CN109322976B

CN109322976B - Multi-mode power system

Info

Publication number: CN109322976B
Application number: CN201810693384.8A
Authority: CN
Inventors: K·K·麦坎齐; R·M·宾德尔
Original assignee: Deere and Co
Current assignee: Deere and Co
Priority date: 2017-07-31
Filing date: 2018-06-29
Publication date: 2023-05-02
Anticipated expiration: 2038-06-29
Also published as: DE102018212712A1; CN109322976A; BR102018013302A2

Abstract

The present disclosure relates to multi-mode power systems. A powertrain system for multi-mode power transfer and associated vehicle are described. A first continuously variable power source ("CVP") may convert rotational power received by the engine for transmission to a second CVP. The variator assembly may receive rotational power from the second CVP at a first input and rotational power directly from the engine at a second input. The control assembly may allow the powertrain to switch between modes such as a series mode, a split path mode, and a direct mode. The control component can provide seamless switching between at least two of these modes.

Description

Multi-mode power system

Technical Field

The present disclosure relates to power systems, including power systems that operate work vehicles for agricultural, forestry, construction, and other applications.

Background

In various settings, it may be useful to provide useful power using both a conventional engine (e.g., an internal combustion engine) and one or more continuously variable power sources (e.g., electric motor/generators or hydraulic motors/pumps, etc.). For example, a portion of the engine power may be diverted to drive a first continuously variable power source ("CVP") (e.g., a first electric motor/generator that acts as a generator, a first hydrostatic or hydrodynamic motor/pump that acts as a pump, etc.), which in turn may drive a second CVP (e.g., a second electric motor/generator that acts as a motor and uses electrical power from the first electric motor/generator, a second hydrostatic or hydrodynamic motor/pump that acts as a motor and uses hydraulic power from the first hydrostatic or hydrodynamic motor/pump, etc.).

In some applications, power from two types of power sources (i.e., an engine and a CVP) may be combined to transfer useful power (e.g., to drive an axle) via an infinitely variable transmission ("IVT") or a continuously variable transmission ("CVT"). This may be referred to as a "split mode" or "split path mode" because the power transfer may split between a direct mechanical path from the engine and an infinitely/continuously variable path through one or more CVPs. In contrast, in other applications, useful power may be provided by the CVP rather than by the engine (except to some extent, where the engine drives the CVP). This may be referred to as "CVP only mode". Finally, in other applications, useful power may be provided by the engine (e.g., via various mechanical transmission elements, such as shafts and gears) rather than by the CVP. This may be referred to as a "mechanical path mode". It will be appreciated that torque converters and various similar devices may sometimes be used in the mechanical path mode. In view of this, the mechanical path mode may be simply considered a power transmission mode in which the engine, rather than the CVP, provides useful power to a particular power sink.

Disclosure of Invention

A work vehicle is disclosed that includes an engine and a continuously variable power source (CVP). The work vehicle further includes a variator operably connected to the engine and the CVP. The work vehicle further includes an output shaft operatively connected to the variator. Further, the work vehicle includes a control assembly having a plurality of transmission members configured to provide selection between a first mode, a second mode, and a third mode. In the first mode, the control assembly is configured to transfer CVP power from the CVP to the output shaft and prevent engine power from being transferred from the engine to the output shaft. In the second mode, the control assembly is configured to transfer engine power from the engine to the variator, to transfer CVP power from the CVP to the variator, and to transfer a combination of engine power and CVP power from the variator to the output shaft. Further, in the third mode, the control assembly is configured to transfer engine power from the engine to the output shaft and prevent transmission of CVP power from the CVP to the output shaft. In addition, the control assembly is configured to provide at least one seamless switch between two of the first mode, the second mode, and the third mode.

In addition, a work vehicle is disclosed that includes an engine, a continuously variable power source (CVP), and a variator operatively connected to the engine and the CVP. The work vehicle also includes an output shaft operatively connected to the variator. The work vehicle further includes a control assembly including a plurality of transmission members configured to provide selection between a first mode and a second mode. The control assembly is configured to provide at least one seamless switch between the first mode and the second mode. In the second mode, the control assembly is configured to transfer engine power from the engine to the variator, to transfer CVP power from the CVP to the variator, and to transfer a combination of engine power and CVP power from the variator to the output shaft. In the first mode, the CVP is configured to supply a first CVP power and rotatably drive a first variator member of the variator's planetary gear set. In the first mode, the CVP is configured to supply a second CVP power to and rotatably drive a second variator member of the planetary gear set. In the first mode, the third variator member of the planetary gearset is configured to output the recombined CVP power to rotatably drive the output shaft.

The details of one or more implementations are set forth in the accompanying drawings and the description below. Other features and advantages will be apparent from the description and drawings, and from the claims.

Drawings

FIG. 1 is a side view of an example vehicle that may include a multi-mode transmission according to the present disclosure;

FIG. 2 is a schematic illustration of an example powertrain of the example vehicle of FIG. 1;

FIG. 3 is a schematic illustration of another example powertrain of the example vehicle of FIG. 1;

FIG. 4 is a schematic illustration of yet another example powertrain of the example vehicle of FIG. 1;

FIG. 5 is a schematic illustration of yet another example powertrain of the example vehicle of FIG. 1;

FIG. 6 is a schematic illustration of another example powertrain of the example vehicle of FIG. 1;

FIG. 7 is a schematic illustration of another example powertrain of the example vehicle of FIG. 1;

FIG. 8 is a schematic illustration of another example powertrain of the example vehicle of FIG. 1; and

FIG. 9 is a schematic illustration of another example powertrain of the example vehicle of FIG. 1.

Like reference symbols in the various drawings indicate like elements.

Detailed Description

One or more example embodiments of the disclosed powertrain (or vehicle) are described below, as shown in the figures briefly described above. Various modifications to the example embodiments may be envisaged by those skilled in the art.

For convenience of notation, particularly in the context of planetary gear sets, "component" may be used herein to refer to an element for transmitting power, such as a sun gear, ring gear, or planet carrier. Furthermore, references to a "continuously" variable transmission, powertrain, or power source will be understood to also encompass configurations that include "infinitely" variable transmissions, powertrain, or power sources in various embodiments.

In the following discussion, various example configurations of shafts, gears, and other power transmitting elements are described. It will be appreciated that various alternative configurations are possible within the spirit of the present disclosure. For example, various configurations may utilize multiple shafts instead of a single shaft (or a single shaft instead of multiple shafts), may interpose one or more idler gears between the various shafts or gears for transmitting rotational power, etc.

As used herein, "directly" or "directly" may be used to refer to the transfer of power between two system elements without converting the power intervention into another form. For example, if power is transmitted via multiple shafts, clutches, and gears (e.g., various spur gears, helical gears, combined, or other gears) rather than being converted to a different form by the CVP (e.g., rather than being converted to electrical or hydraulic power by a generator or hydraulic pump), power may be considered to be transmitted "directly" by the engine to the output member. In some configurations, the fluidic transfer of rotational force by the torque converter may also be considered "direct".

Conversely, if some portion of the power is converted to another form during transmission, the power may not be considered to be transmitted "directly" between the two system elements. For example, if a portion of the engine power is converted to a different form by a CVP, even if that portion is later reconverted to rotational power (e.g., by another CVP) and then recombined with unconverted engine power (e.g., via a merged planetary gear or other merging component), the power may not be considered to be transmitted "directly" between the engine and the output member.

In addition, as used herein, "between" may refer to a particular order or sequence of power transmitting elements, rather than to the physical orientation or placement of the elements. For example, if power is sent to the output member via a clutch device, the clutch device may be considered to be "between" the engine and the output member, whether the engine and the output member are located on physically opposite sides of the clutch device.

In using continuously (or infinitely) variable power systems, the relative efficiency of power transmission in various modes may be of some concern. For example, it will be appreciated that energy loss may exist in each of the following steps: converting rotational power from the engine to electrical or hydraulic power using the first CVP; transmitting the converted power to a second CVP; and then converts the transmitted power into a rotational force. In view of this, mechanical transmissions directly from the engine (i.e., in a mechanical path transmission mode) may be considered a relatively efficient mode of power transmission, while power transmission through the CVP (e.g., in a split path transmission mode or a CVP-only transmission mode) may be less efficient. Thus, in some situations, it may be desirable to utilize a mechanical path transmission mode instead of a split path mode or a CVP only mode. However, in other cases, the flexibility and other advantages provided by using CVP may be more than the inherent energy loss of the split path or CVP-only mode.

Among other advantages, the powertrain disclosed herein may usefully facilitate transitions between a split path mode, a mechanical path mode, and a CVP-only mode of a vehicle or other power platform. For example, by appropriate placement and control of the various gear sets, shafts, and clutches, the disclosed powertrain may allow the vehicle to easily transition between any of the three modes, depending on the needs of a particular operation.

In certain embodiments of contemplated powertrain systems, the engine may provide power to both the first input member of the variator (e.g., the carrier of the combined planetary gear set) and the input interface of the first CVP (e.g., the spline connection for the rotating shaft) via various mechanical (or other) power transmitting elements (e.g., various shafts and gears, etc.). The first CVP (e.g., an electrical or hydraulic machine) may convert power into a different form (e.g., electrical or hydraulic power) for transmission to the second CVP (e.g., another electrical or hydraulic machine) to allow the second CVP to provide rotational power to a second input of the variator (e.g., a sun gear of a compound planetary gear set).

A control assembly may be provided having at least a first clutch device and a second clutch device in communication with one or more output members (e.g., an input shaft to a power-shift transmission). The clutch device may be generally oriented between the output member (and various power sinks of the vehicle, such as wheels, differentials, power take-off shafts, etc.) and one or more of the engine and the CVP. In some embodiments, the first and second clutch devices may be mounted to a single shaft (or a set of coaxial shafts) that may rotate in parallel with the various inputs of the variator (e.g., the various inputs of the planetary gear set), the output shaft of the engine and the CVP, etc. In some embodiments, the first clutch and the second clutch may be mounted to different shafts, each of which may rotate parallel to the input of the variator.

The first clutch device of the control assembly may receive rotational power directly from the engine. For example, the first clutch device may engage a gear that communicates with an output shaft of the engine (e.g., the same output shaft that drives the first input member of the variator) through one or more gear connections. In this way, the first clutch device may provide a controllable power transmission path for direct power transmission from the engine to the output of the control assembly.

The second clutch device of the control assembly may receive rotational power from an output member of the variator (e.g., a ring gear of a planetary gear set). For example, the second clutch device may engage a gear in communication with the output member of the variator through one or more gear connections. In this way, the second clutch device may provide a controllable power transmission path for power transmission from both the engine and the second CVP via the variator to the output of the control assembly.

