Patent Publication Number: US-2022235856-A1

Title: Torque converter lockup clutch structure

Description:
RELATED APPLICATIONS 
     The present application is a divisional of U.S. patent application Ser. No. 16/790,898, which was filed on Feb. 14, 2020, and which is a continuation of U.S. patent application Ser. No. 16/122,049, which was filed on Sep. 5, 2018, and which is a continuation of U.S. patent application Ser. No. 15/043,810, which was filed on Feb. 15, 2016, and which claims the benefit of U.S. Provisional Application Ser. No. 62/117,143, which was filed on Feb. 17, 2015. The contents of those applications are hereby expressly incorporated by reference herein in their entireties. 
    
    
     FIELD OF THE DISCLOSURE 
     The present disclosure relates to a transmission system, and in particular to a lockup clutch assembly of a torque converter for the transmission system. 
     BACKGROUND 
     A torque converter is a fluid coupling device that is used to transfer rotating power from a power unit, such as an engine or electric motor, to a power-transferring device such as a transmission. A torque converter can have a clutch system to allow the torque converter to be selectable for either fluid coupling or mechanical coupling depending on the engagement of the clutch system. The transmission is an apparatus through which power and torque can be transmitted from a vehicle&#39;s power unit to a load-bearing device such as a drive axis. Conventional transmissions include a variety of gears, shafts, and clutches that transmit torque therethrough. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The above-mentioned aspects of the present disclosure and the manner of obtaining them will become more apparent and the disclosure itself will be better understood by reference to the following description of the embodiments of the disclosure, taken in conjunction with the accompanying drawings, wherein: 
         FIG. 1  is an exemplary block diagram and schematic view of one illustrative embodiment of a powered vehicular system; 
         FIG. 2  is a top half cross-sectional view of a conventional torque converter; 
         FIG. 3  is a top half cross-sectional view of a torque converter as disclosed herein; 
         FIG. 4  is an elevated perspective view of a backing plate with a radial lip as disclosed herein; 
         FIG. 5  is a cross sectional view of the backing plate of  FIG. 4 ; 
         FIG. 6  is an elevated perspective view of a backing plate without a radial lip as disclosed herein; 
         FIG. 7  is a cross sectional view of the backing plate of  FIG. 6 ; 
         FIG. 8  is an elevated perspective view of a single piece backing plate as disclosed herein; 
         FIG. 9  is a cross sectional view of the backing plate of  FIG. 8 ; 
         FIG. 10  is an elevated perspective view of a single piece bent backing plate assembly as disclosed herein; 
         FIG. 11  is a cross section view of the backing plate of  FIG. 10 ; and 
         FIG. 12  is a perspective view of a piston plate of the torque converter of  FIG. 3 . 
     
    
    
     Corresponding reference numerals are used to indicate corresponding parts throughout the several views. 
     DETAILED DESCRIPTION 
     The embodiments of the present disclosure described below are not intended to be exhaustive or to limit the disclosure to the precise forms disclosed in the following detailed description. Rather, the embodiments are chosen and described so that others skilled in the art may appreciate and understand the principles and practices of the present disclosure. 
     The terminology used herein is for the purpose of describing particular illustrative embodiments only and is not intended to be limiting. As used herein, the singular forms “a”, “an” and “the” may be intended to include the plural forms as well, unless the context clearly indicates otherwise. Similarly, plural forms may have been used to describe particular illustrative embodiments when singular forms would be applicable as well. The terms “comprises,” “comprising,” “including,” and “having,” are inclusive and therefore 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 method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order discussed or illustrated, unless specifically identified as an order of performance. It is also to be understood that additional or alternative steps may be employed. 
     Referring now to  FIG. 1 , a block diagram and schematic view of one illustrative embodiment of a vehicular system  100  having a drive unit  102  and transmission  118  is shown. In the illustrated embodiment, the drive unit  102  may include an internal combustion engine, diesel engine, electric motor, or other power-generating device. The drive unit  102  is configured to rotatably drive an output shaft  104  that is coupled to an input or pump shaft  106  of a conventional torque converter  108 . The input or pump shaft  106  is coupled to an impeller or pump  110  that is rotatably driven by the output shaft  104  of the drive unit  102 . The torque converter  108  further includes a turbine  112  that is coupled to a turbine shaft  114 , and the turbine shaft  114  is coupled to, or integral with, a rotatable input shaft  124  of the transmission  118 . The transmission  118  can also include an internal pump  120  for building pressure within different flow circuits (e.g., main circuit, lube circuit, etc.) of the transmission  118 . The pump  120  can be driven by a shaft  116  that is coupled to the output shaft  104  of the drive unit  102 . In this arrangement, the drive unit  102  can deliver torque to the shaft  116  for driving the pump  120  and building pressure within the different circuits of the transmission  118 . 
