(12) United States Patent
`Maienschein et al.
`
`US006244401B1
`US 6,244,401 B1
`(10) Patent No.:
`Jun. 12, 2001
`(45) Date of Patent:
`
`(54) FORCE TRANSMITTING APPARATUS
`(75) Inventors: Stephan Maienschein, Bühl; Marc
`Meisner, Bühl Weitenung; Rudolf
`Hönemann, Ottersweier, all of (DE)
`(73) Assignee: Luk Getriebe-Systeme GmbH,
`Buhl/Baden (DE)
`Subject to any disclaimer, the term of this
`patent is extended or adjusted under 35
`U.S.C. 154(b) by 0 days.
`
`(*) Notice:
`
`4,347,717 * 9/1982 Lamarche ...................... 192/213.1 X
`5,667,042 * 9/1997 Olsen et al. ........................ 192/3.29
`5,975,261 * 11/1999 Woerner et al. .................... 192/3.29
`
`* cited by examiner
`
`Primary Examiner—Richard M. Lorence
`(74) Attorney, Agent, or Firm—Darby & Darby
`(57)
`ABSTRACT
`
`A torque-transmitting apparatus for motor vehicles includes
`(21) Appl. No.: 09/305,504
`a hydrokinetic torque converter with a housing connected to
`(22) Filed:
`May 5, 1999
`the driving shaft of an engine. The housing contains a pump
`(30)
`Foreign Application Priority Data
`and a turbine, the latter arranged to drive an input shaft of
`a power train. At least one damper is arranged in the power
`May 6, 1998 (DE) .............................................. 198 20 128
`flow path between the turbine and a rotary output element of
`Jun. 18, 1998 (DE) .............................................. 198 27 127
`the apparatus. The damper has an input member constrained
`(51) Int. Cl." … F16H 45/02
`to rotate with the turbine and an output member connected
`(52) U.S. Cl. .................... 192/3.3; 192/70.17; 192/213.1;
`to the rotary output element. The input member and the
`464/66
`output member are rotatable relative to each other against
`(58) Field of Search .................................. 192/3.28, 3.29,
`the opposing forces of energy-storing devices arranged
`192/3.3, 70, 17, 212, 213, 213.1; 464/66,
`67
`between the input member and the output member. The input
`member has a radially outer portion in form-locking engage
`ment with the turbine.
`
`(56)
`
`References Cited
`U.S. PATENT DOCUMENTS
`4,138,003 * 2/1979 Malloy ................................ 192/3.29
`
`49 Claims, 11 Drawing Sheets
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`
`

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`U.S. Patent
`
`Jun. 12, 2001
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`U.S. Patent
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`Jun. 12, 2001
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`US 6,244,401 B1
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`U.S. Patent
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`Jun. 12, 2001
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`Sheet 3 of 11
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`US 6,244,401 B1
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`

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`U.S. Patent
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`Jun. 12, 2001
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`Sheet 4 of 11
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`US 6,244,401 B1
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`Valeo Exhibit 1015, pg. 5
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`U.S. Patent
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`Jun. 12, 2001
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`U.S. Patent
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`Jun. 12, 2001
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`U.S. Patent
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`Jun. 12, 2001
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`US 6,244,401 B1
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`U.S. Patent
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`Jun. 12, 2001
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`US 6,244,401 B1
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`U.S. Patent
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`Jun. 12, 2001
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`U.S. Patent
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`Jun. 12, 2001
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`US 6,244,401 B1
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`U.S. Patent
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`Jun. 12, 2001
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`US 6,244,401 B1
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`
`

`
`1
`FORCE TRANSMITTING APPARATUS
`
`BACKGROUND OF THE INVENTION
`The invention relates to a torque-transmitting apparatus
`with a fluid-operated torque coupler such as, e.g., a fluid
`coupling or a hydrodynamic torque converter, with at least
`one housing that can be connected to a driving shaft of a
`prime mover. The housing contains at least one impeller
`pump receiving torque from the housing and a turbine that
`is connected to the input shaft, such as a transmission shaft,
`of a power train to be driven. Also, if applicable, the housing
`contains at least one stator arranged between the pump and
`the turbine. Further, at least one damper is arranged in the
`power flow between the turbine and a rotary output element
`of the device. The damper has an input member constrained
`to rotate together with the turbine and an output member
`connected to the rotary output element. The input member
`and the output member are rotatable relative to each other at
`least against the opposition of a restoring force furnished by
`energy-storing devices arranged between them.