With the configuration generally described above (and others), engaging the first clutch device and disengaging the second clutch device may place the powertrain in a mechanical path mode, resulting in power flowing directly from the engine, through the first clutch device and the control assembly, and to the output of the control assembly. In some embodiments, such an output may be, or may be engaged with, an input of an additional powertrain component (e.g., an input of a power shift or other transmission). Similarly, engaging the second clutch device and disengaging the first clutch device may place the powertrain in a split path mode, with power from the engine and the second CVP (powered by the engine via the first CVP) being combined by the variator before flowing through the second clutch device and the control assembly to the control assembly output.

In some embodiments, a third clutch device may also be included in the control assembly, between an output member of the control assembly and one or more of the engine and the CVP. In some embodiments, the third clutch device may be mounted to the same shaft (or set of coaxial shafts) as the first clutch device and the second clutch device. In some embodiments, the third clutch device may be mounted to a different shaft (e.g., a different parallel shaft) than one or both of the first clutch device and the second clutch device.

The third clutch device may receive rotational power directly from the second CVP. For example, the third clutch device may engage a gear that communicates with an output shaft of the second CVP (e.g., the same output shaft that drives the second input member of the variator) through one or more gear connections. As such, engaging the third clutch device and disengaging the first and second clutch devices may place the powertrain in a CVP-only mode, with power flowing directly from the second CVP through the third clutch device and the control assembly to an output (e.g., an input of a power shift or other transmission). In such a configuration, the third clutch device may then be disengaged to perform the mechanical path mode and the split path mode described above.

As will become apparent from the discussion herein, the disclosed power system may be advantageously used in a variety of settings as well as for use with a variety of machines. For example, referring now to FIG. 1, an example of the disclosed powertrain may be included in a vehicle 10. In fig. 1, vehicle 10 is depicted as a tractor with a powertrain 12. However, it will be appreciated that other configurations are possible, including configurations with the vehicle 10 as a different type of tractor, harvester, log collector, grader, or one of a variety of other work vehicle types. It will be further appreciated that the disclosed power system may also be used in non-work vehicles and non-vehicle applications (e.g., fixed position power plants).

With additional reference to fig. 2, an example configuration of power system 12 is depicted as power system 12a. Power system 12a may include an engine 20 (which may be an internal combustion engine of various known configurations). Power system 12a may also include a CVP 30 (e.g., a generator or hydraulic pump) and a CVP 34 (e.g., an electric or hydraulic motor, respectively) that may be connected by a conduit 32 (e.g., an electric or hydraulic conduit, respectively).

The engine 20 may provide rotational power to an output shaft 22 for transmission to various power sinks (e.g., wheels, power take-off ("PTO") shafts, etc.) of the vehicle 10. In certain embodiments, a torque converter or other device may be included between engine 20 and shaft 22 (or another shaft (not shown)), but such a device is not necessary for operation of power system 12a, as contemplated by the present disclosure. Further, in certain embodiments, multiple shafts (not shown), including various shafts interconnected by various gears or other power transmission devices or equivalent power transmission devices (e.g., chains, belts, etc.), may be used in place of shaft 22 (or various other shafts discussed herein).

Engine 20 may also provide rotational power to CVP 30. For example, the engine output shaft 22 may be configured to provide rotational power to a gear 24 or another power transmission component (not shown) to transfer power from the engine 20 to a gear 26 on a parallel shaft. Further, gear 26 may provide rotational power (via parallel axes) to CVP 30.

Continuing, CVP 30 may convert the received power into an alternative form (e.g., electrical or hydraulic power) for transmission on conduit 32. The converted and transmitted power may be received by the CVP 34 and then reconverted by the CVP 34 to provide (e.g., along the output shaft 36) a rotational power output. Various known control devices (not shown) may be provided to regulate such conversion, transmission, re-conversion, etc.

Both the engine 20 and the CVP 34 may provide rotational power to the variator 40 via shafts 22 and 36 (or various similar components), respectively. In general, variator 40 can include various devices capable of combining mechanical inputs from

shafts

22 and 36 to obtain a combined mechanical output (which may be useful, for example, for split path power transmission). In certain embodiments, as depicted in FIG. 2, the variator 40 can be configured as a merged planetary gear set. As depicted, shaft 22 may provide power to planet carrier 44, shaft 36 may provide power to sun gear 42, and planet gears 46 may transmit power from both planet carrier 44 and sun gear 42 to ring gear 48. This may be a useful configuration because the CVP 34 may operate more efficiently at higher rotational speeds than the engine 20, which may be supplemented by a deceleration from the sun gear 42 to the planet carrier 44. However, it will be appreciated that other configurations are possible, with the engine 20 providing rotational power to any one of the sun gear 42, the planet carrier 44, and the ring gear 48, and the CVP 34 providing rotational power to the other one of the sun gear 42, the planet carrier 44, and the ring gear 48, and the remaining one of the sun gear 42, the planet carrier 44, and the ring gear 48, respectively.

To control transitions between various transmission modes, the control assembly 56 may be configured to receive power in one or more of the following ways: receiving power directly from the engine 20; receiving power from engine 20 and CVP 34 via variator 40; and directly receives power from the CVP 34 and transmits the received power to various downstream components. In powertrain 12a, for example, control assembly 56 may include a single output shaft (or a set of coaxial output shafts) 58 or various other output components that may communicate with various power sinks or other downstream components (not shown) of vehicle 10, such as various wheels, one or more differentials, power switches or other transmissions, etc. Shaft 58 may also be in communication with (e.g., engageable with)

clutch devices

62 and 64, and

clutch devices

62 and 64 may be variously configured as wet clutches, dry clutches, shoulder clutches, or other similar devices mounted to shaft 58.

The clutch device 62 may be in communication with a gear 68, and the gear 68 may be meshed (directly or indirectly) with the gear 24 on the engine output shaft 22. Accordingly, when clutch device 62 is engaged, a power transmission path may be provided from engine 20 to shaft 58 via

gears

24 and 68 and clutch device 62. (as depicted, gear 24 may transmit power from shaft 22 to both CVP 30 and gear 68. However, it will be appreciated that a separate gear (not shown) may transmit power from engine 20 to

gears

26 and 68, respectively, separately.

Similarly, the clutch device 64 may be in communication with a gear 70, and the gear 70 may be engaged (directly or indirectly) with the ring gear 48 (or another output member) of the variator 40. Accordingly, when the clutch device 64 is engaged, a power transmission path may be provided from the variator 40 to the shaft 58 via the gear 70 and the clutch device 64.

In this manner, engagement of, for example, clutch device 62 and disengagement of clutch device 64 may place powertrain 12a in a mechanical path mode in which rotational power is transmitted directly from engine 20 to shaft 58 via clutch device 62. Further, engagement of clutch device 64 and disengagement of clutch device 62 may place powertrain 12a in a split path mode, wherein power from both engine 20 and CVP 34 is combined in variator 40 before being transmitted to shaft 58 via clutch device 64.

With additional reference to FIG. 3, another example power system 12b is depicted. Power system 12b may include an engine 120, and engine 120 may be an internal combustion engine having various known configurations. Power system 12b may also include a CVP 130 (e.g., a generator or hydraulic pump) and a CVP 134 (e.g., an electric or hydraulic motor, respectively) that may be connected by a conduit 132 (e.g., an electric or hydraulic conduit, respectively).

The engine 120 may provide rotational power to an output shaft 122 for transmission to various power sinks (e.g., wheels, PTO shafts, etc.) of the vehicle 10. In certain embodiments, a torque converter or other device may be included between engine 120 and shaft 122 (or another shaft (not shown)), but such a device is not necessary for operation of power system 12b, as contemplated by the present disclosure. Further, in certain embodiments, multiple shafts (not shown), including various shafts interconnected by various gears or other power transmission devices or equivalent power transmission devices (e.g., chains, belts, etc.), may be used in place of shaft 122 (or various other shafts discussed herein).

Shaft 122 may be configured to provide rotational power to gear 124 or another power transmission component (not shown) to transfer power from engine 120 to gear 126. In turn, gear 126 may provide rotational power to CVP 130 for conversion to an alternative form (e.g., electrical or hydraulic power) for transmission over conduit 132. The converted and transmitted power may then be reconverted by the CVP 134 for mechanical output along the output shaft 136. Various known control devices (not shown) may be provided to regulate such conversion, transmission, re-conversion, etc. In certain embodiments, shaft 136 may be in communication with spur gear 138 (or other similar component).

Both the engine 120 and the CVP 134 may provide rotational power to the variator 140 via

shafts

122 and 136, respectively. In general, variator 140 can include various devices capable of combining mechanical inputs from

shafts

122 and 136 to obtain a combined mechanical output (which may be useful, for example, for split path power transmission). In certain embodiments, as depicted in FIG. 3, the variator 140 can be configured as a merged planetary gear set. As depicted, shaft 122 may provide power to planet carrier 144, shaft 136 may provide power to sun gear 142, and planet gears 146 may transmit power from both planet carrier 144 and sun gear 142 to ring gear 148. This may be a useful configuration because the CVP 134 may operate more efficiently at higher rotational speeds than the engine 120, which may be supplemented by a deceleration from the sun gear 142 to the planet carrier 144. However, it will be appreciated that other configurations are possible, with the engine 120 providing rotational power to any one of the sun gear 142, the planet carrier 144, and the ring gear 148, and the CVP 134 providing rotational power to the other of the sun gear 142, the planet carrier 144, and the ring gear 148, and the remaining one of the sun gear 142, the planet carrier 144, and the ring gear 148, respectively.

To control transitions between various transmission modes, the control assembly 156 may be configured to receive power in one or more of the following ways: receiving power directly from the engine 120; receiving power from engine 120 and CVP134 via variator 140; and directly receives power from the CVP134 and transmits the received power to various downstream components. In powertrain 12b, for example, control assembly 156 may include a single shaft (or a set of coaxial shafts) 158 that may be in communication with various power sinks or other downstream components (not shown) of vehicle 10, such as various wheels, one or more differentials, power switches or other transmissions, and the like. Shaft 158 may also be in communication (e.g., engageable) with

clutch devices

162 and 164, and

clutch devices

162 and 164 may be variously configured as wet clutches, dry clutches, shoulder clutches, or other similar devices mounted to shaft 158.

The clutch device 162 may be in communication with a gear 168, and the gear 168 may be meshed (directly or indirectly) with the gear 124 on the engine output shaft 122. Accordingly, when the clutch device 162 is engaged, a power transmission path may be provided from the engine 120 to the shaft 158 via the

gears

124 and 168 and the clutch device 162. ( As depicted, gear 124 may transmit power from shaft 122 to both CVP 130 and gear 168. However, it will be appreciated that separate gears (not shown) may separately transmit power from the engine 120 to the

gears

126 and 168, respectively. )

Similarly, the clutch device 164 may be in communication with a gear 170, and the gear 170 may be engaged (directly or indirectly) with the ring gear 148 (or another output member) of the variator 140. Accordingly, when the clutch device 164 is engaged, a power transmission path may be provided from the variator 140 to the shaft 158 via the gear 170 and the clutch device 164. Finally, the clutch device 166 may be in communication with a gear 170, and the gear 170 may be meshed (directly or indirectly) with a gear 138 on the output shaft 136 of the CVP 134. Accordingly, when clutch device 166 is engaged, a power transmission path may be provided from CVP 134 to shaft 158 via

gears

138 and 172 and clutch device 166.

