| Title of Invention | MULTI-SPEED TRANSMISSION |
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| Abstract | A transmission is provided having an input member (12), an output member (22), four planetary gear sets (14, 16, 18, 20), a plurality of coupling members and a plurality of torque transmitting devices (26, 28, 30, 32, 34). Each of the planetary gear sets includes first (14A, 16C, 18B, 20B), second (14C, 16A, 18C, 20A) and third members (14B, 16B, 18A, 20C). The torque transmitting devices may include clutches. |
| Full Text | MULTI-SPEED TRANSMISSION CROSS-REFERENCE TO RELATED APPLICATIONS [0001] This application claims the benefit of U.S. Provisional Application No. 60/916,439, filed on May 7, 2007. The disclosure of the above application is incorporated herein by reference. FIELD [0002] 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 eight or more speeds, four planetary gear sets and a plurality of torque transmitting devices. BACKGROUND [0003] The statements in this section merely provide background information related to the present disclosure and may or may not constitute prior art. [0004] 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. [0005] 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 multiple speed transmission. SUMMARY [0006] 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 includes first, second and third members. The torque transmitting devices are for example clutches. [0007] An embodiment of the transmission includes an input member, an output member, and first, second, third and fourth planetary gear sets each having first, second and third members. A first interconnecting member continuously interconnects the third member of the first planetary gear set with the third member of the second planetary gear set. A second interconnecting member continuously interconnects the second member of the second planetary gear set with a stationary element. A third interconnecting member continuously interconnects the second member of the second planetary gear set with the first member of the first planetary gear set. A fourth interconnecting member continuously interconnects the first member of the third planetary gear set with the first member of the fourth planetary gear set. Five torque-transmitting mechanisms are selectively engageable to interconnect one of the first, second, and third members with another of the first, second, and third members. The torque-transmitting mechanisms are selectively engageable in combinations of at least three to establish at least eight forward speed ratios and at least one reverse speed ratio between the input member and the output member. [0008] In one aspect of the embodiment of the present invention, a first of the five torque transmitting mechanisms is selectively engageable to interconnect the input member with the first member of the second planetary gear set. [0009] In another aspect of the embodiment of the present invention, a second of the five torque transmitting mechanisms is selectively engageable to interconnect the third member of the first planetary gear set with the third member of the fourth planetary gear set. [0010] In yet another aspect of the embodiment of the present invention, a third of the five torque transmitting mechanisms is selectively engageable to interconnect the second member of the first planetary gear set with the third member of the fourth planetary gear set. [0011] In yet another aspect of the embodiment of the present invention, a fourth of the five torque transmitting mechanisms is selectively engageable to interconnect the third member of the first planetary gear set with the second member of the fourth planetary gear set. [0012] In yet another aspect of the embodiment of the present invention, a fifth of the five torque transmitting mechanisms is selectively engageable to interconnect the second member of the fourth planetary gear set with the third member of the third planetary gear set. [0013] In yet another aspect of the embodiment of the present invention, the input member is continuously interconnected with the second member of the third planetary gear set and the output member is continuously interconnected with the third member of the third planetary gear set. [0014] In yet another aspect of the embodiment of the present invention, the five torque transmitting mechanisms are clutches. [0015] In yet another aspect of the embodiment of the present invention, the first members are sun gears, the second members are carrier members, and the third members are ring gears. [0016] Another embodiment of the transmission of the present invention includes an input member, an output member, first, second, third and fourth planetary gear sets each having first, second and third members, wherein the input member is continuously interconnected with the second member of the third planetary gear set and the output member is continuously interconnected with the third member of the third planetary gear set. A first interconnecting member continuously interconnects the third member of the first planetary gear set with the third member of the second planetary gear set. A second interconnecting member continuously interconnects the second member of the second planetary gear set with a stationary element. A third interconnecting member continuously interconnects the second member of the second planetary gear set with the first member of the first planetary gear set. A fourth interconnecting member continuously interconnects the first member of the third planetary gear set with the first member of the fourth planetary gear set. A first torque transmitting mechanism is selectively engageable to interconnect the input member with the first member of the second planetary gear set. A second torque transmitting mechanism is selectively engageable to interconnect the third member of the first planetary gear set with the third member of the fourth planetary gear set. A third torque transmitting mechanism is selectively engageable to interconnect the second member of the first planetary gear set with the third member of the fourth