`Torque-transmitting apparatuses of this kind have been
`proposed, e.g., in DE-OS 195 14411. To allow rotational
`displacement of the input and output members relative to
`each other, it is customary for torque-transmitting appara
`tuses of this kind to be equipped with a hub that has a
`toothed internal profile establishing a positive engagement
`with the transmission shaft and also a toothed external
`profile which mates with a further component, normally a
`further hub that carries the turbine and has a toothed internal
`profile, with play between the flanks of the mating teeth.
`When a lockup clutch is added that is activated by an axial
`control piston, there needs to be a corresponding axial space
`to allow for the axial travel of the hub containing the two
`toothed profiles. The manufacture of hubs of this kind is
`complex and therefore expensive. Furthermore, due to the
`required axial dimension, longer transmission shafts will be
`needed. Added to this is the difficulty of connecting bulky
`hub components with the filigreed construction of the tur
`bine shell. Also, dampers that extend far in the radial
`direction have a tendency to wobble. If in an attempt to solve
`these problems, the damper is axially docked to the turbine
`along two or more perimeters of different radii, this will
`cause undesirable stresses and frictional losses in the
`damper.
`
`OBJECTS OF THE INVENTION
`It is therefore an object of the present invention to
`improve the design of a torque-transmitting apparatus in a
`manner that allows a stress-free accommodation of the
`damper as well as economical and technical improvements
`in the manufacturing process for torque-transmitting appa
`ratuses of this kind. According to a further object of the
`invention, the device is to be manufacturable in such a
`manner that a modular assembly without time-consuming
`fastening operations can be performed during final assem
`bly. Also required of the torque-transmitting apparatus are
`the capabilities to transfer torque of high magnitude and to
`attenuate rotational perturbations over a broad RPM range.
`Besides, the unit is to meet the objectives that it will
`minimize wear and prolong the useful life of the overall
`system of which it is a part.
`SUMMARY OF THE INVENTION
`The invention is embodied in a torque-transmitting appa
`ratus of the kind that has a fluid-operated torque coupler
`such as a hydrodynamic torque converter or a similar device
`comprising
`
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`US 6,244,401 B1
`
`2
`at least one housing that can be connected to a driving
`shaft of a prime mover,
`at least one pump that is arranged inside of and driven by
`the housing,
`a turbine that is connected to and drives the input shaft of
`a power train such as a transmission shaft and also, if
`applicable,
`at least one stator arranged between the pump and the
`turbine, and further
`at least one damper arranged in the torque-flow path
`between the turbine and a rotary output element of the
`apparatus, with an input member of the damper being
`constrained to rotate together with the turbine and an
`output member of the damper being connected to the
`rotary output element, the input member and the output
`member being at least rotatable relative to each other at
`least against the opposition of the restoring force
`exerted by energy-storing devices arranged between
`them.
`In accordance with one presently preferred embodiment
`of the improved torque-transmitting apparatus, the damper
`at its outside perimeter is directly or indirectly connected to
`the turbine through a positive rotational constraint. This
`connection may be free of play relative to coaxial rotational
`displacements but may allow an axial displacement of the
`turbine and the input member of the damper relative to each
`other. For example, the connection may be axially displace
`able by means of an axial plug-in connection with the
`damper rigidly attached to a hub. The problem can further be
`solved through a torque-transmitting apparatus with a
`damper whose connection to the turbine shell or turbine, or
`to the hub, is rotationally fixed both along an inside and
`outside perimeter, while in the axial direction the connection
`is fixed only along one perimeter, either on the hub or on the
`turbine shell, so that axial stresses are relieved by an axial
`displacement at the axially nonrestrained connection.
`In accordance with a further inventive concept, there may
`also be an axially and rotationally fixed connection at the
`outside perimeter of the damper in which case, in order to
`prevent stresses in the damper, the inside perimeter of the
`damper may be designed to be axially displaceable, e.g., in
`an arrangement where the damper, by means of a positive
`circumferential coupling such as a toothed profile, engages
`a complementary profile on the hub. In addition, the profile
`on the hub may be axially fixed but rotatable on a comple
`mentary profile of the turbine hub on which the turbine is
`seated, with the amount of rotational play designed to be at
`least equal to the working range, i.e., the effective angular
`range, of the damper. The play in the form-fitting engage
`ment between the turbine hub and the hub may also be
`obtained through additional devices such as window-like
`openings that are distributed over the circumference of the
`hub and are engaged with angular play by a corresponding
`series of axially directed projections on the turbine hub.