In this manner, engagement of, for example, clutch device 162 and disengagement of

clutch devices

164 and 166 may place powertrain 12b in a mechanical path mode, wherein rotational power is transmitted directly from engine 120 to shaft 158 via clutch device 162. Further, engagement of the engagement clutch device 164 and disengagement of the

clutch devices

162 and 166 may place the powertrain 12b in a split path mode, wherein power from both the engine 120 and the CVP 134 is combined in the variator 140 prior to transmission to the shaft 158 via the clutch device 164. Finally, engagement of clutch device 166 and disengagement of

clutches

162 and 164 may place powertrain 12b in a CVP-only mode, wherein rotational power is transmitted directly from CVP 134 to shaft 158 via clutch device 166.

With additional reference to FIG. 4, another example power system 12c is depicted. Powertrain 12c may include an engine 220, and engine 220 may be an internal combustion engine having various known configurations. Power system 12c may also include a CVP 230 (e.g., a generator or hydraulic pump) and a CVP 234 (e.g., an electric or hydraulic motor, respectively) that may be connected by a conduit 232 (e.g., an electric or hydraulic conduit, respectively).

The engine 220 may provide rotational power to an output shaft 222 for transmission to various power sinks (e.g., wheels, PTO shafts, etc.) of the vehicle 10. In certain embodiments, a torque converter or other device may be included between engine 220 and shaft 222 (or another shaft (not shown)), but such a device is not necessary for operation of power system 12c, as contemplated by the present disclosure. Further, in certain embodiments, multiple shafts (not shown), including various shafts interconnected by various gears or other power transmission devices or equivalent power transmission devices (e.g., chains, belts, etc.), may be used in place of shaft 222 (or various other shafts discussed herein).

Shaft 222 may be configured to provide rotational power to gear 224 or another power transmission component (not shown) to transfer power from engine 220 to gear 226. In turn, gear 226 may provide rotational power to CVP 230 for conversion to an alternative form (e.g., electrical or hydraulic power) for transmission over conduit 232. The converted and transmitted power may then be reconverted by the CVP 234 for mechanical output along an output shaft 236. Various known control devices (not shown) may be provided to regulate such conversion, transmission, re-conversion, etc. In certain embodiments, the shaft 236 may be in communication with a spur gear 238 (or other similar component).

Both engine 220 and CVP 234 may provide rotational power to variator 240 via

shafts

222 and 236, respectively. In general, variator 240 can include various devices capable of combining mechanical inputs from

shafts

222 and 236 to obtain a combined mechanical output (which may be useful, for example, for split path power transmission). In certain embodiments, as depicted in FIG. 4, the variator 240 can be configured as a merged planetary gear set. As depicted, shaft 222 may provide power to planet carrier 244, shaft 236 may provide power to sun gear 242, and planet gears 246 may transmit power from both planet carrier 244 and sun gear 242 to ring gear 248. This may be a useful configuration because CVP 234 may operate more efficiently at higher rotational speeds than engine 220, which may be supplemented by a deceleration from sun gear 242 to planet carrier 244. However, it will be appreciated that other configurations are possible, with engine 220 providing rotational power to any one of sun gear 242, carrier 244, and ring gear 248, and CVP 234 providing rotational power to the other of sun gear 242, carrier 244, and ring gear 248, and the remaining one of sun gear 242, carrier 244, and ring gear 248, respectively.

To control transitions between various transmission modes, the control assembly 256 may be configured to receive power in one or more of the following ways: receiving power directly from engine 220; receiving power from engine 220 and CVP 234 via variator 240; and directly receives power from the CVP 234 and transmits the received power to various downstream components. In powertrain 12c, for example, control assembly 256 may include a single shaft (or a set of coaxial shafts) 258 and a shaft 260, which may each communicate with various power sinks or other downstream components (not shown) of vehicle 10, such as various wheels, one or more differentials, power switches or other transmissions, and the like. The shaft 258 may also be in communication with (e.g., engageable with)

clutch devices

262 and 266, and the

clutch devices

262 and 266 may be variously configured as wet clutches, dry clutches, shoulder clutches, or other similar devices mounted to the shaft 258. Similarly, the shaft 260 may be in communication with (e.g., engageable with) a clutch device 264, which clutch device 264 may also be configured as a wet clutch, a dry clutch, a shoulder clutch, or other similar device mounted to the shaft 260. It will be appreciated that other configurations are possible, including the following: with different combinations of

clutch devices

262, 264, and 266 engaged with

shafts

258 and 260, or with additional shafts (not shown) for engaging one or more of

clutch devices

262, 264, and 266.

The clutch device 262 may be in communication with a gear 268, and the gear 268 may be meshed (directly or indirectly) with a gear 224 on the engine output shaft 222. Accordingly, when the clutch device 262 is engaged, a power transmission path may be provided from the engine 220 to the shaft 258, via the

gears

224 and 268 and the clutch device 262. ( As depicted, gear 224 may transmit power from shaft 222 to both CVP 230 and gear 268. However, it will be appreciated that separate gears (not shown) may separately transfer power from engine 220 to

gears

226 and 268, respectively. )

Similarly, the clutch device 264 may be in communication with a gear 270, and the gear 270 may be engaged (directly or indirectly) with the ring gear 248 (or another output member) of the variator 240. Accordingly, when the clutch device 264 is engaged, a power transmission path may be provided from the variator 240 to the shaft 258 via the gear 270 and the clutch device 264. Finally, the clutch device 266 may be in communication with a gear 270, and the gear 270 may be meshed (directly or indirectly) with a gear 238 on the output shaft 236 of the CVP 234. Accordingly, when the clutch device 266 is engaged, a power transmission path may be provided from the CVP 234 to the shaft 258 via the

gears

238 and 272 and the clutch device 266.

In this manner, engagement of, for example, the engagement of clutch device 262 and disengagement of

clutch devices

264 and 266 may place powertrain 12c in a mechanical path mode, wherein rotational power is transmitted directly from engine 220 to shaft 258 via clutch device 262. Further, engagement of the engagement clutch device 264 and disengagement of the

clutch devices

262 and 266 may place the powertrain 12c in a split path mode, wherein power from both the engine 220 and the CVP 234 is combined in the variator 240 prior to transmission to the shaft 258 via the clutch device 264. Finally, engagement of clutch device 266 and engagement of

disconnect clutches

262 and 264 may place powertrain 12c in a CVP-only mode, wherein rotational power is transmitted directly from CVP 234 to shaft 258 via clutch device 266.

Various other configurations are possible. For example, in certain embodiments (including embodiments similar to the examples described above), the first CVP may be provided in series with the engine and the variator. With additional reference to fig. 5, for example, the power system 12d may be substantially similar to the power system 12c of fig. 4. However, in powertrain 12d, CVP 230a may be disposed between engine 220 and variator 240 such that engine 220 provides power to CVP 230a and variator 240 in series.

As noted above, in certain embodiments, multiple parallel (or other) axes (including parallel and non-coaxial axes) may be utilized for the various functions of the disclosed power system. For example, as depicted in fig. 4, the various

clutch devices

262, 264, and 266 of the control assembly 256 may be disposed on a plurality of parallel and

non-coaxial shafts

258 and 260. The rotational power transmitted to the

shafts

258 and 260, respectively, may be used for different functions or may be recombined in various known ways (e.g., through another consolidated planetary gear set). Other configurations are possible, including configurations with different numbers or arrangements of various shafts.

Referring now to FIG. 6, another example powertrain 12e is depicted. Power system 12e may include an engine 320, and engine 320 may be an internal combustion engine having various known configurations. Power system 12e may also include a CVP 330 (e.g., a generator or hydraulic pump) and a CVP 334 (e.g., an electric or hydraulic motor, respectively) that may be connected by a conduit 332 (e.g., an electric or hydraulic conduit, respectively).

The engine 320 may provide rotational power to an output shaft 322 for transmission to various power sinks (e.g., wheels, PTO shafts, etc.) of the vehicle 10. In certain embodiments, a torque converter or other device may be included between engine 320 and shaft 322 (or another shaft (not shown)), but such a device is not necessary for operation of power system 12e, as contemplated by the present disclosure. Further, in certain embodiments, multiple shafts (not shown), including various shafts interconnected by various gears or other power transmission devices or equivalent power transmission devices (e.g., chains, belts, etc.), may be used in place of shaft 322 (or various other shafts discussed herein).

Shaft 322 may be configured to provide rotational power to gear 324 or another power transmission component (not shown) to transfer power from engine 320 to gear 326. Further, gear 326 may provide rotational power to a gear 327 mounted to a common shaft 329. Gear 327 may be meshed with gear 370, gear 370 being mounted on parallel shaft 371. Gear 327 may also mesh with gear 331 on another parallel shaft 333. Shaft 333 may provide rotational power to CVP 330. The CVP 330 converts power into an alternative form (e.g., electrical or hydraulic power) for transmission on the conduit 332. The converted and transmitted power may then be reconverted by the CVP 334 for mechanical output along the output shaft 336. Various known control devices (not shown) may be provided to regulate such conversion, transmission, re-conversion, etc.

In certain embodiments, the shaft 336 may be in communication with a gear 338 (or other similar component). The gear 338 may transmit power to a gear 339 mounted on a shaft 341, which shaft 341 may be parallel to the shaft 336. The shaft 341 may provide rotational power to the variator 340. The engine 320 may also provide rotational power to the variator 340 along another path, which will be discussed in detail below.

In general, variator 340 can include various devices capable of combining mechanical inputs from CVP 334 and engine 320 to obtain a combined mechanical output (which may be useful, for example, for split path power transmission). In certain embodiments, as depicted in fig. 6, the variator 340 can be configured as a combined planetary gear set (e.g., a single planetary gear set).

As depicted, shaft 341 may provide power to sun gear 342 of variator 340. Variator 340 can also include a ring gear 348. As will be discussed, engine 320 may selectively provide power to ring gear 348. Variator 340 can further include a plurality of planetary gears 346 and an associated carrier 344. The planetary gears 346 may combine power from the sun gear 342 and the ring gear 348, and the carrier 344 may transfer the combined power to the attached gears 349. The gear 349 may be mounted on the output shaft 351 and may transmit power to the output shaft 351. The output shaft 351 may transfer power to an output component 353, such as a range bin, an axle, a power take-off (PTO) shaft, or other component.