planetary gear set. A fourth torque transmitting mechanism is selectively engageable to interconnect the third member of the first planetary gear set with the second member of the fourth planetary gear set. A fifth torque transmitting mechanism is selectively engageable to interconnect the second member of the fourth planetary gear set with the third member of the third planetary gear set. The torque-transmitting mechanisms are selectively engageable in combinations of at least three to establish at least eight forward speed ratios and at least one reverse speed ratio between the input member and the output member. [0017] In one aspect of the embodiment of the present invention, the torque transmitting mechanisms are clutches. [0018] In another aspect of the embodiment of the present invention, the first members are sun gears, the second members are carrier members, and the third members are ring gears. [0019] Another embodiment of the transmission of the present invention includes an input member, an output member, first, second, third and fourth planetary gear sets each having a sun gear member, a carrier member, and a ring gear member, wherein the input member is continuously interconnected with the carrier member of the third planetary gear set and the output member is continuously interconnected with the ring gear member of the third planetary gear set. A first interconnecting member continuously interconnects the ring gear member of the first planetary gear set with the ring gear member of the second planetary gear set. A second interconnecting member continuously interconnects the carrier member of the second planetary gear set with a stationary element. A third interconnecting member continuously interconnects the carrier member of the second planetary gear set with the sun gear member of the first planetary gear set. A fourth interconnecting member continuously interconnects the sun gear member of the third planetary gear set with the sun gear member of the fourth planetary gear set. A first torque transmitting mechanism is selectively engageable to interconnect the input member with the sun gear member of the second planetary gear set. A second torque transmitting mechanism is selectively engageable to interconnect the ring gear member of the first planetary gear set with the ring gear member of the fourth planetary gear set. A third torque transmitting mechanism is selectively engageable to interconnect the carrier member of the first planetary gear set with ■ the ring gear member of the fourth planetary gear set. A fourth torque transmitting mechanism is selectively engageable to interconnect the ring gear member of the first planetary gear set with the carrier member of the fourth planetary gear set. A fifth torque transmitting mechanism is selectively engageable to interconnect the carrier member of the fourth planetary gear set with the ring gear member of the third. planetary gear set. The torque- transmitting mechanisms are selectively engageable in combinations of at least three to establish at least eight forward speed ratios and at least one reverse • speed ratio between the input member and the output member. i [0020] 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. DRAWINGS [0021] The drawings described herein are for illustration purposes only ,. and are not intended to limit the scope of the present disclosure in any way. [0022] Figure 1 is a lever diagram of an embodiment of an eight speed transmission according to the present invention; [0023] Figure 2 is a diagrammatic view of an embodiment of an eight speed transmission according to the present invention; and [0024] Figure 3 is a truth table presenting the state of engagement of I i the various torque transmitting clutches in each of the available forward and : reverse speeds or gear ratios of the transmission illustrated in Figures 1 and 2. i DETAILED DESCRIPTION [0025] The following description is-merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. [0026] At the outset, it should be appreciated that in the particular example provided, the eight speed automatic transmission of the present invention has an arrangement of permanent mechanical connections between the elements of the four planetary gear sets. A first component or element of a first planetary gear set is permanently coupled to a ground. A first component or element of a second planetary gear set is also permanently coupled to a ground. A second component or element of the first planetary gear set is permanently coupled to a second component or element of the second planetary gear set. Finally, a second component or element of the third planetary gear set is permanently coupled to a second component or element of a fourth planetary gear set. [0027] Referring now to FIG. 1, an embodiment of an eight 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 set 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. i 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 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 mechanisms or devices such as clutches and brakes are , presented as interleaved fingers. If the device is a brake, one set of the fingers is grounded. 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. [0028] The transmission 10 includes an input shaft or member 12, a first planetary gear set 14 having three nodes: a first node 14A, a second node 14B and a third node 14C, a second planetary gear set 16 having three nodes: a first node 16A, a second node 16B and a third node 16C, -a third planetary gear set 18 having three nodes: a first node 18A, a second node 18B and a third node 18C, a fourth planetary gear set 20 having three nodes: a first node 20A, a second node 20B and a third node 20C and an output shaft or member 22. [0029] The input member 12 is coupled to the third node 18C of the third planetary gear set 18. The output member 22 is coupled to the first node 18A of the third planetary gear set 18. The first node 14A of the first planetary • gear set 14 is coupled to a ground or transmission housing 40. The first node 16A of the second planetary gear