`With particular advantage, the connection between the
`turbine and the input member of the damper is accomplished
`through welding processes such as laser welding, impulse
`welding, or resistance welding, in which case the damper
`can be centered on the hub by means of a disk-shaped part
`that holds the energy-storing devices, or on the turbine shell,
`e.g., by providing the turbine shell with a series of projec
`tions that are distributed over the circumference and that
`may also serve as locating references for the weld.
`It is advantageous for the torque-transmitting apparatus to
`be provided with a lockup clutch arranged in the torque-flow
`path between the driving shaft and the damper, in which case
`it has proved to be beneficial if the lockup clutch, by means
`
`Valeo Exhibit 1015, pg. 13
`
`

`
`3
`of friction linings or laminar disks, establishes a positive
`engagement with a housing surface and transfers the torque
`to be transmitted directly to the input member of the damper.
`Thus, when the lockup clutch is engaged, the torque con
`verter is bypassed and the torque to be transmitted is
`introduced directly into the damper and from there to the
`rotary output element and subsequently to the transmission
`shaft. When the lockup clutch is disengaged, the turbine will
`impart the torque that has been converted—in most cases
`amplified through the effect of the stator—to the input
`member of the damper from where the torque will follow the
`same path as has been previously described.
`The clutch can be engaged and disengaged through an
`axially moveable control piston that is controlled by an
`application of pressure. It is advantageous if the control
`piston defines a plenum chamber which, in the engaged state
`of the lockup clutch, is essentially sealed tight against the
`interior space of the housing (except for insignificant flows
`of pressure medium into the housing that may be provided
`to cool the friction linings) and is energized by a pressure
`medium identical to the converter fluid that is admitted
`through a bore hole, whereby a pressure force is applied to
`the piston in the axial direction towards the turbine. Accord
`ing to the invention, this axial displacement is compensated
`by allowing an axial displacement of the axial plug-in
`connection. Another possibility for controlling the piston is
`to apply an over pressure to the control piston, in which case
`the piston will seal off the chamber when the clutch is open;
`and when the pressure in the chamber is reduced, the piston
`is pushed to the housing wall by the fluid pressure in the
`torque converter, thereby causing the lockup clutch to
`engage.
`The control piston can be centered on the transmission
`shaft, on a hub holding the housing of the torque converter,
`or on another appropriate part of the apparatus and is
`preferably provided with sealing means at the interface
`surfaces to these components for the purpose of sealing the
`plenum chamber in the same manner as the piston can be
`sealed at its outside perimeter against the housing.
`A further embodiment comprises a form-fitting engage
`ment between the control piston and the housing by means
`of complementary profiles extending in the axial direction,
`in which case the axial profile is formed by alternating ridges
`and grooves in the shape of ring segments that are distrib
`uted over a perimeter where, e.g., the ridges of the control
`piston may engage the grooves in the housing. An advantage
`of such configuration is the direct engagement of the piston
`with the housing so that the piston can transmit torque to the
`friction linings directly and/or through other pressure
`transmitting devices, whereby the use of an enlarged friction
`surface and/or of a larger number of friction surfaces and
`thus a greater transmission torque is made possible.
`For this purpose, there may be one or more carriers of
`friction linings in the form of annular disks or laminar disks
`that can carry friction linings in the outer zones of their
`axially facing surfaces. The friction-lining carriers or lami
`nar disks are axially movable, and the pressure force is
`applied against a ring-shaped pressure plate that is con
`nected with the housing either directly or indirectly, e.g.,
`welded, riveted or attached to a flange that is, in turn,
`connected to the housing. For better cooling fluid
`distribution, the pressure plate can have one or more circles
`of holes.
`It is advantageous to center the friction-lining carrier on
`the housing. For this purpose, the friction-lining carrier can
`be provided with lugs that protrude axially towards the
`housing and are inserted in a shoulder extending in the
`direction away from the friction-lining carrier.
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`US 6,244,401 B1
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`4
`A further advantageous embodiment renders it possible to
`configure the piston itself as the lockup clutch or, more
`precisely, as the friction-lining carrier. For this, the radially
`outer part of the control piston surface that faces axially
`towards the housing carries a ring-shaped friction lining that
`may be provided with an optimized surface finish to achieve
`better cooling. The piston surface may be bent in the axial
`direction towards the turbine, so that the piston may rest in
`form-fitting contact against the housing, which in the respec
`tive surface portion is shaped similar to a cone shell.