     The transmission  118  can include a planetary gear system  122  having a number of automatically selected gears. An output shaft  126  of the transmission  118  is coupled to or integral with, and rotatably drives, a propeller shaft  128  that is coupled to a conventional universal joint  130 . The universal joint  130  is coupled to, and rotatably drives, an axle  132  having wheels  134 A and  134 B mounted thereto at each end. The output shaft  126  of the transmission  118  drives the wheels  134 A and  134 B in a conventional manner via the propeller shaft  128 , universal joint  130  and axle  132 . 
     A conventional lockup clutch  136  is connected between the pump  110  and the turbine  112  of the torque converter  108 . The operation of the torque converter  108  is conventional in that the torque converter  108  is operable in a so-called “torque converter” mode during certain operating conditions such as vehicle launch, low speed and certain gear shifting conditions. In the torque converter mode, the lockup clutch  136  is disengaged and the pump  110  rotates at the rotational speed of the drive unit output shaft  104  while the turbine  112  is rotatably actuated by the pump  110  through a fluid (not shown) interposed between the pump  110  and the turbine  112 . In this operational mode, torque multiplication occurs through the fluid coupling such that the turbine shaft  114  is exposed to drive more torque than is being supplied by the drive unit  102 , as is known in the art. The torque converter  108  is alternatively operable in a so-called “lockup” mode during other operating conditions, such as when certain gears of the planetary gear system  122  of the transmission  118  are engaged. In the lockup mode, the lockup clutch  136  is engaged and the pump  110  is thereby secured directly to the turbine  112  so that the drive unit output shaft  104  is directly coupled to the input shaft  124  of the transmission  118 , as is also known in the art. 
     The transmission  118  further includes an electro-hydraulic system  138  that is fluidly coupled to the planetary gear system  122  via a number, J, of fluid paths,  140   1 - 140   1 , where J may be any positive integer. The electro-hydraulic system  138  is responsive to control signals to selectively cause fluid to flow through one or more of the fluid paths,  140   1 - 140   1 , to thereby control operation, i.e., engagement and disengagement, of a plurality of corresponding friction devices in the planetary gear system  122 . The plurality of friction devices may include, but are not limited to, one or more conventional brake devices, one or more torque transmitting devices, and the like. Generally, the operation, i.e., engagement and disengagement, of the plurality of friction devices is controlled by selectively controlling the friction applied by each of the plurality of friction devices, such as by controlling fluid pressure to each of the friction devices. In one example embodiment, which is not intended to be limiting in any way, the plurality of friction devices include a plurality of brake and torque transmitting devices in the form of conventional clutches that may each be controllably engaged and disengaged via fluid pressure supplied by the electro-hydraulic system  138 . In any case, changing or shifting between the various gears of the transmission  118  is accomplished in a conventional manner by selectively controlling the plurality of friction devices via control of fluid pressure within the number of fluid paths  140   1 - 140   1 . 
     The system  100  further includes a transmission control circuit  142  that can include a memory unit  144 . The transmission control circuit  142  is illustratively microprocessor-based, and the memory unit  144  generally includes instructions stored therein that are executable by a processor of the transmission control circuit  142  to control operation of the torque converter  108  and operation of the transmission  118 , i.e., shifting between the various gears of the planetary gear system  122 . It will be understood, however, that this disclosure contemplates other embodiments in which the transmission control circuit  142  is not microprocessor-based, but is configured to control operation of the torque converter  108  and/or transmission  118  based on one or more sets of hardwired instructions and/or software instructions stored in the memory unit  144 . 
     In the system  100  illustrated in  FIG. 1 , the torque converter  108  and the transmission  118  include a number of sensors configured to produce sensor signals that are indicative of one or more operating states of the torque converter  108  and transmission  118 , respectively. For example, the torque converter  108  illustratively includes a conventional speed sensor  146  that is positioned and configured to produce a speed signal corresponding to the rotational speed of the pump shaft  106 , which is the same rotational speed of the output shaft  104  of the drive unit  102 . The speed sensor  146  is electrically connected to a pump speed input, PS, of the transmission control circuit  142  via a signal path  152 , and the transmission control circuit  142  is operable to process the speed signal produced by the speed sensor  146  in a conventional manner to determine the rotational speed of the turbine shaft  106 /drive unit output shaft  104 . 