set 16 is also coupled to the ground or transmission housing 40. The second node 14B of the first planetary gear set 14 is coupled to the second node 16B of the second planetary gear set 16. The j ' second node 18B of the third planetary gear set 18 is coupled to the second node 20B of the fourth planetary gear set 20. [0030] A first clutch 26 selectively connects the input member 12 to the third node 16C of the second planetary gear set 16. A second clutch 28 selectively connects the second node 14B of the first planetary gear set 14 to'the first node 20A of the fourth planetary gear set 20. A third clutch 30 selectively connects the second node 14B of the first planetary gear set 14 to the third node 20C of the fourth planetary gear set 20. A fourth clutch 32 selectively connects the third node 14C of the first planetary gear set 14 to the third node 20C of the fourth planetary gear set 20. A fifth clutch 34 selectively connects the first node 20A of the fourth planetary gear set 20 to the first node 18A of the third planetary gear set 18. [0031] Referring now to Fig. 2, a stick diagram presents a schematic layout of the embodiment of the eight 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 i 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. [0032] For example, the planetary gear set 14 is a planetary gear set that includes a sun gear member 14A, a planet gear carrier member 14C and a ring gear member 14B. The sun gear member 14A is connected for common rotation with a first shaft or interconnecting member 42. The ring gear member 14B is connected to a second shaft or interconnecting member 44 and to a third j i shaft or interconnecting member 46. The planet gear carrier member 14C rotatably supports a set of planet gears 14D (only one shown) and is connected for common rotation with a fourth shaft or interconnecting member 48. The planet gears 14D are configured to intermesh with the sun gear member 14A and the ring gear member 14B. [0033] 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). [0034] The planetary gear set 16 is a planetary gear set that includes a sun gear member 16C, a planet carrier member 16A that rotatably supports a set of planet gears 16D and a ring gear member 16B. The sun gear member 16C is connected for common rotation with the first clutch 26. The planet carrier member 16A is connected to the ground or transmission housing 40 by a fifth shaft or interconnecting member 50 in order to restrict the planet carrier member 16A from rotating relative to the ground or transmission housing 40. The planet carrier member 16A is also connected for common rotation with the first interconnecting member 42. The ring gear member 16B is connected for common rotation with the second interconnecting member 44. The planet gears 16D are configured to intermesh with both the sun gear member 16C and the ring gear member 16B. [0035] The planetary gear set 18 is a planetary gear set that includes a sun gear member 18B, a ring gear member 18A and a planet carrier member 18C that rotatably supports a set of planet gears 18D. The sun gear member i 18B is connected for common rotation with a sixth shaft or interconnecting member 52. The ring gear member 18A is connected for common rotation with a seventh shaft or interconnecting member 54 and with the output member 22. The planet carrier member 18C is connected for common rotation with the input member 12. The planet gears 18D are configured to intermesh with both sun • gear member 18B and ring gear member 18A. [0036] * The planetary gear set 20 is a planetary gear set that includes a sun gear member 20B, a ring gear member 20C and a planet carrier member 20A that rotatably supports a set of planet gears 20D. The sun gear member 20B is connected for common rotation with the sixth interconnecting member 52. The ring gear member 20C is connected for common rotation with an eighth shaft or interconnecting member 56. The planet carrier member 20A is connected for common rotation with a ninth shaft or interconnecting member 58. The planet ; gears 20D are configured to intermesh with both the sun gear member 20B and the ring gear member 20C. [0037] The torque-transmitting mechanisms or clutches 26, 28, 30, 32 and 34 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 sun gear member 16C to the input member 12. The second clutch 28 is selectively engageable to connect the third interconnecting member 46 to the ninth interconnecting member 58. The third clutch 30 is selectively engageable to connect the third interconnecting member 46 to the eighth interconnecting member 56. The fourth clutch 32 is selectively engageable to connect the fourth interconnecting i member 48 to the eighth interconnecting member 56. The fifth clutch 34 is selectively engageable to connect the seventh interconnecting member 54 to the ninth interconnecting member 58. [0038] Referring now to Figs. 2 and 3, the operation of the embodiment of the eight 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 eight forward speed or torque ratios and at least one reverse speed or torque ratio. 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, and fifth clutch 34), 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. 