KR20220050152A - Electric drive module with transmission with parallel twin gear pairs sharing the load to the final drive gear - Google Patents

Abstract

An electric drive module comprising an electric motor, a differential assembly, and a transmission that transmits rotational power between the electric motor and the differential assembly. The transmission has first and second reduction units. The first reduction portion has a drive gear rotatable about a first axis, and a pair of first reduction gears each meshingly coupled to a drive gear rotatable about a respective second axis. The second axes are spaced apart from each other and parallel to the first axis. The second reduction portion has a driven gear and a pair of second reduction gears. The driven gear is rotatable about a third axis parallel to the first axis. Each second reduction gear is meshedly coupled to the driven gear and is non-rotatably coupled to an associated one of the first reduction gears.

Description

Electric drive module with transmission with parallel twin gear pairs sharing the load to the final drive gear

CROSS REFERENCE TO RELATED APPLICATIONS

This application enjoys the benefit of U.S. Provisional Patent Application No. 62/942496, filed December 2, 2019, the disclosure of which is incorporated by reference as if set forth in full detail herein.

Field

The present disclosure relates to an electric drive module having a transmission having a pair of parallel gears that share a load for a final drive gear.

This section provides background information related to the present disclosure, which is not necessarily prior art.

It is known in the art to provide an electric drive module having an electric motor that drives a differential assembly through a transmission. A known electric drive module configuration is a coaxial arrangement in which the output shaft of the electric motor, the differential assembly and the input and output portions of the transmission are disposed about a common axis of rotation, or the output shaft of the electric motor, the differential assembly and the input and output portions of the transmission are parallel to each other. It may have an arrangement arranged around one or two or more rotation axes. While these configurations are well suited for their intended purpose, they can be somewhat difficult to package or fit into a particular vehicle because insufficient space may exist in the lateral or side-to-side or radial direction. Accordingly, there remains a need in the art for an electric drive module of a relatively compact design.

This section provides an overall overview of the disclosure and is not an exhaustive disclosure of the complete scope or features of the disclosure.

In one form, the present disclosure provides an electric drive module comprising an electric motor, a differential assembly, and a transmission that transmits rotational power between the electric motor and the differential assembly. The transmission has first and second reduction units. The first reduction portion has a drive gear rotatable about a first axis, and a pair of first reduction gears each meshingly coupled to a drive gear rotatable about a respective second axis. The second axes are spaced apart from each other and parallel to the first axis. The second reduction portion has a driven gear and a pair of second reduction gears. The driven gear is rotatable about a third axis parallel to the first axis. Each second reduction gear is meshedly coupled to the driven gear and is non-rotatably coupled to an associated one of the first reduction gears.

Additional fields of application will become apparent from the description provided herein. The description and specific examples in this summary are intended for purposes of illustration only, and are not intended to limit the scope of the disclosure.

The drawings described herein are for the purpose of illustrating selected embodiments only and not all possible implementations, and are not intended to limit the scope of the present disclosure.
1 is a schematic diagram of an exemplary vehicle having an electric drive module constructed in accordance with the teachings of this disclosure.
FIG. 2 is a perspective view of a partially fragmented portion of the electric drive module of FIG. 1 showing the electric motor and transmission in greater detail;
3 is a cross-sectional view of a portion of the electric drive module of FIG. 1 showing the final drive gear of the transmission and differential assembly;
4 is a schematic diagram of a portion of the electric drive module of FIG. 1 showing the relative positioning of the electric motor, transmission and differential assembly;
Fig. 5 is a perspective view of a portion of the electric drive module of Fig. 1 showing an optional parking lock mechanism;
6 is a plan view of a portion of a parking lock mechanism showing pawls disposed in engagement with a pair of parking gears to secure a countershaft of an electric drive module;
7 is a cross-sectional view taken through a portion of the parking lock mechanism, showing a cam plate oriented in a first rotational position and a pair of plungers disposed in an extended position;
8 is a perspective view of a portion of the parking lock mechanism showing the pawls disengaged from the pair of parking gears to allow rotation of the countershaft of the electric drive module;
9 is a cross-sectional view taken through a portion of the parking lock mechanism, showing a cam plate oriented in a second rotational position and a pair of plungers disposed in a retracted position;
Fig. 10 is a partial sectional perspective view of the parking lock mechanism;
11 is a perspective view of a portion of the parking lock mechanism showing the first side of the cam plate in greater detail;
12 is a cross-sectional view of a portion of the parking lock mechanism showing the lock actuator in greater detail;
13 is a perspective view of a portion of a cam plate showing a locking opening formed in a second face of the cam plate;
14 is a perspective view of a portion of the parking lock mechanism showing the plunger in the extended position and the pawl in the engaged position;
Corresponding reference numerals indicate corresponding parts throughout the various figures.

