Rotating multi-mode clutch module with stationary actuator

A multi-mode clutch module for connecting two components rotating relative to each other may include an outer race, an inner race and pawls coupled to the inner race and movable between engagement to and disengagement from the outer race to alternately lock and unlock the races for relative rotation in one or both directions. A cam ring and a plurality of cams extending therefrom are coupled to the inner race for rotation therewith and for axial movement parallel to a rotational axis of the races. A shift ring is operatively connected between the cam ring and a shift drum such that rotation of the shift drum caused by a stationary actuator causes translation of the shift ring to move the cam ring and cams so the cams engage the pawls to move the pawls between their locked and unlocked positions.

TECHNICAL FIELD

This disclosure relates generally to clutches, and in particular to clutches having multiple modes of engagement between two element rotating relative to each other for selectively locking the elements against relative rotation with respect to each other in one or both directions.

BACKGROUND

An automotive vehicle typically includes an internal combustion engine containing a rotary crankshaft configured to transfer motive power from the engine through a driveshaft to turn the wheels. A transmission is interposed between engine and driveshaft components to selectively control torque and speed ratios between the crankshaft and driveshaft. In a manually operated transmission, a corresponding manually operated clutch may be interposed between the engine and transmission to selectively engage and disengage the crankshaft from the driveshaft to facilitate manual shifting among available transmission gear ratios. On the other hand, if the transmission is automatic, the transmission will normally include an internal plurality of automatically actuated clutch units adapted to dynamically shift among variously available gear ratios without requiring driver intervention. Pluralities of such clutch units, also called clutch modules, are incorporated within such transmissions to facilitate the automatic gear ratio changes.

Multi-mode clutch modules (MMCMs) have become an important part of transmission designs in order to meet government fuel efficiency standards. The MMCMs can take the place of friction plates that are currently used in many applications. This is accomplished using two sets of pawls (a forward pawl set and a reverse pawl set) that are moved by an actuator of the MMCM. The forward pawl set will prevent rotation in one direction (clockwise will be used for clarification, but the direction of the rotation depends on the transmission design) and the reverse pawl set prevents rotation in the opposite direction (i.e., counterclockwise as used herein). The pawls are designed to be movable between engaged and disengaged positions to alternately lock and unlock an inner race relative to an outer race or notch ring of the MMCM. The forward and reverse pawl sets can be actuated in concert or independently to provide up to four modes for the MMCM: locked in both directions, one-way locking in the clockwise direction, one-way locking in the counterclockwise direction, and unlocked to allow free rotation in both directions.

In some applications, a clutch is used to connect two members that are both rotating. In many of these applications, however, it is not practical to have an actuator that rotates with the inner race or the outer race. Rotation of the actuator along with the race on which it is mounted can cause wires of the actuator to twist or create excessive drag on the MMCM that can reduce the efficiency of the vehicle or other machine in which the MMCM is implemented.

SUMMARY OF THE DISCLOSURE

In one aspect of the present disclosure, a clutch module for coupling a first rotating component and a second rotating component of a machine to each other is disclosed. The clutch module includes an outer race configured to be coupled to and to rotate with the first rotating component, wherein the outer race is rotatable in both directions about a clutch rotational axis, an inner race configured to be coupled to and to rotate with the second rotating component, wherein the inner race is concentrically aligned with the outer race and rotatable in both directions relative to the outer race about the clutch rotational axis, and a first pawl operatively coupled to one of the inner race and the outer race to rotate therewith and to move between a first pawl locked position where the first pawl engages to prevent rotation of the inner race relative to the outer race in a first direction and a first pawl unlocked position where the first pawl is disengaged to allow rotation of the inner race relative to the outer race in the first direction. The clutch module may further include a first cam operatively coupled to the one of the inner race and the outer race to rotate therewith and to translate relative to the inner race and the outer race parallel to the clutch rotational axis, a shift ring operatively coupled to a stationary structure of the machine and constrained to translate parallel to the clutch rotational axis, and operatively coupled to the first cam so that translation of the shift ring causes translation of the first cam and so that the first cam can rotate about the clutch rotational axis relative to the shift ring, and a shift drum operatively coupled to the stationary structure of the machine and constrained to rotate about a shift drum axis that is parallel to the clutch rotational axis. The shift drum may be operatively coupled to the shift ring so that rotation of the shift drum causes the shift ring and the first cam to translate. The shift drum is rotatable to a first angular position wherein the first cam is disengaged from the first pawl and the first pawl is in the first pawl locked position, and to a second angular position wherein the first cam engages the first pawl to move the first pawl to the first pawl unlocked position.

