Ten-speed transmission

This application claims the benefit of U.S. Provisional Application No. 61/023,506, filed on Jan. 25, 2008, which is hereby incorporated in its entirety herein by reference.

The invention relates generally to a multiple speed transmission having a plurality of planetary gear sets and a plurality of torque transmitting devices and more particularly to a transmission having ten or more speeds, four planetary gear sets and a plurality of torque transmitting devices.

The statements in this section merely provide background information related to the present disclosure and may or may not constitute prior art.

A typical multiple speed transmission uses a combination of friction clutches, planetary gear arrangements and fixed interconnections to achieve a plurality of gear ratios. The number and physical arrangement of the planetary gear sets, generally, are dictated by packaging, cost and desired speed ratios.

While current transmissions achieve their intended purpose, the need for new and improved transmission configurations which exhibit improved performance, especially from the standpoints of efficiency, responsiveness and smoothness and improved packaging, primarily reduced size and weight, is essentially constant. Accordingly, there is a need for an improved, cost-effective, compact ten speed transmission.

A transmission is provided having an input member, an output member, four planetary gear sets, a plurality of coupling members and a plurality of torque transmitting devices. Each of the planetary gear sets include first, second and third members. A first interconnecting member continuously interconnects the third member of the first planetary gear set with the first member of the second planetary gear set. A second interconnecting member continuously interconnects the second member of the second planetary gear set with the third member of the third planetary gear set. A third interconnecting member continuously interconnects the first member of the third planetary gear set with the third member of the fourth planetary gear set. Six torque transmitting mechanisms selectively engageable to interconnects one of the first, second, and third members with at least one other of the first members, second members, third members and a stationary member. The torque transmitting mechanisms are selectively engageable in combinations of at least four to establish at least ten forward speed ratios and at least one reverse speed ratio between the input member and the output member.

In another embodiment of the present invention, a first of the six torque transmitting mechanisms is selectively engageable to interconnect the first member of the first planetary gear set with the first member of the fourth planetary gear set.

In yet another embodiment of the present invention, a second of the six torque transmitting mechanisms is selectively engageable to interconnect the first member of the first planetary gear set with the second member of the fourth planetary gear set.

In yet another embodiment of the present invention, a third of the six torque transmitting mechanisms is selectively engageable to interconnect the input member with at least one of the first member of the third planetary gear set and the third member of the fourth planetary gear set.

In yet another embodiment of the present invention, a fourth of the six torque transmitting mechanisms is selectively engageable to interconnect at least one of the second member of the second planetary gear set and the third member of the third planetary gear set with the second member of the fourth planetary gear set.

In yet another embodiment of the present invention, a fifth of the six torque transmitting mechanisms is selectively engageable to interconnect at least one of the third member of the first planetary gear set and the first member of the second planetary gear set with the stationary member.

In yet another embodiment of the present invention, a sixth of the six torque transmitting mechanisms is selectively engageable to interconnect the third member of the second planetary gear set with the stationary member.

In yet another embodiment of the present invention, the third member of the first planetary gear set and first member of the second, third and fourth planetary gear sets are sun gears, the second members of the first, second, third and fourth planetary gear sets are carrier members and the first member of the first planetary gear set and third member of the second, third and fourth planetary gear sets are ring gears.

In still another embodiment of the present invention, the input member is continuously interconnected with the second member of the first planetary gear set and the output member is continuously interconnected with the second member of the third planetary gear set.

In still another embodiment of the present invention, two of the torque transmitting mechanisms are brakes and four of the torque transmitting mechanisms are clutches.

In still another embodiment of the present invention, the stationary member is a transmission housing.

Further objects, aspects and advantages of the present invention will become apparent by reference to the following description and appended drawings wherein like reference numbers refer to the same component, element or feature.

The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.

FIG. 1 is a lever diagram of an embodiment of a ten speed transmission according to the present invention;

FIG. 2 is a diagrammatic illustration of an embodiment of a ten speed transmission according to the present invention; and

FIG. 3 is a truth table presenting the state of engagement of the various torque transmitting elements in each of the available forward and reverse speeds or gear ratios of the transmission illustrated in FIGS. 1 and 2 .

The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses.

At the outset, it should be appreciated that the embodiments of the ten speed automatic transmission of the present invention have an arrangement of permanent mechanical connections between the elements of the four planetary gear sets. A third component or element of a first planetary gear set is permanently coupled to a first component or element of the second planetary gear set. A second component or element of a second planetary gear set is permanently coupled to a third component or element of the third planetary gear set. A first component or element of the third planetary gear set is permanently coupled to third component or element of the fourth planetary gear set.