1 of the drawings, an exemplary vehicle having a drive module configured in accordance with the teachings of the present disclosure is indicated generally by reference numeral 10 . Vehicle 10 may include a front or primary driveline 14 and a rear or secondary driveline 16 . The front driveline 14 may include an engine 18 and a transmission 20 and may be configured to drive a front or primary set of drive wheels 22 . The rear driveline 16 may include an electric drive module 24 that may be configured to drive a rear or secondary set of drive wheels 26 as needed or on an “on demand” basis. . In this example the front wheel 22 is associated with the primary driveline 14 and the rear wheel 26 is associated with the secondary driveline 16, but alternatively the rear wheel would be driven by the primary driveline. and the front wheel may be driven by a secondary driveline. Also, while the electric drive module 24 is shown in this example as being configured to drive a secondary set of drive wheels part-time, a drive module constructed in accordance with the present teachings may be used as the sole propulsion means for a vehicle or in conjunction with other propulsion means. It will be appreciated that together the drive wheels may be employed to drive a (front, rear or other) set of wheels (eg, a front or set of wheels) on a full-time basis. The electric drive module 24 may include a drive unit 30 and a pair of axle shafts 32 .

2 and 3 , the drive unit 30 may include a housing 40 , an electric motor 42 , a transmission 44 , and a differential assembly 46 . The housing 40 may form a structure in which other components of the drive unit 30 are mounted. The housing 40 may be formed of two or more housing elements that may be fixedly coupled together, for example, via a plurality of threaded fasteners. Electric motor 42 may be any type of electric motor, such as a permanent magnet motor. The electric motor 42 may be mounted to a flange (not specifically shown) on the housing 40 , and may be disposed along a first axis of rotation 58 ( FIG. 4 ) and an output shaft that may be received within the housing 40 . (56) can have.

2 and 4 , transmission 44 includes one or more transmission stages or reduction units that provide a transmission input driven by an output shaft of an electric motor 42 and a transmission output that drives differential assembly 46 . may include Transmission 44 may include one or more transmission stages or reductions to provide multiple levels of gear reduction and may optionally include one or more multi-speed transmission stages. Also, optionally, a clutch (not shown) may be employed between the transmission output and the differential assembly 46 to selectively de-coupling the differential assembly 46 from the electric motor 42 . there is. In the example provided, the transmission 44 includes a drive gear or input pinion 60 , a first plurality of reduction gears 62 , a plurality of second reduction gears 64 , and a driven or final drive gear 66 . do. The input pinion 60 may be coupled to an output shaft of the electric motor 42 for rotation therewith. The first reduction gear 62 is meshed with the input pinion 60 , has more teeth than the input pinion 60 , and has a relatively larger pitch diameter than the pitch diameter of the input pinion 60 . Each first reduction gear 62 may be fixedly coupled to an associated one of the second reduction gears 64 to form a compound reduction gear 70 . The second reduction gear 64 has a larger pitch diameter and more teeth than the first reduction gear 62 . Each compound reduction gear 70 may be disposed on a countershaft or axle 72 mounted to the housing 40 for rotation about a second axis of rotation 74 parallel to and offset from the first axis of rotation 58 . can Each countershaft 72 may be supported by a pair of bearings that may be mounted to the housing 40 . Each countershaft 72 may be formed as a separate component that may be assembled to a corresponding one of the compound reduction gears 70 , or may be formed integrally and integrally with a corresponding one of the compound reduction gears 70 . It will be understood that it can be The final drive gear 66 may be supported by the housing 40 for rotation about a second axis of rotation 74 and an output shaft 76 parallel to and offset from the first axis of rotation 58 . In the example provided, the input pinion 60, the first reduction gear 62, the second reduction gear 64 and the final drive gear 66 are helical gears, and the first reduction gear 62 and the second reduction gear ( 64 is an axial on the compound reduction gear 70 associated with the transmission of rotational power between the input pinion 60 and the first reduction gear 62 and between the second reduction gear 64 and the final drive gear 66 . Opposite handed to counteract the force. Although transmission 44 has been described as employing helical gears, it will be understood that some or all of these gears may be configured as spur gears.