`As already described above, the lockup clutch is con
`nected through one of its components to the input member
`of the damper. In one embodiment, the connecting part may
`be the control piston itself in the manner described above, in
`which case the piston may be connected to lateral parts of
`the input member by rivets, weld joints or similar means. A
`further embodiment employs a ring-shaped friction-lining
`carrier that may form an axial plug-in connection by virtue
`of an appropriately shaped lateral portion. In this case the
`friction-lining carrier has a form-fitting engagement with the
`input member of the damper, e.g., by means of internal teeth
`at its inside perimeter and, e.g., an axially oriented profile on
`the lateral part of the input member. The advantages of axial
`plug-in connections in accordance with the invention are
`that they compensate for axial displacements and facilitate
`the manufacturing process by virtue of a modular
`configuration, because systems of this kind can be built by
`plug-in assembly without further resort to fastening under
`takings such as, e.g., welding or riveting, thus allowing the
`use of work stations that are not equipped with the respective
`infrastructure.
`Further advantageous embodiments of axial plug-in con
`nections between components of the damper and compo
`ments of the turbine will be described hereinafter. An advan
`tageous configuration has two components of the two units
`to be connected meeting each other approximately at a right
`angle, i.e., in the form of a radially and an axially extending
`flange, respectively, with the two parts in a form-fitting
`engagement. In this, it may be advantageous to provide the
`radially extending flange with external teeth and the axially
`extending flange with axially oriented teeth.
`It may also be advantageous if a radially extending
`flange-like part has closed cutouts, distributed along a circle
`of smaller radius than the outside perimeter, that are engaged
`by axially directed extremities of the axially extending
`flange-like part.
`A preferred embodiment may be a radially oriented
`flange-like part that, starting at its inside perimeter, follows
`the shape of the turbine shell outwards in the radial direction
`and is attached in this portion, e.g., welded or riveted. From
`there, the flange-like part bends into the radial direction and
`has a toothed profile along its exterior circumference that is
`engaged by the lateral part of the input member of the
`damper. For this purpose, the lateral part at its exterior
`circumference bends into the axial direction and forms the
`axially directed flange-like part that carries, e.g., the axially
`oriented toothed profile.
`A further advantageous embodiment may include a
`flange-like part in the shape of an annular disk that adjoins
`along its inside perimeter the turbine shell and conforms to
`the shape of the turbine shell towards the inside in the radial
`direction, is attached in the shape-conforming portion as
`described above and then curves into the axial direction. The
`profile facing away from the turbine shell in axial direction,
`e.g., a toothed profile, engages in closed recesses distributed
`over the circumference of a radially directed lateral part and
`in this manner forms an axial plug-in connection. To form
`
`Valeo Exhibit 1015, pg. 14
`
`

`
`US 6,244,401 B1
`
`5
`this plug-in connection, it may be necessary for the axially
`directed toothed profile to pass through the output member
`before engaging the input member of the damper, given that
`the output member is interposed axially between the turbine
`and the input member. For this purpose, the output member
`has a circular arrangement of elongated holes matching the
`number of teeth. The angular width of the holes corresponds
`to the maximum angular displacement of the input and
`output members relative to each other so that at the same
`time the elongated holes in combination with the axially
`directed teeth of the axially oriented flange-like part that is
`connected to the turbine form at least one stop for the
`angular displacement of the damper.
`In an advantageous arrangement, the axially extending
`flange-like part can itself be in the form of a hub that carries
`the turbine, the latter being connected to the hub by, e.g.,
`welding or riveting. The hub carrying the turbine, in turn,
`can be seated on a further hub that performs the function of
`the rotary output element and is attached to the transmission
`shaft. The axially extending flange-like part has a profile
`established, e.g., by axially oriented teeth that extend into
`enclosed cutouts corresponding to the number of teeth in the
`flange whereby an axial plug-in connection is formed.
`Depending on the configuration of the damper, it may be
`necessary with this embodiment, too (as described above), to
`provide in the output member an appropriate arrangement of
`elongated holes which,
`in combination with the axially
`directed profile of the axially oriented flange for the axial
`plug-in connection, can function as stops for the relative
`displacement between the input and output members of the
`damper. The output member, being a radial extension of the
`hub that is attached to the transmission shaft, may also be
`configured as a separate flange-like part, in which case the
`flange needs to be centered on the hub and attached through
`a rotationally fixed connection.