In another aspect of the present disclosure, a clutch module for coupling a first rotating component and a second rotating component of a machine to each other. The clutch module may include an outer race configured to be coupled to and to rotate with the first rotating component, wherein the outer race is rotatable in both directions about a clutch rotational axis, an inner race configured to be coupled to and to rotate with the second rotating component, wherein the inner race is concentrically aligned with the outer race and rotatable in both directions relative to the outer race about the clutch rotational axis, a first pawl operatively coupled to one of the inner race and the outer race to rotate therewith and to move between a first pawl locked position where the first pawl engages to prevent rotation of the inner race relative to the outer race in a first direction and a first pawl unlocked position where the first pawl is disengaged to allow rotation of the inner race relative to the outer race in the first direction, and a second pawl operatively coupled to the one of the inner race and the outer race to rotate therewith and to move between a second pawl locked position where the second pawl engages to prevent rotation of the inner race relative to the outer race in a second direction and a second pawl unlocked position where the second pawl is disengaged to allow rotation of the inner race relative to the outer race in the second direction. The clutch module may further include a first cam operatively coupled to the one of the inner race and the outer race to rotate therewith and to translate relative to the inner race and the outer race parallel to the clutch rotational axis, a cam ring having an annular shape and oriented concentrically with the outer race and the inner race about the clutch rotational axis, wherein the first cam extends axially from the cam ring so that the cam ring rotates with the one of the inner race and the outer race and the cam ring and the first cam translate together relative to the inner race and the outer race parallel to the clutch rotational axis, a shift ring operatively coupled to a stationary structure of the machine and constrained to translate parallel to the clutch rotational axis, and operatively coupled to the cam ring so that translation of the shift ring causes translation of the cam ring and the first cam, and so that the cam ring is rotatable about the clutch rotational axis relative to the shift ring, and a shift drum operatively coupled to the stationary structure of the machine and constrained to rotate about a shift drum axis that is parallel to the clutch rotational axis. The shift drum may be operatively coupled to the shift ring so that rotation of the shift drum causes the shift ring, the cam ring and the first cam to translate. The shift drum is rotatable to a first angular position wherein the first cam is disengaged from the first pawl and the first pawl is in the first pawl locked position and disengaged from the second pawl and the second pawl is in the second pawl locked position, and to a second angular position wherein the first cam engages the first pawl to move the first pawl to the first pawl unlocked position and engages the second pawl to move the second pawl to the second pawl unlocked position.

Additional aspects are defined by the claims of this patent.

DETAILED DESCRIPTION

FIGS. 1 and 2illustrate an embodiment of a MMCM10that can be used to connect a first rotating component (not shown) to a second rotating component (not shown) in a machine, such as a transmission of a vehicle. The MMCM10may include an outer race or notch ring12to which the first rotating component is connected, and an inner race14to which the second rotating component is connected. The notch ring12and the inner race14are concentrically aligned along a clutch rotational axis16that is also common to the rotating components when the MMCM10is installed. The inner race14may be disposed between and connected for rotation with a pair of side plates18(one shown inFIGS. 1 and 2) that maintain the inner race14in an approximately fixed axial location relative to the notch ring12as the second rotating component drives the inner race14and the side plates18.

The locking and unlocking modes of the MMCM10may be controlled by a plurality of pawls20,22(FIG. 2) and corresponding cams24. In the illustrated embodiment, the pawls20,22are pivotally mounted between the side plates18for rotation about pawl axes (not identified) that are parallel to the clutch rotational axis16of the MMCM10. The first pawls20may selectively rotate into engagement with the notch ring12to prevent the inner race14and the second rotating component from rotating in a first direction (clockwise as shown inFIG. 2) relative to the notch ring12and the first rotating component. Similarly, the second pawls22may selectively rotate into engagement with the notch ring12to prevent inner race14and the second rotating component from rotating in a second direction (counterclockwise as shown inFIG. 2) relative to the notch ring12and the first rotating component. Each of the pawls20,22may be biased toward engagement with the notch ring12by a corresponding pawl spring26compressed between the pawl20,22and a spring notch28along an outer edge30of the inner race14.