Referring to FIG. 3 , differential assembly 46 may include a differential input member and a pair of differential output members. A differential input member may be coupled to a final drive gear 66 for rotation with it about an output shaft 76 , while each differential output member is coupled to rotate with a corresponding one of the axle shafts 32 . can be ringed. In the specific example provided, differential assembly 46 includes differential case 80 and differential gearset 82 . The differential case 80 may function as a differential input member and may be supported for rotation on the housing 40 about the output shaft 76 by a pair of bearings 84 . Although bearing 84 is shown as being a tapered roller bearing in the examples provided, it will be appreciated that bearing 84 may be configured as an angular ball bearing or as a ball bearing in alternative examples. The differential gearset 82 may include a pair of differential pinions 90 and a pair of side gears 92 . The differential pinion 90 may be accommodated in the differential case 80 , and is rotatably disposed on a cross pin 94 mounted to the differential case 80 . The cross pins 94 may extend at least partially through the differential case 80 and are oriented perpendicular to the output shaft 76 . The side gear 92 is a differential output member in the example provided. The side gear 92 is accommodated in the differential case 80 and is rotatable relative to the differential case 80 about the output shaft 76 . Each side gear 92 meshes with a differential pinion 90 .

Each axle shaft 32 may be non-rotatably but axially slidably coupled to a corresponding one of the side gears 92 . In the example provided, each axle shaft 32 has a male spline segment 100 that meshes with an internal spline opening 102 of a corresponding one of the side gear 92 . Each axle shaft 32 is configured to transmit rotational power between one of the side gears 92 and an associated one of the vehicle wheels.

The configuration of the transmission 44 is advantageous in several respects. For example, the compound reduction gear 70 allows the use of a relatively high speed electric motor and a relatively small input pinion, which lowers the pitch line speed and thus in a positive manner the input pinion 60 and the first reduction gear ( 62) affects the bending stress, load capacity and service life. As another example, the load on the final drive gear 66 is shared across the second reduction gear 64 , which (as opposed to a configuration where the entire load is transmitted to the final drive gear 66 by a single gear) is 2 Allows a reduction in the size of the reduction gear 64 . As a result, the arrangement of gearing between the electric motor 42 and the final drive gear 66 allows a reduction in the package size of the drive unit 30 , and also these gears are relatively larger than known components of the electric drive unit. It can be formed of smaller and/or less expensive materials, reducing the cost and mass of the electric drive module 24 .

If desired, a parking lock mechanism (not shown) may be integrated into the electric drive module 24 . 2 and 4 , the parking lock mechanism comprises a pawl pivotally coupled to a housing 40 , and a differential assembly 46 rotatable to a final drive gear 66 or about an output shaft 76 . It can be constructed in a conventional manner with a toothed locking wheel rotatably coupled to the component. The pawl may pivot to engage and disengage with teeth on the toothed locking wheel to inhibit rotation of the final drive gear 66 relative to the housing 40 . Alternatively, the parking lock mechanism may be configured to selectively lock the countershaft 72 to the housing 40 . A scissor-like mechanism or a teeter-totter lever mechanism may be employed to simultaneously lock the countershaft 72 to the housing 40 .