     The transmission  118  illustratively includes another conventional speed sensor  148  that is positioned and configured to produce a speed signal corresponding to the rotational speed of the transmission input shaft  124 , which is the same rotational speed as the turbine shaft  114 . The input shaft  124  of the transmission  118  is directly coupled to, or integral with, the turbine shaft  114 , and the speed sensor  148  may alternatively be positioned and configured to produce a speed signal corresponding to the rotational speed of the turbine shaft  114 . In any case, the speed sensor  148  is electrically connected to a transmission input shaft speed input, TIS, of the transmission control circuit  142  via a signal path  154 , and the transmission control circuit  142  is operable to process the speed signal produced by the speed sensor  148  in a conventional manner to determine the rotational speed of the turbine shaft  114 /transmission input shaft  124 . 
     The transmission  118  further includes yet another speed sensor  150  that is positioned and configured to produce a speed signal corresponding to the rotational speed of the output shaft  126  of the transmission  118 . The speed sensor  150  may be conventional, and is electrically connected to a transmission output shaft speed input, TOS, of the transmission control circuit  142  via a signal path  156 . The transmission control circuit  142  is configured to process the speed signal produced by the speed sensor  150  in a conventional manner to determine the rotational speed of the transmission output shaft  126 . 
     In the illustrated embodiment, the transmission  118  further includes one or more actuators configured to control various operations within the transmission  118 . For example, the electro-hydraulic system  138  described herein illustratively includes a number of actuators, e.g., conventional solenoids or other conventional actuators, that are electrically connected to a number, J, of control outputs, CP 1 -CP J , of the transmission control circuit  142  via a corresponding number of signal paths  72   1 - 72   J , where J may be any positive integer as described above. The actuators within the electro-hydraulic system  138  are each responsive to a corresponding one of the control signals, CP 1 -CP J , produced by the transmission control circuit  142  on one of the corresponding signal paths  72   1 - 72   J  to control the friction applied by each of the plurality of friction devices by controlling the pressure of fluid within one or more corresponding fluid passageway  140   1 - 140   J , and thus control the operation, i.e., engaging and disengaging, of one or more corresponding friction devices, based on information provided by the various speed sensors  146 ,  148 , and/or  150 . 
     The friction devices of the planetary gear system  122  are illustratively controlled by hydraulic fluid which is distributed by the electro-hydraulic system in a conventional manner. For example, the electro-hydraulic system  138  illustratively includes a conventional hydraulic positive displacement pump (not shown) which distributes fluid to the one or more friction devices via control of the one or more actuators within the electro-hydraulic system  138 . In this embodiment, the control signals, CP 1 -CP J , are illustratively analog friction device pressure commands to which the one or more actuators are responsive to control the hydraulic pressure to the one or more frictions devices. It will be understood, however, that the friction applied by each of the plurality of friction devices may alternatively be controlled in accordance with other conventional friction device control structures and techniques, and such other conventional friction device control structures and techniques are contemplated by this disclosure. In any case, however, the analog operation of each of the friction devices is controlled by the control circuit  142  in accordance with instructions stored in the memory unit  144 . 
     In the illustrated embodiment, the system  100  further includes a drive unit control circuit  160  having an input/output port (I/O) that is electrically coupled to the drive unit  102  via a number, K, of signal paths  162 , wherein K may be any positive integer. The drive unit control circuit  160  may be conventional, and is operable to control and manage the overall operation of the drive unit  102 . The drive unit control circuit  160  further includes a communication port, COM, which is electrically connected to a similar communication port, COM, of the transmission control circuit  142  via a number, L, of signal paths  164 , wherein L may be any positive integer. The one or more signal paths  164  are typically referred to collectively as a data link. Generally, the drive unit control circuit  160  and the transmission control circuit  142  are operable to share information via the one or more signal paths  164  in a conventional manner. In one embodiment, for example, the drive unit control circuit  160  and transmission control circuit  142  are operable to share information via the one or more signal paths  164  in the form of one or more messages in accordance with a society of automotive engineers (SAE) J-1939 communications protocol, although this disclosure contemplates other embodiments in which the drive unit control circuit  160  and the transmission control circuit  142  are operable to share information via the one or more signal paths  164  in accordance with one or more other conventional communication protocols (e.g., from a conventional databus such as J1587 data bus, J1939 data bus, IESCAN data bus, GMLAN, Mercedes PT-CAN). 
     Referring to  FIG. 2 , one embodiment is shown of a top half, cross-sectional view of a conventional torque converter  200 . Torque converter  200  includes a front cover assembly  202  fixedly attached to a rear cover  204  or shell at a coupled location. In one example, the coupled location can include a bolted joint, a welded joint, or any other type of coupling means. The converter  200  includes a turbine assembly  206  with turbine blades, a shell, and a core ring. The converter  200  also includes a pump assembly  208  with impellor or pump blades, an outer shell, and a core ring. 