Each first pawl20may be paired with a corresponding one of the second pawls22so that the paired pawls20,22may both be acted upon by one of the cams24to rotate between their engaged/locked positions and their disengaged/unlocked positions. The cams24may be disposed within cam notches32,34in the inner race outer edge30and corresponding cam recesses36in side plate inner edges38proximate the corresponding pawls20,22. The cams24may be connected for coordinated movement by a cam ring40disposed on one side of the MMCM10and outside one of the side plates18. The cam notches32,34and/or the cam recesses36may engage the cams24so that the cams24and the cam ring40rotate with the inner race14, the side plates18and the pawls20,22as a single inner race assembly (not numbered) relative to the notch ring12. At the same time, the cams24are slidable within the cam notches32,34and the cam recesses36parallel to the clutch rotational axis16of the MMCM10.

Those skilled in the art will understand that the pivoting pawls20,22of the illustrated embodiment are exemplary. Pawls coupled to the inner race14and movable in radial or axial translation, rotation or other complex motions relative to the inner race14and into and out of engagement with the notch ring12are contemplated by the inventor as having use in MMCMs10in accordance with the present disclosure. Moreover, in other alternative embodiments, the pawls20,22may be mounted on the outer race12and movable into and out of engagement with the inner race14to alternately lock the races12,14for rotation together and unlock the races12,14for relative rotation with respect to each other. The mechanisms for moving the pawls20,22disclosed herein may be modified accordingly for control of the pawls20,22when mounted on the outer race12.

The outer race or notch ring12is shown in greater detail inFIG. 3. The notch ring12may include an annular outer ring42and an annular inner ring44extending radially inwardly from an inward surface46of the outer ring42. The inner ring44may have a narrower width that the outer ring42so that the inner ring44may be captured between the side plates18when the inner race assembly is assembled to maintain the notch ring12and the inner race14in an approximately constant position along the clutch rotational axis16of the MMCM10. The notch ring12may further include a plurality of outer teeth48extending radially outwardly from and circumferentially spaced about a radially outward surface50of the outer ring42. The outer teeth48may be arranged to mesh with and engage corresponding teeth or other structures of the first rotating component so that the notch ring12and the component rotate together. A plurality of inner teeth52may extend radially inwardly from and be circumferentially spaced about an inward surface54of the inner ring44. The inner teeth52will be engaged by the pawls20,22to lock the notch ring12and the inner race14against relative rotation when the pawls20,22are in their locked positions as will be discussed further below.

The inner race14as described above is illustrated in greater detail inFIG. 4. The inner race14is a generally circular plate having an inner race central opening56aligned along the clutch rotational axis16and configured for connection of the second rotating component. The cam notches32are shaped to slidably receive the corresponding cams24therein. The cam notches34have a different configuration that allows the cam notches34to also receive a detent block58therein. As shown inFIG. 5, the detent block58may include a detent member60extending outwardly therefrom that will engage recesses in a corresponding one of the cams24to ensure that the cams24are correctly positioned in each of the lock modes of the MMCM10as will be illustrated and described further below. The cam notches34and the detent blocks58are sized so that the detent blocks58may be press fit into the cam notches34and retained in place as the cams24move axially within the cam notches34. Returning toFIG. 4, the inner race14may further include a plurality of locking rod openings62circumferentially spaced about the inner race14that may receive corresponding locking rods (not shown) that will constrain the inner race14and the side plates18to rotate together about the clutch rotational axis16.

As shown inFIG. 6, each side plate18is a generally annular plate having a side plate inner edge38with the cam recesses36defined there in. The cam recesses36are circumferentially spaced about the side plate inner edge38to align with corresponding ones of the cam notches32,34when the inner race assembly is assembled. The side plates18have a plurality of locking rod openings64circumferentially spaced about the side plates18to correspond to the locking rod openings62of the inner race14. During assembly, locking rods or other alignment mechanisms may be inserted through the locking rod openings62,64to align the cam notches32,34with the cam recesses36, and to constrain the inner race14and the side plates18to rotate together about the clutch rotational axis16. Each of the side plates18further includes a plurality of pawl arm openings66circumferentially spaced about the side plates18proximate a side plate outer edge68. The pawl arm openings66may be sized to receive corresponding pivot arms of the pawls20,22so that the pawls20,22are suspended between the side plates18and are pivotable relative to the side plates18and the inner race14between their locked and unlocked positions.