5-7 , an optional parking lock mechanism 200 may be integrated into the drive unit 30 . The parking lock mechanism 200 may include a pair of parking gears 202 , a pawl 204 , a pair of plungers 206 , a pair of plunger biasing springs 208 , and an actuator 210 .

Each parking gear 202 may be non-rotatably coupled to an associated one of the countershaft 72 and may define a plurality of teeth 216 and a plurality of valleys 218 . Each valley 218 is disposed between each pair of teeth 216 .

The pole 204 includes a pole body 220 and a pair of pawl teeth 222 disposed at opposite ends of the pole body 220 . The pawl body 220 is configured such that each pawl tooth 222 is coupled to an associated one of the parking gear 202 (ie, each pawl tooth 222 is coupled to an associated one trough of the parking gear 202 ). 218 ) with a mating position ( FIG. 6 ) that rotationally locks parking gear 202 and countershaft 72 relative to housing 40 and pawl 204 relative to housing 40 . or pawls 204 between disengagement positions (FIG. 8) where each pawl tooth 222 leaves a tooth 216 on an associated one of the parking gear 202 so as not to inhibit rotation of the countershaft 72. It is pivotally coupled to the housing 40 of the drive unit 30 so that it can be moved. In the example provided, pivot axle 226 is mounted to housing 40 and extends through pawl 204 into actuator 210 . The pawl 204 is slightly on the pivot axle 226 to ensure that the load transmitted through the parking lock mechanism 200 is equally shared by the parking gear 202 and equally by the pawl teeth 222 . can be loosely accommodated. The pawl 204 may be biased about the pivot axle 226 toward a desired rotational position, such as a disengaged position. In the example provided, a helical torsion spring 258 is disposed about the pivot axle 226 and coupled to the housing 40 and the pawl body 220 .

Referring to FIG. 7 , each plunger 206 may have a plunger body having a guide portion 230 , a first body portion 232 , a transition portion 234 , and a second body portion 236 . . The guide portion 230 may be disposed on the first axial end of the plunger 206 and may be cylindrical in shape having a first diameter. The first body portion 232 may be disposed between the guide portion 230 and the transition portion 234 and may be sized in a desired manner. For example, the first body portion 232 may be generally cylindrical in shape having a desired diameter equal to the first diameter. In the example provided, the first body portion 232 has a diameter equal to the first diameter and the outer surface of the first body portion 232 is a guide portion by a desired amount, such as between 2 degrees and 30 degrees, preferably between 5 degrees and 15 degrees. Between 230 and transition portion 234 , a base (where first body portion 232 intersects guide portion 230 ) has a relatively shallow cone angle that tapers inwardly toward the central axis of plunger 206 . It has a truncated cone shape.

The second body portion 236 may also be cylindrical in shape, but has a second diameter that is less than the first diameter. Transition portion 234 may be formed in a frusto-conical shape to taper between first body portion 232 and second body portion 236 . A spring opening 240 may be formed in the first axial end of the plunger 206 and sized to receive a corresponding one of the plunger biasing springs 208 therein. In the examples provided, each plunger bias spring 208 is a helical coil compression spring, although it will be appreciated that other types of springs may be used in place of or in addition to the helical coil compression spring.

Each plunger 206 and plunger biasing spring 208 are received within a plunger opening 244 of the housing 40 . In the illustrated example, the housing 40 includes any pair of plunger bushings 246 that may be formed from a suitable material, such as hardened steel. Each plunger bushing 246 defines a first body portion 232 of a corresponding one of the plungers 206 and a plunger opening 244 sized to receive a corresponding one of the plunger biasing spring 208 . The plunger opening 244 may be a blind hole such that the plunger bushing 246 defines an interior wall 248 into which the end of a corresponding one of the plunger biasing springs 208 may abut.