Referring now to FIG. 1 , an embodiment of a ten speed transmission 10 is illustrated in a lever diagram format. A lever diagram is a schematic representation of the components of a mechanical device such as an automatic transmission. Each individual lever represents a planetary gear set wherein the three basic mechanical components of the planetary gear are each represented by a node. Therefore, a single lever contains three nodes: one for the sun gear, one for the planet gear carrier, and one for the ring gear. The relative length between the nodes of each lever can be used to represent the ring-to-sun ratio of each respective gear set. These lever ratios, in turn, are used to vary the gear ratios of the transmission in order to achieve an appropriate ratios and ratio progression. Mechanical couplings or interconnections between the nodes of the various planetary gear sets are illustrated by thin, horizontal lines and torque transmitting devices such as clutches and brakes are presented as interleaved fingers. Further explanation of the format, purpose and use of lever diagrams can be found in SAE Paper 810102, “The Lever Analogy: A New Tool in Transmission Analysis” by Benford and Leising which is hereby fully incorporated by reference.

The transmission 10 includes an input shaft or member 12 , a first planetary gear set 14 having three nodes: a first node 14 A, a second node 14 B and a third node 14 C, a second planetary gear set 16 having three nodes: a first node 16 A, a second node 16 B and a third node 16 C, a third planetary gear set 18 having three nodes: a first node 18 A, a second node 18 B and a third node 18 C, a fourth planetary gear set 20 having three nodes: a first node 20 A, a second node 20 B and a third node 20 C and an output shaft or member 22 .

The input member 12 is coupled to the second node 14 B of the first planetary gear set 14 . The output member 22 is coupled to the second node 18 B of the third planetary gear set 18 . The third node 14 C of the first planetary gear set 14 is coupled to the first node 16 A of the second planetary gear set 16 . The second node 16 B of the second planetary gear set 16 is coupled to the third node 18 C of the third planetary gear set 18 . The first node 18 A of the third planetary gear set 18 is coupled to the third node 20 C of the fourth planetary gear set 20 .

A first clutch 26 selectively connects the first node 14 A of the first planetary gear set 14 with the first node 20 A of the fourth planetary gear set 20 . A second clutch 28 selectively connects the first node 14 A of the first planetary gear set 14 with the second node 20 B of the fourth planetary gear set 20 . A third clutch 30 selectively connects the second node 14 B of the second planetary gear set 14 to the third node 20 C of the fourth planetary gear set 20 . A fourth clutch 32 selectively connects the second node 16 B of the second planetary gear set 16 and the third node 18 C of the third planetary gear set 18 with the second node 20 B of the fourth planetary gear set 20 . A first brake 34 selectively connects the third node 14 C of the first planetary gear set 14 to a stationary member or transmission housing 50 . A second brake 36 selectively connects the third node 16 C of the second planetary gear set 16 to a stationary member or transmission housing 50 .

Referring now to FIG. 2 , a stick diagram presents a schematic layout of the embodiment of the ten speed transmission 10 according to the present invention. In FIG. 2 , the numbering from the lever diagram of FIG. 1 is carried over. The clutches and couplings are correspondingly presented whereas the nodes of the planetary gear sets now appear as components of planetary gear sets such as sun gears, ring gears, planet gears and planet gear carriers.

For example, the planetary gear set 14 includes a sun gear member 14 C, a ring gear member 14 A and a planet gear carrier member 14 B that rotatably supports a set of planet gears 14 D (only one of which is shown). The sun gear member 14 C is connected for common rotation with a first shaft or intermediate member 42 . The ring gear member 14 A is connected for common rotation with a second shaft or intermediate member 44 . The planet carrier member 14 B is connected for common rotation with input shaft or member 12 . The set of planet gears 14 D are each configured to intermesh with both the sun gear member 14 C and the ring gear member 14 A.

The planetary gear set 16 includes a sun gear member 16 A, a ring gear member 16 C and a planet gear carrier member 16 B that rotatably supports a set of planet gears 16 D (only one of which is shown). The sun gear member 16 A is connected for common rotation with first shaft or intermediate member 42 and with a third shaft or intermediate member 46 . The ring gear member 16 C is connected to brake 36 . The planet carrier member 16 B is connected for common rotation with a fourth shaft or intermediate member 48 . The planet gears 16 D are each configured to intermesh with both the sun gear member 16 A and the ring gear member 16 C.