     A stator assembly  210  is axially disposed between the pump assembly  208  and the turbine assembly  206 . The stator assembly  210  can include a housing, one or more stator blades, and a one-way clutch  212 . The one-way clutch  212  may be a roller or sprag design as is commonly known in the art. 
     The torque converter  200  can include a clutch assembly  218  that transmits torque from the front cover  202  to a turbine hub  214 . The clutch assembly  218  includes a piston plate  216 , a backing plate  226 , a plurality of clutch plates  220 , and a plurality of reaction plates  222 . The plurality of clutch plates  220  and reaction plates  222  can be splined to the turbine hub  214 , which is bolted to a turbine assembly as shown in  FIG. 2 . The piston plate  216  can be hydraulically actuated to engage and apply the clutch assembly  218 , thereby “hydraulically coupling” the turbine assembly  206  and pump assembly  208  to one another. Hydraulic fluid can flow through a dedicated flow passage in the torque converter  200  on a front side of the piston plate  216  to urge the plate  216  towards and into engagement with the clutch assembly  218 . One skilled in the art can appreciate how this and other designs of fluid-coupling devices can be used for fluidly coupling an engine and transmission to one another. 
     Referring now to  FIG. 3 , an embodiment is shown of a top half, cross-sectional view of a torque converter  300 . Torque converter  300  includes a front cover  302  coupled to a rear cover  304  or shell at a coupling location. In one example, the coupled location can include a bolted joint, a welded joint, or any other type of coupling means. The torque converter  300  includes a turbine assembly  306  having turbine blades, a shell, and a core ring. The torque converter  300  also includes a pump assembly  308  with impellor or pump blades, an outer shell, and a core ring. 
     A stator assembly  310  may be axially disposed between the pump assembly  308  and the turbine assembly  306 . The stator assembly  310  can include a housing, one or more stator blades, and a one-way clutch  312 . The one-way clutch  312  may be a roller or sprag design as is commonly known in the art. 
     The torque converter  300  can include a clutch assembly  318  that transmits torque from the front cover  302  to a turbine hub  314 . The turbine hub  314  may further be splined or otherwise coupled to a turbine shaft of a transmission (not shown). The clutch assembly  318  may include a piston  316  disposed within a cavity created by the front cover  302 . The piston  316  may have a radial protrusion  354  that is defined radially about the piston  316  and protrudes partially towards the rear cover  304 . At least one clutch plate  320  and at least one reaction plate  322  may also be disposed within the cavity. The clutch plate  320  and the reaction plate  322  may be radially disposed to axially adjacent to the protrusion  354  of the piston  316 . Additionally a backing plate  326  may also be disposed within the cavity created by the front cover  302  at a location that permits the backing plate  326  to be substantially adjacent to the clutch plate  320  and/or the reaction plate  322 . 
     The clutch assembly  318  may be coupled to the turbine hub  314  through a damper  328 . The damper  328  may provide for damping torque variations experienced between the front cover  302  and the turbine hub  314  as is known in the art. One of ordinary skill in the art may be familiar with the plurality ways the torque load distribution in a torque converter can be damped, and this disclosure is not be limited to any one type of damper. For example, a coil spring may be used to rotationally couple two components to one another. When a torsional load is distributed from one component to the other, the spring may provide a damped transmission of the torsional load. Additionally, any other type of damping system can be used. Damping systems such as hydraulic shock absorbers, gas springs, clutch assemblies, and the like are considered and this disclosure is not limited to any particular type of damper. 
     The piston  316  can be hydraulically actuated to engage and apply the clutch assembly  318 , thereby mechanically coupling the turbine assembly  306  and front cover  302  to one another. Fluid can flow through a dedicated flow passage in the torque converter  300  on a front side of the piston  316  to urge the piston  316  towards, and into engagement with, the clutch assembly  318 . One skilled in the art can appreciate how this and other designs of clutch assemblies can be used for mechanically coupling two rotating components to one another. 
     One embodiment where the backing plate  326  can be supported by a first member  332  and a second member  334  is shown in  FIG. 3 . The first member  332  and the second member  334  can be used to transfer torsional loads from the front cover  302  to the turbine hub  314  when the clutch assembly  318  is in the engaged position. In one nonlimiting example, when the clutch is engaged, the torque applied to the front cover  302  may be transferred into the nose hub  330 . The nose hub  330  may be fixedly coupled to the first and second member  332 ,  334  and transfer the applied torque through the clutch assembly  318 , down the damper  328 , and into the turbine hub  314 . 