`It can further be advantageous if an annular disk in the
`form of a radially extending flange-like part with an exterior
`profile, e.g., an arrangement of external teeth, is centered on
`the hub that carries the turbine. By attachment means such
`as, e.g., rivets, the annular disk is rotationally tied to the
`turbine, and its outward-pointing teeth, mentioned above by
`way of an example, engage a lateral part that is bent in the
`axial direction along the interior perimeter and (also by way
`of example) has a complementary, axially directed toothed
`profile. In this case, too, a connection is established that
`constrains rotational but allows translational displacement
`of the engaged parts relative to each other. The angular
`displacement of the damper may advantageously be defined
`by means of a toothed profile with play between the respec-
`tive tooth flanks of the hub and the annular disk. The
`
`outward-facing profile of the hub may also be engaged by
`the inward-facing profile of the output member, albeit with-
`out play at the flanks, in order to secure the output member
`for rotation with the hub. This has the advantage of saving
`space in the axial direction of the hub, given that the relative
`axial displacement occurring between the damper and the
`turbine as a result of the axial movement of the control
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`piston is already compensated for by the axial plug-in
`connection.
`
`The axial plug-in connection between the damper and the
`turbine in different practical variations may be arranged,
`e.g., at a radial distance beyond the energy-storing devices,
`at an intermediate radius between the storage devices in the
`case of at least two damper stages, or inside the radial
`distance of the storage devices.
`Other embodiments of the invention concern the advan-
`
`tageous design of the damper. The damper may be of the
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`single-stage or multi-stage type. A dual-stage damper may
`be configured in such a way that the damper stages can
`function in a serial or parallel mode, with the additional
`possibility of different limits of rotation so that, e.g., in a
`serial arrangement of the damper stages the relative rotation
`of one stage is stopped before the other stage, e.g., for the
`purpose of achieving particular damping characteristics.
`In connection with the damper, it is also advantageous to
`combine different energy-storing devices, e.g., by selecting
`arc-shaped springs in a radially exterior damper stage, and
`short, stiff spring elements for use in smaller-diameter areas
`so that, e.g., a damper characteristic can be achieved that
`provides a high amount of energy to compensate for both
`large-amplitude rotational irregularities at low RPM and
`small-amplitude rotational irregularities at high RPM. In this
`kind of an arrangement,
`the arc-shaped springs in the
`radially exterior area may be pre-bent
`to their working
`diameter and are retained radially by a chamber that is
`formed by at least one lateral part or by other components of
`the damper or of the torque-transmitting apparatus, e.g., by
`the wall of the housing. In addition, there may be wear-
`reducing components such as wear-protection shells inter-
`posed between the arc-shaped springs and the chamber, with
`the characteristic of the arc-shaped spring being determined
`by all of the aforementioned factors.
`It can be advantageous to provide the individual damper
`stages with displacement properties that depend on the
`direction from which the torque is introduced. Thus, the
`damper system may be designed to function in two stages in
`the “pull” mode and in one stage in the “push” mode. In this
`manner, the damper characteristic may be adapted to the
`possibility of hard transient peaks in the torque-flow that are
`introduced from the “push” side, i.e., from the input shaft of
`the transmission, in which case, e.g., the soft damper stage
`is bypassed completely and the firm damper stage is effec-
`tive instantly. The bypass can accomplished by means of
`limit stops that block angular displacement against the drive
`direction in the input and output members of the damper
`stage that is inactive in the push mode.
`It is advantageous to accommodate the storage devices in
`disk-shaped parts that have dimensionally matched recesses
`into which the storage devices are fitted and which may at
`their ends have force-introduction elements facing against
`the direction of the restoring force. The force-introduction
`elements retain and thereby compress the storage devices
`when the input and output members are displaced in relation
`to each other. The disk-shaped parts forming the input and
`output members may be arranged in such a manner that
`either the input or output member is formed by two mutually
`connected lateral parts, while the other of the two members
`is formed by a corresponding disk-shaped, flange-like part
`arranged between the two lateral parts. A further embodi-
`ment that brings cost advantages has two disk-shaped parts,
`one representing a lateral part serving as input member and
`the other representing a lateral part serving as output mem-
`ber. In two-stage dampers, it can further be cost-effective to
`use a common disk-shaped part working with both damper
`stages.