Thus, variator 340 can receive power from CVP 334 (i.e., CVP power) and power from engine 320 (i.e., engine power). The variator 340 can transmit the combination (i.e., the sum) of the powers to the output component 353. This may be a useful configuration because the CVP 334 may operate more efficiently at higher rotational speeds than the engine 320, which may be supplemented by a reduction in speed from the sun gear 342 to the planet carrier 347. However, it will be appreciated that other configurations are possible, with engine 320 providing rotational power to any one of sun gear 342, carrier 347 and ring gear 348; the CVP 334 supplies rotational power to the other of the sun gear 342, the carrier 344, and the ring gear 348 and the remaining one of the sun gear 342, the carrier 344, and the ring gear 348, respectively, to output power to the output member 353.

To control transitions between various transmission modes, the control assembly 356 may be configured to receive power in one or more of the following ways: 1) Receiving power directly from engine 320; 2) Receiving power from both engine 320 and CVP 334 via variator 340; and 3) receives power directly from the CVP 334. The control assembly 356 may also be configured to transmit the received power to the output member 353. In power system 12e, for example, control assembly 356 may include one or more selectable transmission components. The selectable transmission components may each have a first position (e.g., an engaged position) in which the components transmit power from the input member to the output member. The selectable transmission component may also have a corresponding second position (e.g., a disengaged position) in which the device prevents power from being transferred from the input component to the output component. The selectable transmission components may include one or more wet clutches, dry clutches, shoulder clutches, brakes, synchronizers, or other similar devices. The device may also include an actuator (e.g., a hydraulic actuator, an electric motor, etc.) for actuating the selectable transmission between the first and second positions. Further, the control assembly 356 may include a controller (e.g., a computer controller or a hydraulic controller) configured to control the actuators and ultimately the movement of the selectable transmission components.

As shown in fig. 6, the control assembly 356 may include a first clutch 360, a second clutch 362, and a brake 364. Each of these selectable transmission components is discussed in detail below. As will be discussed, the control assembly 356 may include various features that provide for efficient selective power transfer. Additionally, control assembly 356 may include features that make power system 12e more compact, reduce the number of overall components, increase manufacturability, etc.

The first clutch 360 may include one or more first members 361 (e.g., clutch/friction plates, etc.) mounted on a shaft 329. The first clutch 360 may also include one or more corresponding second components 363 attached to the shaft 359. Gear 365 is mounted on shaft 359. Thus, when the first clutch 360 is in the first (engaged) position, power may be transferred from the shaft 329 to the gear 365. Conversely, when in the second (disengaged) position, the first clutch 360 may prevent such power transmission.

In some embodiments, the first clutch 360 may be configured to selectively transfer power from the engine 320 to the variator 340. More specifically, as described above, shaft 329 may receive power from engine 320 (via shaft 322, gear 324, and gear 326). Gear 365 may be meshed with gear 367 mounted for rotation on shaft 341. Gear 367 may be connected (via a transmission member 357) to ring gear 348 of variator 340.

The second clutch 362 may include one or more first members 369 (e.g., friction/clutch plates, etc.) mounted on a shaft 371. The second clutch 362 may also include one or more corresponding second members 373 mounted on a shaft 375. Thus, when the second clutch 362 is in the first (engaged) position, power may be transferred from the shaft 371 to the shaft 375. Conversely, when in the second (disengaged) position, the second clutch 362 may prevent such power transfer.

In some embodiments, the second clutch 362 may be configured to selectively transfer power from the engine 320 to the output member 353. The power transmission path bypasses the variator 340. More specifically, as described above, shaft 371 may receive power from engine 320 (via shaft 322, gear 324, gear 326, shaft 329, gear 327 and gear 370). In addition, the shaft 375 may include a gear 376 secured thereto. The gear 376 may be meshed with an idler gear 378, and the idler gear 378 is meshed with a gear 349. As described above, the gear 349 may be mounted on the output shaft 351 of the output member 353.

Brake 364 may be mounted to chassis 380 of vehicle 10. Brake 364 may be operatively coupled to ring gear 348 of variator 340. Accordingly, brake 364 may have a first (braking) position in which brake 364 secures ring gear 348 to the chassis of vehicle 10. Brake 364 may also have a second (unbraked) position in which brake 364 allows ring gear 348 to move relative to the chassis.

In some embodiments, engaging second clutch 362 and disengaging first clutch 360 and brake 364 may place powertrain 12e in a mechanical path mode (i.e., direct drive mode) in which rotational power is directly transferred from engine 320 to output member 353. Specifically, power from engine 320 is transferred from shaft 322 to gear 324, gear 326, shaft 329, gear 327, gear 370, through second clutch 362 to gear 376, gear 378, gear 349, shaft 351, and ultimately to output member 353. It should be noted that this transmission path from the engine 320 to the output member 353 bypasses the variator 340. In addition, in this mode, the transmission of the rotational power from the CVP 334 to the output member 353 is prevented.

Further, engaging first clutch 360 and disengaging second clutch 362 and brake 364 may place powertrain 12e in a split path mode, wherein power from both engine 320 and CVP 334 is combined in variator 240 prior to transmission to output member 353. Specifically, power from engine 320 is transferred from shaft 322 to gear 324, gear 326, shaft 329, through first clutch 360 to gear 365, gear 367 and ring gear 348 of variator 340. At the same time, power from the CVP 334 is transferred from the shaft 336 to the

gears

338, 339, 341, and the sun gear 342 of the variator 340. Planet gears 346 and associated carrier 344 may combine power from engine 320 and CVP 334 and output the combined power to gears 349, shaft 351, and ultimately to output member 353.

Moreover, engaging brake 364 and disengaging the engagement of first and

second clutches

360, 362 may place powertrain 12e in a CVP-only mode (i.e., a series mode). In this mode, rotational power may be transferred from engine 320 to CVP 330, powering CVP 334, and CVP 334 may output rotational power to output component 353. Specifically, power from engine 320 is transferred from shaft 322 to

gears

324, 326, 329, 327, 331, 333, providing power to CVP 330. The CVP 330 may convert the mechanical power into another form and supply power (via the conduit 332) to the CVP 334. CVP 334 may output mechanical power to shaft 336, gear 338, gear 339, shaft 341, sun gear 342, planetary gears 346, and carrier 344, gear 349, shaft 351, and ultimately to output member 353. It should be noted that in this mode, the transmission of the rotational power from the engine 320 to the output member 353 is prevented.

In some embodiments, vehicle 10 may be propelled in a forward direction with powertrain 12e in any of a direct drive mode, a split path mode, and a series mode. Additionally, in some embodiments, vehicle 10 may be propelled in an opposite reverse direction with powertrain 12e in a series mode, rather than in a direct drive mode and a split path mode.

Powertrain 12e may be switched between a direct drive mode, a split path mode, and a series mode to maintain efficient operation. It will be appreciated that power system 12e may be relatively compact and have a relatively low number of components. In particular, brake 364 provides simplicity to the layout of power system 12 e. Additionally, brake 364 reduces the number of components of powertrain 12e as compared to other selectively engageable transmission components.

Referring now to FIG. 7, another example powertrain 12f is depicted. Power system 12f may include an engine 420, and engine 420 may be an internal combustion engine having various known configurations. Power system 12f may also include a CVP 430 (e.g., a generator or hydraulic pump) and a CVP 434 (e.g., an electric or hydraulic motor, respectively) that may be connected by a conduit 432 (e.g., an electric or hydraulic conduit, respectively).

The engine 420 may provide rotational power to an output shaft 422 for transmission to various power sinks (e.g., wheels, PTO shafts, etc.) of the vehicle 10. In certain embodiments, a torque converter or other device may be included between engine 420 and shaft 422 (or another shaft (not shown)), but such a device is not necessary for operation of power system 12f, as contemplated by the present disclosure. Further, in certain embodiments, multiple shafts (not shown), including various shafts interconnected by various gears or other power transmission devices or equivalent power transmission devices (e.g., chains, belts, etc.), may be used in place of shaft 422 (or various other shafts discussed herein).

Shaft 422 may be configured to provide rotational power to gear 424 or another power transmission component (not shown) to transfer power from engine 420 to gear 426. Power from engine 420 may be transmitted to other components of power system 12f via gears 424 and/or gears 426, which will be discussed in detail below.

The CVP 430 converts power (e.g., power from the engine 420) into an alternative form (e.g., electrical or hydraulic power) that is transmitted on the conduit 432. The converted and transmitted power may then be reconverted by CVP 434 for mechanical output along output shaft 436. Various known control devices (not shown) may be provided to regulate such conversion, transmission, re-conversion, etc.

In certain embodiments, the output shaft 436 may be in communication with a gear 438 (or other similar component). The gear 438 may transmit power to the gear 439 mounted on the shaft 441. Axis 441 may be parallel to axis 436. Gear 442 may also be fixedly mounted on shaft 441. Gear 442 may be meshed with gear 443, gear 443 being fixedly mounted on shaft 444. The axis 444 may be parallel to the axis 441. Shaft 444 may provide rotational power to variator 440 (initially provided from CVP 434). The engine 420 may also provide rotational power to the variator 440 along another path, which will be discussed in detail below.

In general, variator 440 may comprise various devices capable of combining mechanical inputs from CVP 434 and engine 420 to obtain a combined mechanical output (which may be useful, for example, for split path power transfer). In certain embodiments, as depicted in FIG. 7, the variator 440 can be configured as a merged planetary gear set. In some embodiments, the variator 440 can comprise a double planetary gear set.

As depicted, shaft 444 may selectively provide power to first sun gear 445 and second sun gear 446 of variator 440. The variator 440 may also include a first ring gear 447 and a second ring gear 437. In addition, the variator 440 can include a first planetary gear 449 and a second planetary gear 450. The first planetary gear 449 may be disposed between the first gear ring 447 and the first sun gear 445 and meshed with the first gear ring 447 and the first sun gear 445. The second planetary gears 450 may be disposed between the second ring gear 437 and the second sun gear 446 and mesh with the second ring gear 437 and the second sun gear 446. Further, the first planet gears 449 may be interconnected with the first carrier 490. The second planetary gears 450 may be interconnected with a second carrier 454. The first ring gear 447 may be connected to the second planetary gears 450 via the second carrier 454. The second ring gear 437 can also be connected to the gear 448. The variator 440 can also include a third carrier 456, the third carrier 456 being attached to the second planetary gear 450. The third carrier 456 may be connected to a gear 458. Gear 458 may be meshed with gear 460, gear 460 being fixedly mounted to shaft 461. Gear 458 may also be meshed with gear 462, gear 462 being fixedly mounted to shaft 463.