     More specifically, the first member  332  may be coupled to the backing plate  326  at a radially outer location of the backing plate  326 , while the second member  334  may be coupled to the backing plate  326  at a radially inner location of the backing plate  326 . Alternatively, the backing plate  326  may be a continuation of, or integrally formed with, the second member  334 . 
     The first member  332  may be substantially annular in shape with a central hole or bore therethrough. Further, the first member  332  may have an arc-shaped cross section as shown in  FIG. 3 . The arc-shaped cross section may be coupled at one end to the backing plate  326  and coupled at the other end to the second member  334 . 
     The second member  334  may also be annular and be formed with a plurality of bends when viewed in the cross section of  FIG. 3 . The second member  334  may form the backing plate  326  and terminate at a backing plate lip  336 . The second member  334  may also have at least one finger  338  that may engage the splines of the clutch plate  320  or reaction plate  322 . 
     Now referring to  FIG. 12 , an isolated view of a piston  1200  is shown. In one embodiment of the present disclosure, the piston  316  may be located partially along one end of the clutch assembly  318  as shown in  FIG. 3 . The piston  316  may have a protrusion  354  that is defined radially in the piston  316 . The protrusion  354  may also align at least partially with the clutch assembly  318 . The protrusion  354  can extend sufficiently away from a planar surface  1210  of a piston plate  1204  so a portion of the protrusion  354  will contact the clutch assembly  318  when the piston  316  is disposed in the engaged position. 
     The piston  316  may have an inner sleeve  1206  and an outer sleeve  1208 . The inner sleeve  1206  may have an inner radius that is slightly greater than an outer radius of an internal portion  342  of a nose hub  330  as shown in  FIG. 3 . The radius of the inner sleeve  1206  may be sufficiently large to allow the piston  316  to slide axially along the internal portion  342  of the nose hub  330  while simultaneously being able to substantially restrict fluid from passing between the inner sleeve  1206  and the nose hub  330 . To further limit fluid transfer through the inner sleeve  1206 , a first seal  344  may be located between the inner sleeve  1206  and the internal portion  342  of the nose hub  330 . 
     The outer sleeve  1208  may have an outer radius that is slightly less than an inner portion  346  of the front cover  302  as shown in  FIG. 3 . The outer radius of the outer sleeve  1208  may be adequately sized to allow the piston  316  to slide axially along the inner portion  346  of the front cover  302  while simultaneously being tight enough to substantially restrict fluid from passing between the inner portion of the front cover  302  and the outer sleeve  1208 . To further limit fluid transfer through the outer sleeve  1208 , a second seal  348  may be located between the outer sleeve  1208  and the inner portion  346  of the front cover  302 . 
     The inner sleeve  1206  and the outer sleeve  1208  may be configured to allow the piston  316  to move both axially and radially about a first or rotation axis  406 . The axial movement of the piston  316  may be controlled by filling a piston plate cavity  350  with a pressurized fluid (not shown) via one or more of the fluid paths  140   1 - 140   J . As the piston plate cavity  350  is filled with fluid, the piston  316  may move axially away from the front cover  302 . As the piston  316  is forced away from the front cover  302 , the protrusion  354  in the piston  316  may contact the clutch assembly  318 . In turn, the clutch plate  320  and the reaction plate  322  may be forced into contact with one another sufficiently to transfer torsional loads between the front cover  302  and the turbine hub  314 . Further, when pressurized fluid is no longer supplied to the piston plate cavity  350 , the protrusion  354  may no longer provide sufficient axial force to the clutch assembly  318  to provide mechanical coupling between the front cover  302  and the turbine hub  314  through the clutch assembly  318 . 
     In one embodiment, the piston  316  is not required to transfer any torque to the clutch assembly  318 . In this embodiment, the first and second seal  344 ,  348  may allow sufficient frictional properties between the piston  316 , the front cover  302 , and the nose hub  330  to rotate the piston  316  as the front cover rotates  316 . In a different embodiment, the frictional properties of the first and second seal  344 ,  348  may allow the piston  316  to rotate independently of the front cover  302 . In yet another embodiment, the piston  316  may be radially coupled to either the front cover  302  or the nose hub  330 , or both, so that the piston  316  rotates as the front cover  302  rotates. 
     When the clutch assembly  318  is in the engaged or “lockup” position, the backing plate  326  may adequately counteract the axial force from the piston  316  to keep the backing plate  326  from substantially deflecting towards the rear cover  304 . 