The inner race assembly may capture the notch ring12in a manner that allows relative rotation of the notch ring12and the inner race14while maintaining their relative positions along the clutch rotational axis16. The side plates18have an outer diameter that is slightly less than an inner diameter of the outer ring42so that the side plates18fit within the outer ring42without rubbing against the inward surface46. The outer diameter of the side plates18is greater than an inner diameter of the inner ring inward surface54so that the inner ring44and the inner teeth52are captured between the side plates18. Additionally, the inner race14may have a thickness that is greater a thickness of the inner ring44and the inner teeth52so that the side plates18are spaced apart sufficiently so that the inner ring44is not pinched between side plates18and friction between the notch ring12and the inner race14and resistance to their relative rotation is minimized. The illustrated embodiment is exemplary of relative sizes of the notch ring12, the inner race14and the side plates18. Alternative configurations of the MMCM10are contemplated where the notch ring12and the inner race14are concentric and axially aligned with the pawls20,22rotating with the inner race14and being movable into and out of engagement with the notch ring12.

FIG. 7illustrates an embodiment of the pawls20,22of the inner race assembly. Each of the pawls20,22may have a similar configuration, and be oriented as shown inFIG. 2during assembly to ensure that the pawls20lock the inner race14against rotation relative to the notch ring12in one direction, and the pawls20to lock the inner race14against rotation relative to the notch ring12in the opposite direction. The pawls20,22may have a pawl body70having a pair of pawl pivot arms72,74extending outwardly from the pawl body70in opposite directions. The pawl pivot arms72,74may be generally cylindrical and sized to be received within the pawl arm openings66of the side plates18so that the pawls20,22can pivot about an axis that is approximately parallel to the clutch rotational axis16of the MMCM10. One end of the pawl body70may terminate in a tooth engagement tip76that will be disposed proximate the inward surface54of the notch ring12and engage one of the inner teeth52when the pawl20,22is rotated to its locked position. Opposite the tooth engagement tip76, a camming end78may extend outwardly from the pawl body70and be configured to be engaged by the corresponding cam24to rotate the pawls20,22between the locked and unlocked positions.

The cams24and the cam ring40are illustrated in greater detail inFIG. 8. As will be discussed further below, the cams24extend from a surface80of the cam ring40proximate a cam ring inner edge82so that an area proximate a cam ring outer edge84is free of obstruction. Each of the cams24includes a camming surface86that will engage the camming ends78of the corresponding pawls20,22to control the rotational position of the pawls20,22is the cams24slide within the cam notches32,34. The cams24may further include detent recesses88in inward surfaces90that will face the detent blocks58when the inner race assembly is assembled and receive the detent members60when the cams24are in discrete positions placing the pawls20,22in corresponding ones of the locking modes of the MMCM10.

Returning toFIG. 1, a mode shift execution assembly for the MMCM10may include a shift ring100at least partially encircling the cam ring40, a shift drum102operatively coupled to the shift ring100to cause the shift ring100to move parallel to the clutch rotational axis16when the shift drum102rotates, and an actuator104operatively coupled to the shift drum102to apply torque to the shift drum102and cause the shift drum102to rotate in response to actuator control signals indicating a direction and speed of rotation. During rotation of the rotating components connected by the MMCM10, the clutch rotational axis16, and correspondingly the notch ring12and the inner race14, may remain in a substantially fixed position relative to the structure of the machine in which the MMCM10is implemented, with the notch ring12and the inner race14rotating about the clutch rotational axis16with the corresponding rotating components. The mode shift execution assembly may also be constrained to a substantially fixed position by connecting the components to a mounting plate106that is connected to a frame, housing or other stationary component of the machine.