Each plunger 206 has an extended position (shown in FIGS. 6 and 7 ) and a retracted position ( FIG. 6 ) in which the first body portion 232 of each plunger 206 is disposed in the path of rotation of the pawl body 220 . 8 and 9) relative to the housing 40 along its longitudinal axis. To position the plunger 206 in the extended position, the pawl teeth 222 must engage the parking gear 202 . When the outer surface of the first body portion 232 is tapered (truncated conical), the plunger biasing spring 208 ensures that the outer surface of the first body portion 232 of each plunger 206 is pole body 220 . will press the plunger 206 outwardly from the plunger opening 244 to contact the When the plunger 206 is disposed in its retracted position, the pawl 204 may be rotated to the disengaged position via a torsion spring 258 . When the pawl 204 is in the disengaged position, the pawl 204 may contact the second body portion 236 of one or both of the plungers 206 .

7 and 10 , actuator 210 is configured to control movement of plunger 206 between an extended position and a retracted position. Actuator 210 includes a pair of cam followers 250 , actuator hub 252 , cam plate 254 , bearing 256 , torsion spring 258 , rotation actuator 260 , and lock actuator 262 . may include

7 and 9 , each cam follower 250 may be disposed in series with an associated one of the plungers 206 . In the example provided, each cam follower 250 is integrally and integrally formed with an associated one of the plungers 206 . More specifically, the cam follower 250 may be of a spherical radius on the second axial end of the plunger 206 opposite the first axial end.

Actuator hub 252 may be fixedly coupled to housing 40 concentrically about an axis about which pawl 204 pivots. In the example provided, the actuator hub 252 is press-fitted to the pivot axle 226 . The actuator hub 252 may include a central portion 270 , a bearing mount 272 , and a lock actuator mount 274 . The central portion 270 may define a pivot axle opening 280 and a threaded opening 282 aligned along a common axis. The pivot axle opening 280 is formed through the first axial side of the central portion 270 and is sized to engage the pivot axle 226 in a press-fit manner. A threaded opening 282 is formed through a second opposite axial side of the central portion 270 . A bearing mount 272 is disposed concentrically around the central portion 270 and is to be coupled to the central portion 270 through a flange member 284 or alternatively through a plurality of spokes or webs. can The bearing mount 272 has an outer circumferential surface 286 , a shoulder 288 extending radially outward from the outer circumferential surface, and a retaining ring groove 290 formed into the outer circumferential surface 286 . The lock actuator mount 274 may have a bean-shaped (ie, kidney bean) shape best seen in FIG. 5 , and may be fixedly coupled to the bearing mount 272 to be radially offset from the central portion 270 . There is (eg, it may be formed integrally with it).

5, 7, and 11, the cam plate 254 includes an annular plate 300, a gear portion 302, a torsion spring mount 304, and a pair of sensor targets 306a, 306b. may include The annular plate 300 may be formed of any suitable material. The annular plate 300 may have an inner circumferential surface 310 and may define a pair of cams 312 . Each cam 312 is formed into a first face of the annular plate 300 facing the cam follower 250 and the plunger 206 . Each cam 312 may be a circumferentially extending groove in the first face of the annular plate 300 . Each cam 312 may taper between a first circumferential end 320 ( FIG. 11 ) of the deepest groove and a second opposite circumferential end 322 ( FIG. 11 ) of the shallowest groove. there is. Each cam follower 250 has a cam 312 (ie, a groove) such that rotation of the cam plate 254 about an axis on which the pawl 204 pivots causes a corresponding linear motion of the plunger 206 . ) can be accommodated into the corresponding one of More specifically, the cam bell into the deepest portion of the associated one of the cams 312 (ie, the first circumferential end 320 of the groove forming the associated one of the cams 312 ) as shown in FIG. 7 . The disposition of the eastern part 250 allows a corresponding one of the plunger biasing springs 208 to urge the associated one of the plungers 206 into its extended position, while the associated one of the cams 312 as shown in FIG. 9 . The placement of cam follower 250 in the shallowest portion of Position the corresponding one of the plungers 206 in its retracted position. Gear portion 302 may include a plurality of gear teeth that may be fixedly coupled to annular plate 300 such that the gear teeth are concentric with interior circumferential surface 310 . In the example provided, the gear teeth are integrally and integrally formed with the annular plate 300 . The gear teeth may be disposed around the entire circumference of the annular plate 300 as shown in the examples provided, or may be formed around one sector of the annular plate 300 . The torsion spring mount 304 may be a cylindrical post or protrusion that may extend from a second side of the annular plate 300 opposite the first side. Each sensor target 306a , 306b may be mounted to an annular plate 300 , by sensor 328 ( FIG. 10 ) when the cam plate 254 is in a predetermined rotational position relative to the housing 40 . configured to be detected. In the example provided, each sensor target 306a , 306b is a magnet and sensor 328 is a Hall effect sensor coupled to housing 40 .