Powertrain 12f may operate in a number of different transmission modes. To control the transition between the various modes, the control assembly 464 may be configured to receive power in one or more of the following ways: 1) Receiving power directly from engine 420; 2) Receiving power from both engine 420 and CVP 434 via variator 440; and 3) receives power directly from CVP 434. The control assembly 464 may also be configured to transfer the received power to a shaft 451 of the output component 453, such as a range box, an axle, a power take-off (PTO) shaft, or other component of the vehicle 10.

In powertrain 12f, for example, control assembly 464 may include one or more selectable transmission components. The selectable transmission component may have a first position (e.g., an engaged position) in which the device transmits power from the input component to the output component. The selectable transmission component may also have a second position (e.g., a disengaged position) in which the device prevents power from being transferred from the input component to the output component. The selectable transmission components of the control assembly 464 may include one or more wet clutches, dry clutches, shoulder clutches, brakes, synchronizers, or other similar devices. The device may further comprise an actuator for actuating the selectable transmission member between the first and second positions. Further, the control assembly 464 may include a controller (e.g., a computer controller or a hydraulic controller) configured to control the actuators and ultimately the movement of the selectable transmission components.

As shown in fig. 7, the control assembly 464 may include a first forward clutch 470, a second forward clutch 472, a reverse clutch 473, a brake 474, a first output clutch 476, and a second output clutch 478. As will be discussed, the control assembly 464 may include various features that provide efficient selective power transfer. Additionally, control assembly 464 may include features that make power system 12f more compact, reduce the number of overall components, and increase manufacturability, among other features.

The first forward clutch 470 in the engaged position may engage the gear 426 and the gear 488 such that the

gears

426, 488 rotate in unison. The first forward clutch 470 in the disengaged position may allow the gear 426 to rotate relative to the gear 488. Gear 488 can be meshed with gear 448.

The second forward clutch 472 may engage gear 426 and gear 489, alternatively, disengage gear 426 and gear 489. Gear 489 may be meshed with gear 452. The gear 452 may be connected to a first gear carrier 490 of the variator 440.

The reverse clutch 473 may engage the shaft 422 and the shaft 481 (support gear 480), alternatively, disengage the shaft 422 and the shaft 481. Gear 480 may be meshed with gear 448. Shaft 481 may also support gear 482. Further, gear 482 may be meshed with gear 483. Gear 483 may be fixedly mounted to common shaft 484 with gear 485. Gear 485 may be meshed with gear 486, gear 486 being fixedly mounted to output shaft 487 of CVP 430.

A brake 474 may be mounted to the chassis 491 of the vehicle 10. Brake 474 may be operably coupled to gear 452 (and thus, to first planetary gear 449 via first carrier 490). Thus, the brake 474 may have a first (braking) position in which the brake 474 secures the first planetary gear 449 to the chassis 491. The brake 474 may also have a second (unbraked) position in which the brake 474 allows the first planetary gear 449 to move relative to the chassis 491.

The first output clutch 476 may engage the gear 460 and the gear 492, alternatively, disengage the gear 460 and the gear 492. Gear 492 may be meshed with gear 493, gear 493 being fixedly mounted on shaft 451 for transmitting power to output member 453.

The second output clutch 478 may engage gear 462 and gear 494, alternatively, disengage gear 462 and gear 494. Gear 494 may be meshed with gear 496, gear 496 being fixedly mounted on shaft 451 to transmit power to output member 453.

Different transmission modes of power system 12f will now be discussed. As with the embodiments discussed above, power system 12f may have at least one mechanical path mode (i.e., direct drive mode), at least one split path mode, and at least one CVP-only mode (i.e., series mode).

In some embodiments, engaging the first forward clutch 470, the second forward clutch 472, and the first output clutch 476, and disengaging the brake 474, the second output clutch 478, and the reverse clutch 473 may place the powertrain 12f in a first mechanical path mode (i.e., a low range direct drive mode). In this mode, rotational power is directly transmitted from the engine 420 to the output member 453. In addition, in some embodiments, rotational power from CVP 434 is prevented from being transmitted to output member 453. Specifically, power from the engine 420 is transferred from the shaft 422 to the

gears

424, 426, and is branched off by the first forward clutch 470 and the second forward clutch 472. Power through the first forward clutch 470 is transferred to the gear 488, the gear 448, and the second ring gear 437. At the same time, power through the second forward clutch 472 is transferred to gear 489, gear 452, carrier 490, first ring gear 447. Engine power is recombined at the second planetary gear 450 and transferred to

gears

458, 460, through the first output clutch 476 to

gears

492, 493 and ultimately to the output member 453.

In some embodiments, engaging the first forward clutch 470, the second forward clutch 472, and the second output clutch 478, and disengaging the brake 474, the first output clutch 476, and the reverse clutch 473 may place the powertrain 12f in the second mechanical path mode (i.e., the high range direct drive mode). The power transfer may be substantially similar to the first direct drive mode described above, except that the power at the second planetary gear 450 may be transferred to

gears

458, 462, through the second output clutch 478 to

gears

494, 496, 493, and ultimately to the output member 453. In some embodiments, this mode may provide a higher output speed range for the vehicle 10 than the speed range provided by the first direct drive mode.

Further, engaging first forward clutch 470 and first output clutch 476 and disengaging engagement of second forward clutch 472, reverse clutch 473, second output clutch 478, and brake 474 may place powertrain 12f in a first split path mode, wherein power from both engine 420 and CVP 434 is combined in variator 440 before being transmitted to output member 453. Specifically, power from engine 420 is transferred from shaft 422 to gear 424, gear 426, gear 488, gear 448, second ring gear 437 of variator 440. The power at gear 448 may also be transmitted to

gears

480, 482, 483, 485, 486 to power CVP 430. CVP 430 can convert the mechanical input into electrical power to power CVP 434. Mechanical power from CVP 434 may be transferred from shaft 436 to gear 438, gear 439, gear 442, gear 443, shaft 444, and second sun gear 446 of variator 440. The second planetary gear 450 may combine power from the engine 420 and the CVP 434, and the carrier 456 may output the combined power to the

gears

458, 460, through the first output clutch 476 to the

gear

492, 493, shaft 451, and finally to the output member 453.

Engaging the first forward clutch 470 and the second output clutch 478 and disengaging the second forward clutch 472, the reverse clutch 473, the first output clutch 476 and the brake 474 may place the powertrain 12f in a second split path mode, wherein power from both the engine 420 and the CVP 434 is combined in the variator 440 before being transmitted to the output member 453. The power transfer may be substantially similar to the first split path mode described above, except that the combined power at gear 458 may be transferred to gear 462, to gear 494, to gear 496, to gear 493, and ultimately to output member 453, through second output clutch 478. In some embodiments, this mode may provide a higher output speed range for the vehicle 10 than the speed range provided by the first split path mode.

Additionally, in some embodiments, engaging the second forward clutch 472 and the first output clutch 476 and disengaging the first forward clutch 470, the reverse clutch 473, the second output clutch 478, and the brake 474 may place the powertrain 12f in a third split path mode, wherein power from both the engine 420 and the CVP 434 is combined in the variator 440 before being transmitted to the output member 453. Specifically, power from engine 420 is transferred from shaft 422 to gear 424, gear 426, gear 489, gear 452, first planetary gear 449 of variator 440. Meanwhile, power from CVP 434 may be transmitted from shaft 436 to gear 438, gear 439, gear 442, gear 443, shaft 444, and first sun gear 445 of variator 440. The first ring gear 447 may combine power from engine 420 and CVP 434, and carrier 454 may output the combined power to second planetary gear 450 and carrier 456, gear 458, gear 460, to gear 492, gear 493, shaft 451 through first output clutch 476, and ultimately to output member 453. In some embodiments, this mode may provide a higher output speed range for the vehicle 10 than the speed ranges provided by the first and second split path modes described above.

Engaging the second forward clutch 472 and the second output clutch 478 and disengaging the first forward clutch 470, the reverse clutch 473, the first output clutch 476 and the brake 474 may place the powertrain 12f in a fourth split path mode in which power from both the engine 420 and the CVP 434 is combined in the variator 440 before being transmitted to the output member 453. The power transfer may be substantially similar to the third split path mode described above, except that the combined power at gear 458 may be transferred to gear 462, to gear 494, to gear 496, to gear 493, and ultimately to output member 453, through second output clutch 478. In some embodiments, this mode may provide a higher output speed range for the vehicle 10 than the speed ranges provided by the first, second, and third split path modes.

Also, engaging brake 474 and first output clutch 476 and disengaging the engagement of first forward clutch 470, second forward clutch 472, reverse clutch 473, and second output clutch 478 may place powertrain 12f in a first CVP-only mode (i.e., a first series mode). In this mode, engine 420 may disconnect from variator 440 and CVP 430. The CVP 434 may output rotational power to the output member 453. Specifically, CVP 434 may output mechanical power to shaft 436, gear 438, gear 439, shaft 441, gear 442, gear 443, second sun gear 446, planetary gear 450, and carrier 456, gear 458, gear 460, through first output clutch 476 to gear 492, gear 493, shaft 451, and ultimately to output member 453.

In some embodiments, engaging brake 474 and second output clutch 478 and disengaging the engagement of first forward clutch 470, second forward clutch 472, reverse clutch 473, and first output clutch 476 may place powertrain 12f in a second CVP-only mode (i.e., a second series mode). The power transfer may be substantially similar to the first series mode described above, except that the power at gear 458 may be transferred to gear 462, through second output clutch 478 to gear 494, gear 496, gear 493, and ultimately to output member 453. In some embodiments, this mode may provide a higher output speed range for the vehicle 10 than the speed range provided by the first series mode.

Additionally, in some embodiments, engagement of the reverse clutch 473 and the first output clutch 476 and disengagement of the brake 474, the second output clutch 478, the first forward clutch 470, and the second forward clutch 472 may place the powertrain 12f in the first reverse split path mode. Power from both engine 420 and CVP 434 is combined in variator 440 before being transmitted to output member 453, and vehicle 10 is propelled in a reverse direction. Specifically, power from the engine 420 is transmitted from the shaft 422 to the gear 480, the gear 448, and the second ring gear 437 of the variator 440 through the reverse clutch 473. Power at gear 480 may also be transmitted to

gears

482, 483, 485, 486 to power CVP 430. The CVP 430 can convert the mechanical input into electrical power to power the CVP 434. Mechanical power from CVP 434 may be transferred from shaft 436 to gear 438, gear 439, gear 442, gear 443, shaft 444, and second sun gear 446 of variator 440. The second planetary gear 450 may combine power from the engine 420 and the CVP 434, and the carrier 456 may output the combined power to the

gears

458, 460, through the first output clutch 476 to the

gear

492, 493, shaft 451, and finally to the output member 453.