The shift ring100is shown in greater detail inFIG. 9. The shift ring100may include a circular or semi-circular cam ring engaging portion108that wraps partially around the cam ring40when the MMCM10is assembled. The cam ring engaging portion108may have an annular groove110defined in a shift ring inner surface112. An inner diameter of the inner surface112may be less than an outer diameter of the cam ring40, and the annular groove110may be deep enough into the cam ring engaging portion108so that the cam ring40is disposed within the annular groove110with clearance for the cam ring outer edge84. At the same time, the inner diameter of the inner surface112may be large enough to provide clearance between the inner surface112and the cams24extending from the cam ring40. A width of the annular groove110may be greater than a thickness of the cam ring40to provide an air gap between the cam ring40and the annular groove110when the MMCM10is in position for one of the locking modes as will be described more fully below.

The shift ring100may further include a mounting portion114extending from the cam ring engaging portion108and configured to operatively connect the shift ring100to the mounting plate106. In the illustrated embodiment, the mounting portion114includes two guide rod openings116for slidably receiving guide rods118(FIG. 1) extending from the mounting plate106that will constrain the shift ring100to linear movement parallel to the clutch rotational axis16of the MMCM10. The shift ring100further includes a shift ring cam follower120extending from the mounting portion114that will be operatively coupled to the shift drum102to move the shift ring100and the cam ring40between the discrete locking positions.

An embodiment of the shift drum102is shown inFIG. 10. The shift drum102has a cylindrical shape and is rotationally mounted on the mounting plate106for rotation about an axis that is parallel to the clutch rotational axis16. An outer surface122of the shift drum102may define a shift drum camming groove124extending circumferentially around the shift drum102. The shift drum camming groove124may have a helical shape so that the camming groove124progresses axially along the outer surface122as the camming groove124extends around the shift drum102. The camming groove124may have the shift ring cam follower120disposed therein so that the shift ring100and the cam ring40will move linearly parallel to the clutch rotational axis16when the actuator104rotates the shift drum102and the camming groove124forces the shift ring100to slide along the guide rods118. The camming groove124may have a constant pitch so that its axial position and the axial position of the shift ring100and the cam ring40change at a fixed rate as the shift drum102is rotated by the actuator104.

The actuator104may be any appropriate actuator that produces rotary motion when a signal is transmitted thereto. For example, the actuator104may be a hydraulic actuator, a solenoid actuator, a stepper motor or any other device that can rotate between discrete angular positions and cause the shift drum102to rotate. The actuator104may be operatively connected to a control device that can output control signals, variable current, variable fluid flow or other inputs that can cause the actuator104to rotate between predetermined discrete angular positions that will cause the cams24to move to the discrete positions of the locking modes of the MMCM10. Of course, the actuator104could be a linear actuator or other type of actuator having a non-rotation output movement so long as the actuator is actuatable between discrete positions, fixed relative to the frame or housing of the machine, and operatively connected to the shift drum102by lever arms, a linkage assembly or other appropriate connection mechanism in a manner that converts the output movement of the actuator104into torque on and rotation of the shift drum102between the discrete angular positions.

The operation of the MMCM10will be illustrated and described with reference toFIGS. 11 and 12. InFIG. 11, the MMCM10is illustrated in a two-way locked mode wherein the notch ring12and the inner race14are locked for rotation together in the clockwise and the counterclockwise directions. The shift ring100and the cam ring40are positioned axially away from the notch ring12and the inner race14so that the camming surfaces86of the cams24are not engaging the camming ends78of the pawls20,22. Without the cams24displacing the camming ends78, the pawls20,22are biased toward their locked positions with the tooth engagement tips76positioned to engage the inner teeth52of the notch ring12. The detent members60of the detent blocks58are disposed within the detent recesses88of the cams24corresponding to the two-way locked mode of the MMCM10to ensure that the cams24are correctly positioned. At the same time, the shift drum102has been rotated to a first prescribed angular position for the two-way locked mode by the actuator104so that the portion of the inner surface112defining the annular groove110in the cam ring engaging portion108of the shift ring100is spaced from the cam ring40so that the cam ring40is free to rotate with the inner race14without drag from friction between the cam ring40and the inner surface112.