     Now referring to  FIG. 4 , one embodiment of a backing plate assembly  400  is shown. The backing plate assembly  400  may be radially defined about the first axis  406 . The backing plate assembly  400  can have the lip  336 , backing plate  326 , finger  338 , and second member  334  shown in  FIG. 3 . The second member  334  may include at least one bend  340  radially formed about the first axis  406  to increase the rigidity of the backing plate assembly  400 . Further, the backing plate  326  may be substantially the same piece of material as the second member  334 . More specifically, as the second member  334  extends radially away from the first axis  406 , it may define the backing plate  326  by creating a substantially planar radial surface that is perpendicular to the first axis  406 . 
     Additionally, the finger  338  may be formed from a partially cutout portion of the backing plate  326 . More specifically, the finger  338  may be a cutout of a portion of the backing plate  326  that is bent towards the front cover  302  at a radial distance from the first axis  406  to create a substantially 90 degree bend from the surface of the backing plate  326 . 
     The second member  334  may have a lip  402  defined at a first end thereof about the radially innermost portion of the backing plate assembly  400 . The lip  402  may partially define a passage capable of allowing a shaft to pass therethrough. The backing plate assembly  400  may extend radially outward from the lip  402  to form a hub portion  404 . The hub portion  404  may be radially defined about the first axis  406  to correspond with the interior dimensions of the nose hub  330  ( FIG. 3 ). The hub portion  404  can be dimensioned to be received by a cavity created by the nose hub  330 . Further, the nose hub  330  can be disposed to substantially encompass the lip  402  and the remaining hub portion  404  of the backing plate assembly  400  as shown in  FIG. 3 . 
     In one embodiment, the nose hub  330  can be used to couple the front cover  302  to the second member  334 . The nose hub  330  may be coupled to the front cover  302  at a coupling point  352  in a manner that is sufficient to transfer the torsional loads from the front cover to the nose hub  330 . In one embodiment, the front cover  302  may be welded to the nose hub  330  at the coupling point  352  but this disclosure is not limited to such a coupling method. One skilled in the art will understand how other coupling methods may be utilized to achieve similar results. Such methods as fasteners, adhesives, splines, threads, press fittings, and the like may be used to couple the nose hub  330  and the front cover  302  to one another. 
     The nose hub  330  may also be coupled to the backing plate assembly  400 . The backing plate assembly  400  may be press fit or otherwise disposed within the cavity created by the nose hub  330 . Additionally, the backing plate assembly  400  may also be coupled to the nose hub  330  utilizing one or more of the plurality of coupling methods described above. Once the torque converter  300  is fully assembled, torsional inputs into the front cover  302  may be distributed to the backing plate assembly  400  through the nose hub  330 . 
     Further, the backing plate assembly  400  can terminate at the backing plate lip  336  located at the radially outermost portion of the second member  334 . The backing plate lip  336  may be defined circumferentially about the outermost diameter or edge of the second member  334 . In addition, the lip  336  may be substantially perpendicular to the surface of the backing plate  326 . By terminating the backing plate  326  at the backing plate lip  336 , the stiffness of the backing plate assembly  400  may be improved. While one embodiment may utilize the backing plate lip  336  that is perpendicular to the backing plate  326 , this disclosure is not intended to be limited to such an orientation. One skilled in the art will understand how a plurality of different degree bends may also be utilized to achieve substantially the same result. 
     A cutaway view  500  of the backing plate assembly  400  is shown in  FIG. 5 . More specifically, a first and second location  502 ,  504  are shown as one non-limiting example of where the first member  332  may couple to the second member  334 . The first location  502  may be a radially inner portion of the first member  332  that is substantially adjacent with a portion of the second member  334 . The second location  504  may be a radially outer portion of the first member  332  that is substantially adjacent with a portion of the second member  334 . The first member  332  and the second member  334  can be coupled to one another in a plurality of ways such as welds, bolts, rivets, chemical bonding agents or the like. In one non-limiting aspect, the first location  502  and the second location  504  may substantially affix the first member  332  and the second member  334  to one another. In another aspect, the two members may not be fixed to one another. 
     The backing plate  326  may experience axial forces about the first axis  406  when the piston  316  engages the clutch assembly  318  as described above. By coupling the first member  332  to the second member  334  at the first and second locations  502 ,  504 , the rigidity of the backing plate assembly  400  may be enhanced. More specifically, as the piston  316  applies the axial force to the backing plate  326 , the first member  332  may substantially inhibit any axial movement of the backing plate  326  by being coupled to the second member  334  at both the first and second location  502 ,  504 . 
     When an axial force  506  ( FIG. 5 ) is applied by the piston  316 , the backing plate  326  may resist axial movement by transferring a resistive force  508  through the backing plate assembly  400  to the turbine hub  314 . Further, because the backing plate assembly  400  may resist axial movement at a radially inner portion  510 , it may be more susceptible to axial deflection about the radially outermost portion of the backing plate  326 . In one embodiment, the second location  504  may be a radially outermost portion of the backing plate  326  to substantially resist axial deflection about the backing plate  326 . By coupling the first member  332  to the second member  334  at such a second location  504 , the backing plate  326  may substantially resist deflection under the axial force  506  created by the piston  316 . 