`Further in the interest of optimizing cost, the disk-shaped
`parts may take on additional functions. For example, as
`mentioned already, one or more disk-shaped parts may form
`a chamber for the energy storing devices, or they may
`contain the axial plug-in connection between the damper and
`the turbine, and/or they may perform other functions.
`It is further advantageous for cost-optimization if disk-
`shaped parts and different other components are made of one
`piece. Thus, e.g., the output member of the damper together
`
`Valeo Exhibit 1015, pg. ‘I5
`
`Valeo Exhibit 1015, pg. 15
`
`

`
`7
`with the rotary output element (e.g., the hub that is arranged
`on the transmission shaft), or the output member together
`with the hub that carries the turbine, may be made of one
`piece.
`An advantageous and cost-effective embodiment of
`means for limiting the extent of angular displacement avoids
`the need for special stops. For this purpose, a circular
`arrangement of elongated holes may be provided on at least
`one disk-shaped part, where the fasteners (e.g., rivets) that
`are in any case already provided pass through the holes and
`are held on the opposite side by another disk-shaped part
`and/or by means of a sheet metal holder. The angular width
`of the elongated holes is preferably selected so that the
`extent of relative angular displacement between the input
`member and the output member is limited by the ends of the
`elongated holes stopping the shafts of the fasteners.
`It is advantageous to provide displacement-limiting stops
`insofar as a damper or either some or all of the damper stages
`can be bypassed, so that the damperor the damper stages can
`be protected from wear. This may apply particularly in the
`case of wear-prone versions with storage devices that, e.g.,
`contain arc-shaped springs, permit large angular
`displacements, and/or are exposed to strong shock loads. To
`guard against premature failure, it is advantageous if ini
`tially one damper stage is totally bypassed by means of
`displacement-limiting stops, while the second stage is either
`not bypassed at all or only at a later point. When a damper
`or a damper stage reaches its limit stop, the torque that
`previously entered into the energy-storing device is trans
`mitted through the stop directly to the output member of the
`bypassed damper or damper stage. It may also be advanta
`geous to provide different angular displacement limits in the
`damper device and its damper stages depending on the
`direction of the torque, i.e., whether the torque works in the
`pull or push direction, respectively. Thus, it may be
`advantageous, for example, to provide limit stops in such a
`manner that a damper stage is entirely bypassed in the
`costing mode. Likewise, there may be advantages to a
`configuration in which, e.g., one damper stage works only in
`the coasting direction while the other stage works only in the
`pull direction.
`The novel features that are considered as characteristic of
`the invention are set forth in particular in the appended
`claims. The improved apparatus itself, however, both as to
`its construction and its mode of operation, together with
`additional features and advantages thereof, will be best
`understood upon perusal of the following detailed descrip
`tion of certain presently preferred specific embodiments
`with reference to the accompanying drawing.
`BRIEF DESCRIPTION OF THE DRAWINGS
`FIG. 1 is a fragmentary sectional view of a novel torque
`transmitting apparatus with a two-stage damper.
`FIG. 2 is a fragmentary sectional view of a further
`embodiment of a torque-transmitting apparatus with an axial
`plugin connection located at a radial position between the
`energy-storing devices of two damper stages.
`FIG. 3 is a fragmentary sectional view of an embodiment
`of the invention with axially directed projections formed on
`the hub.
`FIG. 4 is a partial view of a disk-shaped part of a damper.
`FIG. 5 is a fragmentary sectional view of an embodiment
`of a damper.
`FIG. 6 represents a fragmentary view of another embodi
`ment of a damper.
`FIG. 7 is a fragmentary axial sectional view of an embodi
`ment of a torque-transmitting apparatus with a single-stage
`damper.
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`US 6,244,401 B1
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`8
`FIG. 8 is a fragmentary axial sectional view of an embodi
`ment of a torque-transmitting apparatus with a two-stage
`damper and a two-part hub.
`FIGS. 9–12 are fragmentary sectional views of further
`embodiments of two-part turbine dampers.
`FIG. 13 represents an embodiment with a damper docked
`fixedly to the turbine shell.
`FIG. 14 represents a modified version of the damper of the
`embodiment of FIG. 13.
`FIG. 15 represents a detail of an embodiment comprising
`a damper that is docked fixedly to the turbine shell.
`FIG. 16 represents an embodiment of a torque
`transmitting apparatus comprising a damper that is docked
`fixedly to the turbine shell.
`FIG. 17 represents a hub of the embodiment of FIG. 16.
`DETAILED DESCRIPTION OF THE
`INVENTION
`The torque-transmitting apparatus