When the MMCM10is to be transitioned to a two-way unlocked mode shown inFIG. 12, appropriate signals are transmitted to the actuator104to actuate and rotate the shift drum102to a second prescribed angular position for the two-way unlocked mode. As the actuator104rotates the shift drum102toward the second prescribed angular position, the point of engagement between the camming groove124and the shift ring cam follower120moves axially toward the notch ring12and the inner race14. The engagement between the camming groove124and the shift ring cam follower120causes the shift ring100to slide axially along the guide rods118. The annular groove110of the shift ring100will first move into engagement with the cam ring40, and then push the cam ring40and the cams24so that the detent recesses88for the two-way lock mode move past the detent member60and the camming surfaces86of the cams24move into engagement with the camming ends78of the pawls20,22. The camming surfaces86cause the pawls20,22to rotate against the biasing forces of the pawl springs26and out of engagement with the inner teeth52of the notch ring12. As the shift ring100and the cam ring40continue to move axially, the detent recesses88corresponding to the two-way unlocked mode of the MMCM10will approach and receive the corresponding detent members60and the cams24will snap in place in their two-way unlocked position with the detent members60disposed in the detent recesses88for proper alignment. The actuator104will eventually stop the shift drum102at the second predetermined angular position shown inFIG. 12with the inner surface112defining the annular groove110spaced from the cam ring40for rotation of the cam ring40without drag from friction. When the MMCM10returns to the two-way locked mode ofFIG. 11, the actuator104rotates the shift drum102in the opposite direction toward the first prescribed angular position to cause the cams24to disengage from the pawls20,22.

FIGS. 13 and 14illustrate an alternative embodiment of an MMCM130having a modified mode shift execution assembly. Referring toFIG. 13, the notch ring12, the inner race14and the other components of the inner race assembly may be configured in a similar manner as described above. The mode shift execution assembly of the MMCM130may include a shift ring132encircling the cam ring40. The shift ring132may be operatively connected to the frame or housing of the machine so that the shift ring132is concentric with the notch ring12and the inner race14on the clutch rotational axis16and can translate parallel to the clutch rotational axis16, while also being constrained to prevent rotation about the clutch rotational axis16. A shift drum134may also be concentric with the notch ring12, the inner race14and the shift ring132about the clutch rotational axis16and may include a helical camming groove136similar to the camming groove124of the shift drum102as described above.

Referring to the cross-sectional view ofFIG. 14, the shift ring132may be formed from multiple components138,140that are assembled around the cam ring40. In the illustrated embodiment, the components138,140are annular discs that may be disposed on either side of the cam ring40and connected to form the shift ring132and to define an annular groove142surrounding the cam ring40. The annular groove142may have a similar configuration as the annular groove110of the shift ring100, with an inner diameter that is greater than the outer diameter of the cam ring40and a width of the annular groove142may be greater than the thickness of the cam ring40to reduce friction and drag when the cam ring40rotates relative to the shift ring132. The shift ring132further includes a cam follower144extending inwardly into a shift drum opening146in which the shift drum134is disposed, with the cam follower144being received within the camming groove136of the shift drum134. Other arrangements are contemplated for installing the shift ring132on the cam ring40. For example, the annular shift ring132may be divided into two semi-circular half rings that may each be similar to the cam ring engaging portion108of the shift ring100. The half rings may be placed around the cam ring40with their ends connected to form the shift ring132. In a further alternative, the shift ring132may be formed around the cam ring40as a single unitary component by a process such as three dimensional printing. Additional alternatives will be apparent to those skilled in the art and are contemplated by the inventor.

The shift drum134may have a generally similar configuration as the shift drum102and have the helical camming groove136extending around an outer surface148of the shift drum134. The shift drum134have a shift drum opening150centered on the clutch rotational axis16and configured so that the second rotating component of the machine connected to the inner race14may pass there through. The shift drum134may be operatively connected to the frame or housing of the machine so that the shift drum134is centered on the clutch rotational axis16and constrained to a fixed axial position relative to the notch ring12and the inner race14, while also being free to rotate about the clutch rotational axis16. The shift drum134may have an actuator (not shown), such as the actuator104, that is mounted in a stationary position relative to the frame or housing of the machine and operatively connected to the shift drum134to cause the shift drum134to rotate between prescribed angular positions corresponding to the available locking modes of the MMCM130. The actuator may be directly coupled to the shift drum134, such as to the outer surface148, or indirectly coupled thereto by an intermediate linkage, gears or other mechanism that can convert the rotation of the actuator into rotation of the shift drum134.

