected to the fourth node; a drive element that constantly connected to the second node; a first motor / generator, the constantly is connected to the third node, and a second motor / generator, the constantly is connected to the fourth node; a first torque-transmitting mechanism, which serves to selectively connect the first node to the fifth node connect to; a second torque transmitting mechanism, the to serve the fifth Selectively connect nodes to the fixed element; one Output element that is constantly connected to the sixth node; and a third torque-transmitting mechanism, which serves to selectively connect the seventh node to the fixed one Element to connect; the torque-transmitting mechanisms alone or in pairs engageable are to an electrically adjustable backward mode with input branching and an electric forward drive mode provide. The electrically variable transmission of claim 17, further comprising: a fourth torque transmitting mechanism operable to selectively connect any one of the first, second and third nodes to any of the first, second and third nodes; wherein the second and fourth torque-transmitting mechanisms are selectively engageable to provide a fixed reverse speed ratio; wherein the first torque transmitting mechanism and the fourth torque transmitting mechanism are selectively engageable to a fixed one To provide forward speed ratio; and wherein the third torque transmitting mechanism and the fourth torque transmitting mechanism are selectively engageable to provide a different fixed forward speed ratio. Electrically adjustable transmission according to claim 17, further comprising: a fifth torque-transmitting mechanism, which serves to selectively connect the second motor / generator with the fixed one Element to connect; wherein the first torque-transmitting mechanism and the fifth Torque-transmitting mechanism selectively engageable are to provide a fixed forward speed ratio. Electrically adjustable transmission according to claim 17, further comprising: a sixth torque transmitting mechanism, which serves to selectively connect the first motor / generator with the fixed one Element to connect; wherein the first torque-transmitting mechanism and the sixth torque transmitting mechanism selectively engageable are to provide a fixed forward speed ratio; wherein the third torque transmitting mechanism and the sixth torque transmitting mechanism selectively engageable are to provide another fixed forward speed ratio; and wherein the second torque transmitting mechanism and the sixth torque transmitting mechanism selectively engageable are to provide a fixed reverse speed ratio.