Further, in some embodiments, engagement of the reverse clutch 473 and the second output clutch 478 and disengagement of the brake 474, the first output clutch 476, the first forward clutch 470, and the second forward clutch 472 may place the powertrain 12f in the second reverse split path mode. The power transfer may be substantially similar to the first reverse split path mode described above, except that the power at gear 458 may be transferred to gear 462, through second output clutch 478 to gear 494, gear 496, gear 493, and ultimately to output member 453. In some embodiments, this mode may provide a higher output speed range for the vehicle 10 than the speed range provided by the first reverse split path mode.

Powertrain 12f may be switched between a direct drive mode, a split path mode, and a series mode to maintain efficient operation. It will be appreciated that power system 12f may be relatively compact and have a relatively low number of components. In particular, brake 474 provides simplicity to the layout of powertrain 12 f. In addition, brake 474 reduces the number of components compared to other selectively engageable transmission components.

Referring now to FIG. 8, another example powertrain 12g is depicted. Powertrain 12g may include an engine 520, and engine 520 may be an internal combustion engine having various known configurations. Power system 12g may also include a CVP 530 (e.g., an electrical or hydraulic motor) and a CVP 534 (e.g., an electrical or hydraulic motor) that may be connected by a conduit 532 (e.g., an electrical or hydraulic conduit).

The engine 520 may provide rotational power to an engine shaft 522. Shaft 522 may be configured to provide rotational power to gear 524. Gear 524 may be meshed with gear 525, and gear 525 may be supported on (e.g., fixed to) shaft 527. The shaft 527 may be substantially parallel to the engine shaft 522 and spaced from the engine shaft 522. As will be discussed in detail, shaft 527 may support various components of power system 12 g.

Gear 524 may also be meshed with gear 526, with gear 526 being supported on (e.g., fixed to) shaft 528. The shaft 528 may be substantially parallel to the engine shaft 522 and spaced apart from the engine shaft 522, and the shaft 528 may be connected to the CVP 530. Thus, mechanical power from the engine (i.e., engine power) may be transferred to the engaged gears 524, 526, shaft 528, and CVP 530 via the engine shaft 522. CVP 530 can convert this power into an alternative form (e.g., electrical or hydraulic power) that is transmitted to CVP 534 on conduit 532. The converted and transmitted power may then be reconverted by CVP 534 for mechanical output along shaft 536. Various known control devices (not shown) may be provided to regulate such conversion, transmission, re-conversion, etc. Additionally, in some embodiments, shaft 536 may support gear 538 (or other similar components). Gear 538 may mesh with gear 535 and may transfer power to gear 535. Gear 538 may also mesh with gear 537 and may transfer power to gear 537. Thus, power from the CVP 534 (i.e., CVP power) may be split between gear 535 and gear 537 for transmission to other components, which will be discussed in more detail below.

Power system 12g may further include a variator 540. In some embodiments, the variator 540 can include at least two planetary gear sets. In some embodiments, the planetary gear sets may be interconnected and supported on a common shaft (such as shaft 527), and the planetary gear sets may be substantially concentric. In other embodiments, different planetary gear sets may be supported on separate respective shafts that are not concentric. The arrangement of the planetary gear sets may be configured according to the space available within the vehicle 10 for packaging the powertrain 12 g.

As shown in the embodiment of fig. 8, the variator 540 can include a first planetary gear set 550 (i.e., a "low" planetary gear set) having a first sun gear 551, first planet gears and associated carrier 552, and first ring gear 553. Moreover, the variator 540 can include a second planetary gear set 554 (i.e., a "high" planetary gear set) having a second sun gear 555, a second planet gear, and associated carrier 557, and a second ring gear 558. Second planetary gears and carrier 557 may be directly attached to first ring gear 553. In addition, the second planetary gear and carrier 557 may be directly attached to shaft 562 having gear 565 fixed thereto. Also, the second ring gear 558 may be directly attached to the gear 566. As shown, shaft 562, gear 565, and gear 566 may each receive shaft 527 and may be substantially concentric with shaft 527. Although not specifically shown, it will be appreciated that power system 12g may include various bearings for concentrically supporting these components. Specifically, shaft 562 may be rotatably attached to shaft 527 via a bearing, and gear 566 may be rotatably attached to shaft 562 via another bearing.

On the opposite side of the variator 540 (left to right in fig. 8), a gear 537 may be mounted (e.g., fixed) on a shaft 560, the shaft 560 also supporting a first sun gear 551 and a second sun gear 555. In some embodiments, the shaft 560 may be hollow and may receive the shaft 527. Bearings (not shown) rotatably support shaft 560 on shaft 527 substantially concentrically.

Further, a first planetary gear and associated carrier 552 may be attached to gear 568. Gear 568 may be engaged with gear 570, gear 570 being fixed to shaft 572. Shaft 572 may be substantially parallel to shaft 527 and spaced from shaft 527.

Power system 12g may be configured to transfer power (from engine 520, CVP 530, and/or CVP 534) to output shaft 510 or other output components. The output shaft 510 may be configured to transmit the received power to wheels of the vehicle 10, a power take-off (PTO) shaft, a range bin, a tool, or other component of the vehicle 10.

Power system 12g may have a number of selectable modes, such as a direct drive mode, a split path mode, and a series mode. In the direct drive mode, power from engine 520 may be transmitted to output shaft 510 and power from CVP 534 may be prevented from being transmitted to output shaft 510. In split path mode, power from engine 520 and CVP 534 may be combined by variator 540 and the combined or combined power may be transferred to output shaft 510. Also, in the series mode, power from the CVP 534 may be transmitted to the output shaft 510 and power from the engine 520 may be prevented from being transmitted to the output shaft 510. Power system 12g may also have different speed modes in one or more of a direct drive mode, a split path mode, and a series mode, and these different speed modes may provide different angular speed ranges for output shaft 510. Powertrain 12g may be switched between modes to maintain proper operating efficiency. Further, powertrain 12g may have one or more forward modes for moving vehicle 10 in a forward direction, one or more reverse modes for moving vehicle 10 in a reverse direction.

Power system 12g may be switched between different modes, for example, using control assembly 564. The control assembly 564 may include one or more selectable transmission components. The selectable transmission component may have a first position (engaged position) in which the device transmits power from the input component to the output component. The selectable transmission component may also have a second position (a disengaged position) in which the device prevents transmission of power from the input component to the output component. The selectable transmission components of the control assembly 564 may include one or more wet clutches, dry clutches, shoulder clutches, brakes, synchronizers, or other similar devices. The control assembly 564 may also include an actuator for actuating the selectable transmission member between the first and second positions. Further, the control assembly 564 may include a controller (e.g., a computer controller or a hydraulic controller) configured to control the actuators, and consequently the movement of the selectively-transmitted components.

As shown in fig. 8, the control assembly 564 may include a first clutch 512, a second clutch 514, a third clutch 516, a fourth clutch 518, and a fifth clutch 519. Additionally, the control assembly 564 may include the forward clutch 513 and the reverse clutch 515.

In some embodiments, the first clutch 512 may be mounted and supported on the shaft 542. Additionally, the first clutch 512 in the engaged position may engage the gear 535 (rotating as a unit with the shaft 542). The first clutch 512 in the disengaged position may allow the gear 535 to rotate relative to the shaft 542. Additionally, gear 544 may be fixed to shaft 542, and gear 544 may mesh with gear 565 fixed to shaft 562.

The reverse clutch 515 may be supported on the shaft 542 (i.e., on the shaft 542 in conjunction with the first clutch 512). Reverse clutch 515 may engage gear 544 and gear 546, alternatively, disengage gear 544 and gear 546. Gear 546 may be meshed with idler gear 548, and idler gear 548 may be meshed with gear 549.

Forward clutch 513 can be supported on a shaft 562, which in turn is supported on a shaft 527. Thus, forward clutch 513 may be concentric with both shaft 562 and shaft 527.

The second clutch 514 may be supported on a shaft 572. The second clutch 514 may engage the shaft 572 and the gear 574, alternatively, disengage the shaft 572 and the gear 574.

Gear 574 may be in mesh with gear 576. Gear 576 may be secured to and mounted on a countershaft 578. The countershaft 578 may also support gear 580. Gear 580 may be meshed with gear 582, gear 582 being secured to output shaft 510.

The third clutch 516 may be supported on a shaft 584. Shaft 584 may be substantially parallel to shaft 572 and spaced a distance from shaft 572. In addition, a gear 586 may be fixed to the shaft 584 and supported by the shaft 584. As shown, gear 586 may be meshed with gear 566. Third clutch 516 may engage gear 586 and gear 588, alternatively disengage gear 586 and gear 588. Gear 588 may be meshed with gear 576.

The fourth clutch 518 may be supported (in concert with the second clutch 514) on a shaft 572. The fourth clutch 518 may engage the shaft 572 and the gear 590, alternatively, disengage the shaft 572 and the gear 590. Gear 590 may mesh with gear 592, gear 592 being mounted on and secured to countershaft 578.

In addition, a fifth clutch 519 may be supported (co-axially and concentrically with the third clutch 516) on the shaft 584. The fifth clutch 519 may engage the shaft 584 and the gear 594, alternatively, disengage the shaft 584 and the gear 594. Gear 594 may be meshed with gear 592.

Different modes of transmission of powertrain 12g will now be discussed. As with the previous embodiment, powertrain 12g may have at least one split path mode and at least one CVP-only mode (i.e., a series mode). Additionally, in some embodiments, power system 12g may additionally have a direct drive mode.

In some embodiments, engaging first clutch 512 and second clutch 514 may place powertrain 12g in the first forward mode. The mode may be a CVP only mode (i.e., a series mode). In this mode, mechanical power from the engine 520 may flow to the CVP 530 via the shaft 522, gear 524, gear 526, and shaft 528. CVP 530 may convert the input mechanical power to electrical or hydraulic power and supply the converted power to CVP 534. In addition, power from the engine 520 flowing to the shaft 527 via the shaft 522, the gear 524, and the gear 525 is prevented from being input into the variator 540. Moreover, mechanical power from CVP 534 may rotate shaft 536 and attached gear 538. The CVP power may cause gear 537 to rotate to cause first sun gear 551 to rotate. CVP power may also cause gear 535 to rotate, which may be transmitted across first clutch 512 to shaft 542, gear 544, gear 565, shaft 562, second planet gears and associated carrier 557, first ring gear 553. In other words, in this mode, power from the CVP 534 drivably rotates the two components of variator 540 (first sun 551 and first ring 553), and power may be combined and recombined at the first planet gears and associated carrier 552. The recombined power may be transferred to shaft 572 via gear 568 and gear 570. Power at shaft 572 can be transferred across second clutch 514 to

gears

574, 576, along shaft 578 to

gears

580, 582, and ultimately to output shaft 510. In some embodiments, the CVP-only or series mode may provide relatively high torque to the output shaft 510 at low angular velocity output. Thus, in some implementations, this mode may be referred to as a crawling mode. Further, as will become apparent, the first clutch 512 may be used only in this mode; accordingly, the first clutch 512 may be referred to as a "creep clutch".