     Referring back to  FIG. 4 , the finger  338  is also more clearly shown. The finger  338  may be formed during the manufacturing process for the second member  334 . A plurality of fingers  338  may be spaced radially equidistant from one another to allow the engagement between each finger  338  and the reaction plate  322  or the clutch plate  320 . Each finger  338  can be sufficiently strong to transfer any radial forces from the input shaft  106  of the torque converter  108  through the damper  328  and into the turbine shaft  114  when the clutch assembly  318  is in the engaged position. 
     While one embodiment of the disclosure may have the plurality of fingers  338  equidistantly spaced from one another, one skilled in the art will understand how a plurality of offset distances may be used as well to achieve substantially the same result. Further, the number of fingers and the width of each finger may vary greatly depending on the particular load being transferred by each finger. As is known in the art, the particular design of the plurality of fingers  338  can be varied to accommodate the various loads that may need to be transferred therethrough. 
     The embodiment shown in  FIGS. 4 and 5  may be manufactured utilizing a stamping/punching process and a welding process. The first step of the manufacturing process may be stamping or punching the first member  332  out of a sheet of material. The sheet can be any desired material composition or otherwise and may be the appropriate thickness to resist substantial deformation. The stamping or punching process can take place either simultaneously or in different steps. 
     If the stamping or punching process is done in different steps, the needed material for the first member  332  can be punched out of the supplied material to create a blank. The blank can have the desired dimensions to correlate with the stamping process to create the desired final backing plate assembly  400  dimensions. In one non-limiting example, the blank for the first member  332  may have a diameter larger than the final diameter of the first member  332 . During the stamping process, the blank for the first member  332  may be formed into the desired final shape by pressing the blank between a die. The die may form the bend  340  into the first member  332 . Similarly to the above process described for the first member  332 , the second member  334  may undergo a punching or stamping process to achieve a desired final result. 
     After the first member  332  and the second member  334  have been formed, it may be necessary to couple the two pieces to one another to create an adequately strong backing plate assembly  400 . One method of coupling the first member  332  and the second member  334  to one another may include welding the two components to one another. A weld or welds may be located at both the first location  502  and the second location  504 . The weld or welds may be continuous throughout the first location  502  and the second location  504  of the first member  332 . The weld or welds may also be segmented throughout the first location  502  and the second location  504  of the first member  332 . 
     While methods for using a press have been described herein as a way to form the components of the backing plate assembly  400 , this disclosure is not limited to any particular manufacturing method. One skilled in the art will understand how a laser, waterjet, CNC mill, plasma cutter, and/or the like may be used to cut a material into a desired blank. Further, while a press and a die have been described as one way to create the desired shape of the backing plate assembly  400 , other methods such as molding, machining, 3-D printing, additive manufacturing, casting or any other similar manufacturing process may be used. 
     While welding has been described as one method for coupling the first member  332  to the second member  334  other coupling methods may be used. More specifically, the two plates may be bolted, riveted, press fit, or otherwise coupled to one another and no single coupling method should be seen as limiting. 
     Another embodiment of the backing plate assembly  600  absent a lip is shown in  FIGS. 6 and 7 . In this embodiment, the backing plate  326  may terminate at a radial end that is planar with the surface of the backing plate  326 . A cross-section view  700  of the backing plate assembly  600  is shown in  FIG. 7 . Similar to the embodiment shown in  FIG. 4 , this embodiment may also have a first member  702  and a second member  704 . The first member  702  and the second member  704  may be substantially similar in shape to the first backing plate  334  and the second backing plate  336 , respectively, with the exception of the removed backing plate lip  336 . 
     In one embodiment, it may be advantageous to have the backing plate  326  terminate in a way that is planar to the backing plate  326  surface. The embodiment shown in  FIGS. 6 and 7  may allow for the backing plate  326  to be compatible with clutch assemblies of various dimensions. For example, in the backing plate assembly  400  of  FIG. 4 , the clutch assembly  318  may need to be designed to fit within the backing plate  326  as defined by the backing plate lip  336 . In  FIGS. 6 and 7 , however, the backing plate is not bound along an external edge of the backing plate  326 . 
     A different embodiment may have a single piece backing plate assembly  800 , as shown in  FIGS. 8 and 9 , instead of having a plurality of pieces coupled together to form the backing plate assembly. The backing plate assembly  800  may have at least one finger  802  that may extend at least partially outward from a planar surface  804  of the backing plate  800 . The finger  802  may be aligned along a radius that defines an inner radial edge of a backing plate  806 . 