The operation of the MMCM130to shift between the available locking modes is generally similar to the process described above. The actuator is actuated to rotate the shift drum134, and the engagement between the camming groove136and the cam follower144causes the shift ring132and the cam ring40to translate parallel to the clutch rotational axis16between the locking mode positions. The MMCM130is illustrated in a two-way unlocked mode similar to that illustrated inFIG. 12and described in the accompanying text.FIG. 14more clearly illustrates the interaction between the detent members60and the detent recesses88of the cams24. The rightmost detent recesses88have received the detent members60therein to align the cams24in the two-way locked mode position. Similarly, the leftmost detent recesses88will receive the detent members60as the cams24move to the right as shown toward the two-way unlocked mode position and snap the cams24and cam ring40into the proper position so that the cam ring40is not in contact with the annular groove142of the shift ring132.

In the preceding embodiments, the cams24are configured to provide two locking modes in the MMCMs10,130. In alternative embodiments, the MMCMS10,130may be configured to provide up to four locking modes by varying the configurations from the cams24and their camming surfaces86illustrated and described above. For example,FIG. 15illustrates an embodiment of a cam160configured to provide four locking modes in the MMCMs10,130. The following discussion uses the convention ofFIG. 2wherein the pawls20control relative rotation of the inner race14relative to the notch ring12in the clockwise direction, and the pawls22control relative rotation of the inner race14relative to the notch ring12in the counterclockwise direction. The cam160may include a camming surface162having a first camming surface portion164that will interact with the camming end78of the corresponding pawl20, and a second camming surface portion166that will interact with the camming end78of the corresponding pawl22. The cam160may further include four detent recesses (not shown) that will receive the detent member60to align the cam160in the corresponding locking mode positions.

In a two-way locked mode, the cam160may be positioned so that the camming ends78of both pawls20,22are disposed beyond the camming surface162, and the pawls20,22are rotated to their engaged or locked positions by the pawl springs26to lock the inner race14to the notch ring12for rotation in both directions. In a counterclockwise locking area168of the camming surface162for a one-way counterclockwise locked mode, the first camming surface portion164engages the camming end78of the pawl20to rotate the pawl20to the unlocked position that will allow the inner race14to rotate in the clockwise direction. The second camming surface portion166does not extend into the counterclockwise locking area168, so the pawl22remains in the locked position and the inner race14cannot rotate in the counterclockwise direction relative to the notch ring12. In a two-way unlocking area170of the camming surface162for a two-way unlocked mode, both camming surface portions164,166engage the corresponding camming ends78of the pawl20,22to rotate the pawls20,22to the unlocked positions that will allow the inner race14to rotate in either direction relative to the notch ring12. Finally, in a clockwise locking area172of the camming surface162for a one-way clockwise locked mode, the second camming surface portion166engages the camming end78of the pawl22to rotate the pawl22to the unlocked position that will allow the inner race14to rotate in the counterclockwise direction. The first camming surface portion164does not extend into the clockwise locking area172, so the pawl20remains in the locked position and the inner race14cannot rotate in the clockwise direction relative to the notch ring12.

The control mechanism for controlling the operation of MMCMs10,130may be configured to cause the cams160to be moved to the required position for each of the available locking modes. The control mechanism transmits actuation signals to the actuators104to rotate the shift drums102,134to the discrete angular positions necessary to cause the shift rings100,132to position the cams160for the camming surface162to engage the pawls20,22according to the commanded locking mode. Of course, the locations of the positions and the number of positions for the cams24,160will vary on based on factors such as the number of locking modes provided by the MMCMs10,130, the shape of the camming surfaces86,162to achieve a particular sequence of transitions between the available locking modes, and the like.

INDUSTRIAL APPLICABILITY

The MMCMs10,130in accordance with the present disclosure facilitate rotation of both the notch ring12and the inner race14with the rotating components to which they are connected while the actuator104for changing the locking modes of the MMCMs10,130remains stationary relative to the frame or the housing of the machine in which the MMCMs10,130are implemented. Where the actuator104is an electro-mechanical device, this arrangement can eliminate the risk of electrical wires running to the actuator104getting twisted around the rotating components connected by the MMCMs10,130. Similar risks are eliminated in hydraulic actuators having fluid conduits providing hydraulic fluids that could get tangled if the actuator104was operative coupled to move with the rotating components or reducing the complexity of the feeds to the rotating component. Stationary actuators104may also have a place and purpose in mechanically actuated MMCMs10,130.