The planetary gear set 18 includes a sun gear member 18 A, a ring gear member 18 C and a planet gear carrier member 18 B that rotatably supports a set of planet gears 18 D (only one of which is shown). The sun gear member 18 A is connected for common rotation with a fifth intermediate member 52 . The ring gear member 18 C is connected for common rotation with a fourth shaft or intermediate member 48 . The planet carrier member 18 B is connected for common rotation with the output shaft or member 22 . The planet gears 18 D are each configured to intermesh with both the sun gear member 18 A and the ring gear member 18 C.

The planetary gear set 20 includes a sun gear member 20 A, a ring gear member 20 C and a planet gear carrier member 20 B that rotatably supports a set of planet gears 20 D (only one of which is shown). The planet gears 20 D are each configured to intermesh with both the sun gear member 20 A and the ring gear member 20 C. The sun gear member 20 A is connected for common rotation with a sixth shaft or intermediate member 54 . The ring gear member 20 C is connected for common rotation with fifth shaft or intermediate member 52 . The planet carrier member 20 B is connected for common rotation with a seventh intermediate member 56 .

The input shaft or member 12 is continuously connected to an engine (not shown) or to a turbine of a torque converter (not shown). The output shaft or member 22 is continuously connected with the final drive unit or transfer case (not shown).

The torque-transmitting mechanisms or clutches 26 , 28 , 30 , 32 and brakes 34 and 36 allow for selective interconnection of the shafts or interconnecting members, members of the planetary gear sets and the housing. For example, the first clutch 26 is selectively engageable to connect the second shaft or intermediate member 44 with the sixth shaft or intermediate member 54 . The second clutch 28 is selectively engageable to connect the second shaft or intermediate member 44 with the seventh shaft or intermediate member 56 . The third clutch 30 is selectively engageable to connect the input shaft or member 12 with the fifth shaft or intermediate member 52 . The fourth clutch 32 is selectively engageable to connect the fourth shaft or intermediate member 48 with the seventh shaft or intermediate member 56 . The first brake 34 is selectively engageable to connect the third shaft or intermediate member 46 with the stationary element or the transmission housing 50 in order to restrict the member 46 from rotating relative to the transmission housing 50 . The second brake 36 is selectively engageable to connect the ring gear member 16 C with the stationary element or the transmission housing 50 in order to restrict the member 16 C from rotating relative to the transmission housing 50 .

Referring now to FIG. 2 and FIG. 3 , the operation of the embodiment of the ten speed transmission 10 will be described. It will be appreciated that transmission 10 is capable of transmitting torque from the input shaft or member 12 to the output shaft or member 22 in at least ten forward speed or torque ratios and at least one reverse speed or torque ratio with triple overdrive. Each forward and reverse speed or torque ratio is attained by engagement of one or more of the torque-transmitting mechanisms (i.e. first clutch 26 , second clutch 28 , third clutch 30 , fourth clutch 32 , first brake 34 and second brake 36 ), as will be explained below. FIG. 3 is a truth table presenting the various combinations of torque-transmitting mechanisms that are activated or engaged to achieve the various gear states. An “X” in the box means that the particular clutch or brake is engaged to achieve the desired gear state. An “∘” represents that the particular torque transmitting device (i.e. a brake or clutch) is on or active, but not carrying torque. Actual numerical gear ratios of the various gear states are also presented although it should be appreciated that these numerical values are exemplary only and that they may be adjusted over significant ranges to accommodate various applications and operational criteria of the transmission 10 . An example of the gear ratios that may be obtained using the embodiments of the present invention are also shown in FIG. 3 . Of course, other gear ratios are achievable depending on the gear diameter, gear teeth count and gear configuration selected.

To establish a reverse gear, the first clutch 26 , fourth clutch 32 , first brake 34 and second brake 36 are engaged or activated. The first clutch 26 connects the second shaft or intermediate member 44 with the sixth shaft or intermediate member 54 . The fourth clutch 32 connects the fourth shaft or intermediate member 48 with the seventh shaft or intermediate member 56 . The first brake 34 connects the third shaft or intermediate member 46 with the stationary element or the transmission housing 50 in order to restrict the member 46 from rotating relative to the transmission housing 50 . The second brake 36 connects the ring gear member 16 C with the stationary element or the transmission housing 50 in order to restrict the member 16 C from rotating relative to the transmission housing 50 . Likewise, the ten forward ratios are achieved through different combinations of clutch and brake engagement, as shown in FIG. 3 .

It will be appreciated that the foregoing explanation of operation and gear states of the ten speed transmission 10 assumes, first of all, that all the clutches not specifically referenced in a given gear state are inactive or disengaged and, second of all, that during gear shifts, i.e., changes of gear state, between at least adjacent gear states, a clutch engaged or activated in both gear states will remain engaged or activated.

The description of the invention is merely exemplary in nature and variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.