It should be noted that this first (series) mode has no brake (i.e., no braking). In other words, the CVP 534 rotates the first sun 551 and the first ring gear 553, with the result that CVP power is recombined at the first planet gears and carrier 552. This may simplify the layout, design, and assembly of power system 12 g. Additionally, power system 12g may be more reliable and stronger, for example, because the rotating portion is more likely to remain cool than the braking components.

Moreover, in some embodiments, engaging forward clutch 513 and second clutch 514 may place powertrain 12g in the second forward mode. The mode may be a split path mode, in which variator 540 combines power from CVP 534 and engine 520 and outputs the combined power to output shaft 510. Specifically, power from CVP 534 is transmitted from shaft 536 to gear 538, gear 537, shaft 560 to drive first sun gear 551. In addition, power from engine 520 is transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, through forward clutch 513 to shaft 562, second planetary gear and associated carrier 557, first ring gear 553. The combined power from the CVP 534 and the engine 520 is combined at the first planetary gear and associated carrier 552 and transmitted to shaft 572 via gear 568 and gear 570. Power at shaft 572 can be transferred across second clutch 514 to

gears

574, 576, along shaft 578 to

gears

580, 582, and ultimately to output shaft 510.

Additionally, in some embodiments, engaging forward clutch 513 and third clutch 516 may place powertrain 12g in a third forward mode. The mode may be a split path mode. Specifically, power from the CVP 534 may be transmitted from the shaft 536 to the gear 538, the gear 537, the shaft 560 to drive the second sun gear 555. In addition, power from engine 520 is transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, through forward clutch 513 to shaft 562, the second planetary gears, and associated carrier 557. The combined power from the CVP 534 and the engine 520 may be combined at the second ring gear 558 and may be transmitted to the gear 566, the gear 586, through the third clutch 516 to the gear 588, the gear 576, the shaft 578, the gear 580, the gear 582, and ultimately to the output shaft 510.

Additionally, in some embodiments, engaging forward clutch 513 and fourth clutch 518 may place powertrain 12g in a fourth forward mode. The mode may be a split path mode. Specifically, power from CVP 534 is transmitted from shaft 536 to gear 538, gear 537, shaft 560 to drive first sun gear 551. In addition, power from engine 520 is transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, through forward clutch 513 to shaft 562, second planetary gear and associated carrier 557, first ring gear 553. The combined power from the CVP 534 and the engine 520 is combined at the first planetary gear and associated carrier 552 and transmitted to shaft 572 via gear 568 and gear 570. Power at shaft 572 can be transferred across the fourth clutch 518 to gear 590, gear 592, along shaft 578 to gear 580, gear 582, and ultimately to output shaft 510.

Moreover, in some embodiments, engaging forward clutch 513 and fifth clutch 519 may place powertrain 12g in a fifth forward mode. The mode may be a split path mode. Specifically, power from the CVP 534 may be transmitted from the shaft 536 to the gear 538, the gear 537, the shaft 560 to drive the second sun gear 555. In addition, power from engine 520 is transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, through forward clutch 513 to shaft 562, the second planetary gears, and associated carrier 557. The combined power from the CVP 534 and the engine 520 may be combined at the second ring gear 558 and may be transmitted to the gear 566, the gear 586, through the fifth clutch 519 to the gear 594, the gear 592, the shaft 578, the gear 580, the gear 582, and ultimately to the output shaft 510.

The powertrain 12g may also have one or more reverse modes that drive the vehicle 10 in a reverse direction (counter-current) to those modes described above. In some embodiments, power system 12g may provide a first reverse mode that corresponds to the first forward mode described above. Thus, this may be a series mode or a CVP only mode, and the first clutch 512 and the second clutch 514 may be engaged. It will be appreciated that the CVP 534 may drive the shaft 536 and other downstream components in a direction opposite to that described above to move the vehicle 10 in reverse.

Moreover, power system 12g may have multiple split-path reverse modes. In some embodiments, powertrain 12g may provide reverse modes corresponding to the second forward mode, third forward mode, fourth forward mode, and fifth forward mode described above; however, reverse clutch 515 may be engaged (instead of forward clutch 513) to achieve reverse mode.

Thus, powertrain 12g may provide a second reverse mode by engaging reverse clutch 515 and second clutch 514. As such, power from CVP 534 may be transmitted from shaft 536 to gear 538, gear 537, shaft 560 to drive first sun gear 551. In addition, power from engine 520 may be transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, idler gear 548, gear 546, through reverse clutch 515 to gear 544, gear 565, shaft 562, second planetary gears and associated carrier 557, first ring gear 553. The combined power from the CVP 534 and the engine 520 may be combined at the first planetary gear and the associated carrier 552 and may be transmitted to the shaft 572 via gear 568 and gear 570. Power at shaft 572 can be transferred across second clutch 514 to

gears

574, 576, along shaft 578 to

gears

580, 582, and ultimately to output shaft 510.

Powertrain 12g may also provide a third reverse mode by engaging reverse clutch 515 and third clutch 516. As such, power from CVP 534 may be transmitted from shaft 536 to gear 538, gear 537, shaft 560 to drive second sun gear 555. In addition, power from engine 520 may be transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, idler gear, gear 546, through reverse clutch 515 to gear 544, gear 565, shaft 562, second planetary gear, and associated carrier 557. The combined power from the CVP 534 and the engine 520 may be combined at the second ring gear 558 and may be transmitted to the gear 566, the gear 586, through the third clutch 516 to the gear 588, the gear 576, the shaft 578, the gear 580, the gear 582, and ultimately to the output shaft 510.

Additionally, in some embodiments, engaging reverse clutch 515 and fourth clutch 518 may place powertrain 12g in a fourth reverse mode. Specifically, power from the CVP 534 may be transmitted from the shaft 536 to the gear 538, the gear 537, the shaft 560 to drive the first sun gear 551. In addition, power from engine 520 may be transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, idler gear 548, gear 546, through reverse clutch 515 to gear 544, gear 565, shaft 562, second planetary gears and associated carrier 557, first ring gear 553. The combined power from the CVP 534 and the engine 520 may be combined at the first planetary gear and the associated carrier 552 and may be transmitted to the shaft 572 via gear 568 and gear 570. Power at shaft 572 can be transferred across the fourth clutch 518 to gear 590, gear 592, along shaft 578 to gear 580, gear 582, and ultimately to output shaft 510.

Moreover, in some embodiments, engaging reverse clutch 515 and fifth clutch 519 may place powertrain 12g in a fifth reverse mode. Specifically, power from the CVP 534 may be transmitted from the shaft 536 to the gear 538, the gear 537, the shaft 560 to drive the second sun gear 555. In addition, power from engine 520 may be transmitted to shaft 522, gear 524, gear 525, shaft 527, gear 549, idler gear 548, gear 546, through reverse clutch 515 to gear 544, gear 565, shaft 562, second planetary gear, and associated carrier 557. The combined power from the CVP 534 and the engine 520 may be combined at the second ring gear 558 and may be transmitted to the gear 566, the gear 586, through the fifth clutch 519 to the gear 594, the gear 592, the shaft 578, the gear 580, the gear 582, and ultimately to the output shaft 510.

Further, power system 12g may provide one or more direct drive modes in which power from engine 520 is transmitted to output shaft 510 and power from CVP 534 is prevented from being transmitted to output shaft 510. Specifically, engaging the second clutch 514, the third clutch 516, and the forward clutch 513 may provide a first forward direct drive mode. In this manner, power from engine 520 may be transferred from shaft 522 to gear 524, shaft 527, gear 549, through forward clutch 513 to second planetary gear and carrier 557, and to first ring gear 553. Also, with the second clutch 514 and the third clutch 516 engaged, the second ring gear 558 and the first planetary gears and carrier 552 are locked to the shaft 578 at a fixed ratio, thereby locking to the output shaft 510. This effectively limits the ratio of each side of the variator 540 and locks the engine speed directly to the ground speed of the vehicle 10 at a ratio determined by the number of teeth of the engaged gear train. In this case, the speed of the sun gears 551, 555 is fixed, and the sun gears 551, 555 carry torque between the sides of the variator 540. Further, the first CVP 530 and the second CVP 534 may be unpowered.

Similarly, engaging the fourth clutch 518, the fifth clutch 519, and the forward clutch 513 may provide a second forward direct drive mode. Further, engaging the second clutch 514, the third clutch 516, and the reverse clutch 515 may provide a first reverse direct drive mode. Additionally, engaging the fourth clutch 518, the fifth clutch 519, and the reverse clutch 515 may provide a second reverse direct drive mode.

Additionally, power system 12g may provide one or more seamless transitions between the two of the various modes described above. This means that the mode switch may be substantially imperceptible to the user.

In some embodiments, for example, powertrain 12g may seamlessly switch from a first (series) forward mode in which first clutch 512 and second clutch 514 are engaged to a second (split path) forward mode in which forward clutch 513 and second clutch 514 are engaged. To complete the shift, the first clutch 512 is disengaged and the forward clutch 513 is engaged. Just prior to engagement of forward clutch 513, power flows from engine 520 via shaft 522 to gear 524, gear 525, gear 527 and gear 549. In addition, just prior to engaging forward clutch 513, power flows from CVP 534 to shaft 536, gear 538, gear 535, and across first clutch 512 to shaft 542, gear 544, gear 565, and shaft 562. When the forward clutch 513 is engaged, there may be a substantially zero relative speed between the engageable components of the forward clutch 513. In other words, gear 549 may rotate at substantially the same speed as shaft 562 when forward clutch 513 is engaged to accomplish a seamless transition. In some embodiments, the "substantially zero relative speed" may be a difference between gear 549 and shaft 562 of less than two revolutions per minute (< 2 RPM) when forward clutch 513 is engaged.

Also, in some embodiments, to complete the switch from the second split path forward mode to the third split path forward mode, forward clutch 513 may remain engaged, second clutch 514 may be disengaged, and third clutch 516 may be engaged. When the third clutch 516 is engaged, there may be a substantially zero relative speed between the engageable components of the third clutch 516. In other words, upon a shift, gear 586 and gear 588 may rotate at substantially the same speed.

Likewise, when powertrain 12g is switched from the third split path forward mode to the fourth split path forward mode, there may be a substantially zero relative speed across fourth clutch 518. Additionally, when powertrain 12g switches from the fourth split path forward mode to the fifth split path forward mode, there may be a substantially zero relative speed across fifth clutch 519. It will be appreciated that power system 12g may provide seamless switching in the opposite direction (e.g., from the fifth mode to the fourth mode, etc.). Moreover, it will be appreciated that power system 12g may provide seamless switching between the different reverse modes.