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. [0039] To establish reverse gear, the first clutch 26, the second clutch I 28, and the fifth clutch 34 are engaged or activated. The first clutch 26 connects the second sun gear member 16C to the input member 12. The second clutch 28 connects the third interconnecting member 46 to the ninth interconnecting member 58. The fifth clutch 34 connects the seventh interconnecting member 54 ; to the ninth interconnecting member 58. Likewise, the eight forward ratios are achieved through different combinations of clutch engagement, as shown in Fig. 3. [0040] It will be appreciated that the foregoing explanation of operation and gear states of the eight 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. [0041] 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. WE CLAIM 1. A transmission comprising: an input member (12); an output member (22); first (14), second (16), third (18) and fourth (20) planetary gear sets each having first (14A, 16C, 18B, 20B), second (14C, 16A, 18C, 20A) and third (14B, 16B, 18A, 20C) members, wherein the input member is continuously interconnected with the second member (18C) of the third (18) planetary gear set and the output member (22) is continuously interconnected with the third member (18A) of the third planetary gear set (18). a first interconnecting member (42) continuously interconnecting the third member (14B) of the first planetary gear set (14) with the third member (16B) of the second planetary gear set (16); a second interconnecting member (44) continuously interconnecting the second member (16A) of the second planetary gear set (16) with a stationary element (40); a third interconnecting member (46) continuously interconnecting the second member (16A) of the second planetary gear set (16) with the first member (14A) of the first planetary gear set (14); a fourth interconnecting member (48) continuously,interconnecting the first member (18B) of the third planetary gear set (18) with the first member (20B) of the fourth planetary gear set (20); a first torque transmitting mechanism (26) selectively engageable to interconnect the input member (12) with the first member (16C) of the second planetary gear set (16); a second torque transmitting mechanism (28) selectively engageable to interconnect the third member (14B) of the first planetary gear (14) set with the third member (20C) of the fourth planetary gear set (20); a third torque transmitting mechanism (30) selectively engageable to interconnect the second member (14C) of the first planetary gear set (14) with the third member (20C) of the fourth planetary gear set (20); a fourth torque transmitting mechanism (32) selectively engageable to interconnect the third member (14B) of the first planetary gear set (14) with the second member (20A) of the fourth planetary gear set (20); and a fifth torque transmitting mechanism (34) selectively engageable to interconnect the second member (20A) of the fourth planetary gear set (20) with the third member (18A) of the third planetary gear set (18); and wherein the torque-transmitting mechanisms (26, 28, 30, 32, 34) are selectively engageable in combinations of at least three to establish at least eight forward speed ratios and at least one reverse speed ratio between the input member (12) and the output member (22). 2. The transmission as claimed in claim 1 wherein a first (26) of the five torque transmitting mechanisms is selectively engageable to interconnect the input member (12) with the first member (16C) of the second planetary gear set (16). 3. The transmission as claimed in claim 2 wherein a second (28) of the five torque transmitting mechanisms is selectively engageable to interconnect the third member (14B) of the first planetary gear set (14) with the third member (20C) of the fourth planetary gear set (20). 4. The transmission as claimed in claim 3 wherein a third (30) of the five torque transmitting mechanisms is selectively engageable to interconnect the second member (14C) of the first planetary gear set (14) with the third member (20C) of the fourth planetary gear set (20). 5. The transmission as claimed in claim 4 wherein a fourth (32) of the five torque transmitting mechanisms is selectively engageable to interconnect the third member (14B) of the first planetary gear set (14) with the second member (20A) of the fourth planetary gear set (20). 6. The transmission as claimed in claim 5 wherein a fifth (34) of the five torque transmitting mechanisms is selectively engageable to interconnect the second member (20A) of the fourth planetary gear set (20) with the third member (18A) of the third planetary gear set (18). 7. The transmission as claimed in claim 5 wherein the input member (12) is continuously interconnected with the second member (18C) of the third planetary gear set (18) and the output member is continuously interconnected with the third member (18A) of the third planetary gear set (18). 8. The transmission as claimed in claim 1 wherein the five torque transmitting mechanisms (26, 28, 30, 32, 34) are clutches. 9. The transmission as claimed in claim 1 wherein the first members are sun gears ' (14A, 16C, 18B, 20B), the second (14C, 16A, 18C, 20A) members are carrier members, and the third members (14B, 16B, 18A, 20C) are ring gears. 10.The transmission as claimed in claim 1 wherein the torque transmitting mechanisms (26, 28, 30, 32, 34) are clutches. 11.The transmission as claimed in claim 1 wherein the first members are sun gears (14A, 18C, 18B, 20B), the second members are carrier members (14C, 16A, 18C, 20A), and the third members are ring gears (14B, 16B, 18A, 20C). ABSTRACT MULTI-SPEED TRANSMISSION A transmission is provided having an input member (12), an output member (22), four planetary gear sets (14, 16, 18, 20), a plurality of coupling members and a plurality of torque transmitting devices (26, 28, 30, 32, 34). Each of the planetary gear sets includes first (14A, 16C, 18B, 20B), second (14C, 16A, 18C, 20A) and third members (14B, 16B, 18A, 20C). The torque transmitting devices may include clutches. |
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| Patent Number | 269038 | |||||||||||||||
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| Indian Patent Application Number | 696/KOL/2008 | |||||||||||||||
| PG Journal Number | 40/2015 | |||||||||||||||
| Publication Date | 02-Oct-2015 | |||||||||||||||
| Grant Date | 29-Sep-2015 | |||||||||||||||
| Date of Filing | 09-Apr-2008 | |||||||||||||||
| Name of Patentee | GM GLOBAL TECHNOLOGY OPERATIONS, INC. | |||||||||||||||
| Applicant Address | 300 RENAISSANCE CENTER, DETROIT, MICHIGAN | |||||||||||||||
Inventors:
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| PCT International Classification Number | F16H3/62; F16H3/44 | |||||||||||||||
| PCT International Application Number | N/A | |||||||||||||||
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PCT Conventions:
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