     A cutaway view  900  of the backing plate assembly  800  is shown in  FIG. 9 . The finger  802  may be formed as a substantially perpendicular bend from the planar surface  804  of the backing plate assembly  800 . More specifically, the finger  802  can be formed by cutting a partial profile of the finger  802  out of the backing plate  806  prior to making the substantially perpendicular bend. 
     One aspect of the embodiment shown in  FIGS. 8 and 9  is that it may only require one manufacturing step. For example, a stamping process may form the single piece backing plate  800  in one step. One example of manufacturing the embodiment shown in  FIGS. 8 and 9  is first supplying a sheet of material having a desired thickness to a press. The press may then form the features of the single piece backing plate  800  by pressing the material into a die. A punching process may simultaneously be executed that can separate the single piece backing plate  800  from the excess material. The pressing step and the punching step may be performed either simultaneously or in any order, and this disclosure is not limited to any one method or particular order. 
     One advantage of the embodiment shown in  FIGS. 8 and 9  is that the single piece backing plate  800  may be complete after the stamping or punching process. More specifically, the single piece backing plate  800  may be completed without welding or otherwise coupling multiple pieces to one another to form the backing plate  800 . Thus, the process is relatively simple and parts can be easily mass produced. 
     Yet another embodiment of the present disclosure is shown in  FIGS. 10 and 11 . Another backing plate assembly  1000  is shown in  FIG. 10  that is made of substantially one piece. The backing plate assembly  1000  may include many of the features previously described such as a backing plate  1002 , at least one finger  1004 , at least one bend  1006 , a shaft passage or bore  1008 , and a hub portion  1010 . The backing plate assembly  1000  can function in substantially the same way as previous embodiments. 
     As illustrated by the cutaway portion  1100  shown in  FIG. 11 , the backing plate assembly  1000  can be formed of one piece of material. The material can include a series of bends and cuts to allow it to be formed into the backing plate assembly  1000  shown in  FIG. 10 . The backing plate  1002  may be formed by a 180 degree bend  1018  at the outermost portion of the backing plate assembly  1000 . There may be an approximately 180 degree bend  1018  at a radially outermost section of each of a plurality of backing plate sections  1012 . Each section  1012  may define a portion of the backing plate  1002  where the material of the backing plate assembly  1000  is folded under the backing plate  1002  surface to create a twofold layer of material. The backing plate sections  1012  may be defined partially by at least one cutout  1014  in the backing plate material. Additional cutouts  1014  may be spaced radially around the backing plate assembly  1000 . 
     The backing plate sections  1012  may terminate about a radially outermost edge to create substantially straight exterior edges  1016  of the backing plate assembly  1000 . The straight exterior edges  1016  may be angularly offset from one another so that they combine to create a substantially 360 degree sum. For example, there may be eight sections  1012  that create a substantially octagonal circumference with their eight straight exterior edges  1016 . 
     A portion of the cutout  1014  may be utilized to form the finger  1004 . Additionally, in one embodiment the finger  1004  may be formed by a substantially 90 degree bend  1104  of the backing plate  1002 . Further, the bend  1006  in the finger  1004  may be a 180 degree bend at the distal portion of the finger  1004  from the backing plate  1002 . The bend  1006  may terminate at a base  1108  of the finger  1004 . As a result of the 180 degree bend, the finger  1004  may be comprised of a twofold layer of the backing plate assembly  1000  material. 
     In one embodiment of the finger  1004 , a weld may be created along the base  1108  of the finger  1004 . The weld may add sufficient rigidity to the finger  1004  to allow the backing plate assembly  1000  to adequately transfer torsional loads from the clutch assembly  318  to the nose hub  330 . Additionally, a weld may be created along the sides of the finger  1004  to further couple the two layers to one another. This too may be utilized to increase the load bearing capacity of the finger  1004 . 
     In yet another embodiment of the present disclosure, the backing plate  1002  may also include a weld or other means to increase the stiffness of the backing plate assembly  1000 . The weld may be located along a backing plate edge terminus  1110 . By locating the weld along the terminus  1110 , the rigidity of the backing plate  1002  can be increased by both the added reinforcement of the weld and by additional layers of the backing plate material in parallel alignment with one another. 
     While exemplary embodiments incorporating the principles of the present disclosure have been disclosed hereinabove, the present disclosure is not limited to the disclosed embodiments. Instead, this application is intended to cover any variations, uses, or adaptations of the disclosure using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this disclosure pertains and which fall within the limits of the appended claims.