Thus, power system 12g may provide various transmission modes to maintain high operating efficiency. Additionally, powertrain 12g may provide seamless switching between different modes to improve ride quality, reduce wear, etc.

Referring now to FIG. 9, an additional power system 12h is illustrated according to an additional example embodiment. Power system 12h may be substantially similar to the embodiment of fig. 8, except as noted. Parts corresponding to those of fig. 8 are denoted by corresponding reference numerals increased by 100.

As shown, power system 12h may include an engine 620. Power system 12h may additionally include a CVP 630 and a CVP 634.

Power system 12h may further include a variator 640. However, the variator 640 can include a first planetary gear set 691 (low variator) and a second planetary gear set 693 (high variator) mounted on separate shafts that are not concentric. In other words, the first sun gear 651, the first planet gears 652, and the first ring gear 653 may be supported on the first variator shaft 695, the second sun gear 655, the second planet gears 657, and the second ring gear 658 may be supported on the second variator shaft 697, and the first variator shaft 695 and the second variator shaft 697 may be non-concentric. In some embodiments, the first and

second variator shafts

695, 697 can be substantially parallel to and spaced apart from one another. This arrangement may allow for different packages within the vehicle 10. For example, this arrangement may result in the power system 12h being more streamlined and shorter when measured from left to right in FIG. 9. This direction may correspond to the fore-aft direction of the vehicle 10.

Further, the control assembly 664 of the powertrain 12h may include a first clutch 612, a second clutch 614, a third clutch 616, a fourth clutch 618, a fifth clutch 619, a forward clutch 613, and a reverse clutch 615. Powertrain 12h may implement different transmission modes by engaging the same combination of these clutches as described above with respect to fig. 8. The power to the output shaft 610 may vary depending on the current mode, similar to the embodiment of fig. 8. Additionally, power system 12h may implement a substantially seamless transition as described above with respect to FIG. 8.

Other selectable drive components of the clutches, brakes, and/or

control assemblies

56, 156, 256, 356, 464, 564, 664 (or other control assemblies) may be controlled by actuators of known construction (not shown). In turn, these actuators may be controlled by a transmission control unit ("TCU") (not shown), which may receive various inputs from various sensors or devices (not shown) via a CAN bus (not shown) of the vehicle 10. In some embodiments, for example, the various control components may be controlled according to programmed or hardwired switching control logic contained in or executed by the TCU.

Similarly, the various CVPs contemplated by the present disclosure (e.g.,

CVPs

30, 32, 130, 132, 230, 232, 230a, 330, 334, 430, 434, 530, 534, 630, 634) may be controlled by various known means. For example, the TCU or other controller may control the output speed (or other characteristics) of the CVP based on various inputs of various sensors or other controllers, various programmed or hardwired control strategies, and the like. The transfer of converted power between the CVP (e.g., between CVPs 30 and 32) and various intermediate devices such as a battery or other energy storage device (not shown) may also be similarly controlled.

In certain embodiments, an additional set of gears (e.g., a set of range gears) may be interposed between the components of power system 12 and various power sinks (e.g., a differential or PTO shaft (not shown)) of vehicle 10. For example, transmissions having various configurations (e.g., multi-speed range transmissions such as wet clutch range boxes with power shifting capabilities, or power shifting range boxes with various synchronizers) may be provided downstream of the various

clutch devices

62, 64, 162, 164, 166, 262, 264, 266, 360, 362, 470, 472, 473, 476, 478, 512, 513, 514, 515, 516, 518, 519, 612, 613, 614, 615, 616, 618, 619, the

various brakes

364, 474, and/or other selectable transmission components to further regulate speed and torque to power the various vehicle powertrains.

In certain embodiments, the disclosed variator (e.g.,

variator

40, 140, 240, 340, 440, 540, 640) can generally provide infinitely variable control over a particular gear range (e.g., of a downstream power-shifting transmission). Thus, the disclosed variator may be utilized to usefully address the transient speed response of an associated vehicle or other platform (e.g., due to switching between gears, ground speed changes, etc.), a conventional engine may be utilized to usefully address any transient torque demand (e.g., due to vehicle load changes), and an associated control assembly may switch between transmission modes as desired.

In certain embodiments, the disclosed systems may allow for relatively simple customization of various vehicle (or other) platforms. For example, standard engines, standard variators, and standard control assembly components may be provided for various vehicle platforms, addressing the needs of any particular platform by including a particular transmission downstream of the control assembly (and by other customization as needed).

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the disclosure. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It will be further understood that any use of the terms "comprises" and/or "comprising," in this specification, specify the presence of stated features, integers, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and/or groups thereof.

The description of the present disclosure has been presented for purposes of illustration and description, but is not intended to be exhaustive or limited to the disclosure in the form disclosed. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the disclosure. The embodiments explicitly referenced herein were chosen and described in order to best explain the principles of the disclosure and its practical application, and to enable others of ordinary skill in the art to understand the disclosure and to recognize many alternatives, modifications, and variations of the described examples. Accordingly, various other implementations are within the scope of the following claims.

Cross Reference to Related Applications

The present application is a continuation-in-part application of U.S. patent application Ser. No. 15/664,289, filed on 7/31/2017, 4/9/2014 and published as a continuation-in-part application of U.S. patent application Ser. No. 14/249,258, published as U.S. patent publication No. 2015/0292608/15/2015. The disclosures of the above applications are incorporated herein by reference.

Claims

1. A work vehicle, the work vehicle comprising:

an engine;

continuously variable power sources, i.e., CVPs;

a variator operably connected to the engine and the CVP;

An output shaft operatively connected to the variator; and

a control assembly including a plurality of transmission members configured to provide selection between a first mode, a second mode, and a third mode;

in the first mode, the control assembly is configured to transmit CVP power from the CVP to the output shaft and prevent engine power from being transmitted from the engine to the output shaft;

in the second mode, the control assembly is configured to transfer engine power from the engine to the variator, to transfer CVP power from the CVP to the variator, and to transfer a combination of engine power and CVP power from the variator to the output shaft; and is also provided with

In the third mode, the control assembly is configured to transfer engine power from the engine to the output shaft and prevent transmission of CVP power from the CVP to the output shaft; and is also provided with

The control assembly is configured to provide at least one seamless switch between two of the first mode, the second mode and the third mode,

wherein the control assembly includes a first clutch and a second clutch;

Wherein the first clutch is configured to be engaged and the second clutch is configured to be disengaged to provide a low speed range for the output shaft;

wherein the first clutch is configured to be disengaged and the second clutch is configured to be engaged to provide a high speed range for the output shaft; and is also provided with

The work vehicle further includes an output countershaft supporting a first gear rotatably engaged with the first clutch, a second gear rotatably engaged with the second clutch, and a third gear rotatably engaged with the output shaft.

2. The work vehicle of claim 1, wherein the control assembly includes an engageable transmission member configured to move between an engaged position and a disengaged position;

wherein the engageable transmission member comprises a first part and a second part rotatably engaged in the engaged position, the first part and second part being disengaged in the disengaged position;

wherein in the at least one seamless transition, the engageable transmission member is configured to move from the disengaged position to the engaged position, the first and second components being configured to rotate at substantially the same angular velocity as the engageable transmission member moves from the disengaged position to the engaged position.

3. The work vehicle of claim 2, wherein the engageable transmission member is a clutch.

4. A work vehicle according to claim 3, wherein the clutch is the first clutch supported on a first shaft;

wherein the control assembly includes the second clutch supported on a second shaft, the first shaft and the second shaft being non-concentric; and is also provided with

Wherein the control assembly is configured to provide at least one seamless transition in which the first clutch is disengaged and the second clutch is engaged.

5. The work vehicle of claim 1, wherein, in the first mode, the CVP is configured to supply a first CVP power and rotatably drive a first variator member of a planetary gear set of the variator;

wherein, in the first mode, the CVP is configured to supply a second CVP power to and rotatably drive a second variator member of the planetary gear set;

wherein, in the first mode, the third variator member of the planetary gearset is configured to output the recombined CVP power to rotatably drive the output shaft.

6. The work vehicle of claim 5, wherein the CVP is a first CVP;

the work vehicle further includes a second CVP electrically connected to the first CVP;

wherein the second CVP has a generator mode in which the second CVP generates electrical power from mechanical power supplied by the engine and wherein the second CVP provides the generated electrical power to the first CVP; and is also provided with

Wherein the second CVP has a motor mode in which the second CVP provides power to the engine.

7. The work vehicle of claim 1, wherein the variator comprises a first planetary gear set and a second planetary gear set interconnected and supported on a common shaft.

8. The work vehicle of claim 7, wherein the control assembly includes a clutch supported on the common shaft; and is also provided with

Wherein the clutch is configured to selectively power the variator from one of the engine and the CVP.

9. The work vehicle of claim 1, wherein the variator comprises a first planetary gear set supported on a first shaft and a second gear set supported on a second shaft; and is also provided with

Wherein the first and second axes are non-concentric.

10. A work vehicle, the work vehicle comprising:

an engine;

continuously variable power sources, i.e., CVPs;

a variator operably connected to the engine and the CVP;

an output shaft operatively connected to the variator; and

a control assembly including a plurality of transmission members configured to provide selection between a first mode and a second mode, the control assembly configured to provide at least one seamless transition between the first mode and the second mode;

in the second mode, the control assembly is configured to transfer engine power from the engine to the variator, to transfer CVP power from the CVP to the variator, and to transfer a combination of engine power and CVP power from the variator to the output shaft;

in the first mode, the CVP is configured to supply a first CVP power and rotatably drive a first variator member of the variator's planetary gear set;

Wherein, in the first mode, the third variator member of the planetary gearset is configured to output a recombined CVP power to rotatably drive the output shaft,

wherein the control assembly includes a first clutch and a second clutch;

11. The work vehicle of claim 10, wherein the CVP is a first CVP;

12. The work vehicle of claim 10, wherein the control assembly includes an engageable transmission member configured to move between an engaged position and a disengaged position;

13. The work vehicle of claim 12, wherein the engageable transmission member is a clutch.

14. The work vehicle of claim 13, wherein the clutch is the first clutch supported on a first shaft;

15. The work vehicle of claim 10, wherein the control assembly is configured to provide selection between the first mode, the second mode, and a third mode; and is also provided with

Wherein, in the third mode, the control assembly is configured to transfer engine power from the engine to the output shaft and prevent transmission of CVP power from the CVP to the output shaft.

16. The work vehicle of claim 10, wherein the variator comprises a first planetary gear set and a second planetary gear set interconnected and supported on a common shaft.

17. The work vehicle of claim 16, wherein the control assembly includes a clutch supported on the common shaft; and is also provided with

18. The work vehicle of claim 10, wherein the variator comprises a first planetary gear set supported on a first shaft and a second gear set supported on a second shaft; and is also provided with

Wherein the first and second axes are non-concentric.