Referring to FIG. 7 , bearing 256 is configured to support cam plate 254 for rotation relative to actuator hub 252 . Bearing 256 may include an inner bearing race 330 , an outer bearing race 332 , and a plurality of bearing elements 334 received between the inner bearing race 330 and the outer bearing race 332 . The inner bearing race 330 may be received onto the outer circumferential surface 286 of the bearing mount 272 and may abut against the shoulder 288 . If desired, the inner bearing race 330 may be press-fitted to the outer circumferential surface 286 of the bearing mount 272 . An outer retaining ring 336 may be received within the retaining ring groove 290 and may inhibit axial movement of the inner bearing race 330 on the actuator hub 252 in a direction away from the shoulder 288 . The outer bearing race 332 may be coupled to the cam plate 254 in any desired manner. For example, the outer bearing race 332 may be press fit or adhesively bonded to the inner circumferential surface 310 of the annular plate 300 . Alternatively, where the annular plate is formed from a plastic material, the annular plate 300 may be overmolded onto the outer bearing race 332 such that the outer bearing race 332 is adhesively bonded to the annular plate 300 . .

5 and 7 , a torsion spring 258 may be wound around a central portion 270 , and may repel against an actuator hub 252 , a first tang 340 and a cam plate. It can have a second tang 342 that can repel against a torsion spring mount 304 on 254 . In the example provided, the first tang 340 is received into a hole formed in the flange member 284 . The torsion spring 258 may be secured to the central portion 270 via a washer 346 and a threaded fastener 348 that is threaded into a threaded opening 282 in the central portion 270 . The torsion spring 258 is configured to rotationally bias the cam plate 254 about its axis of rotation toward a first rotational position, wherein the first rotational position moves the deepest portion of the cam 312 to the cam follower 250 . It may be a position oriented with respect to . Alternatively, the torsion spring 258 may be configured to rotationally bias the cam plate 254 about its axis of rotation to a position where the shallowest portion of the cam 312 is oriented relative to the cam follower 250 . .

Referring to FIG. 10 , the rotation actuator 260 is configured to control rotation of the cam plate 254 about an axis of rotation of the cam plate between a first rotation position and a second rotation position. The rotary actuator 260 may include a rotary electric motor (not specifically shown) and an output pinion (not specifically shown) that is meshably coupled to the gear teeth of the gear portion 302 of the cam plate 254 . . The electric motor may be coupled (eg, mounted) to the housing 40 . The output pinion may have one or more gears (not shown) disposed either directly by the electric motor (eg, the output pinion is mounted on the output shaft of the electric motor) or in a power transmission path between the electric motor and the output pinion. It may be driven through a transmission (not shown) with

The electric motor may be operated to drive the cam plate 254 to a second rotational position, wherein the second rotational position moves the opposite circumferential end of the cam 312, such as the shallowest portion of the cam 312, to the cam follower. 250) may be positioned. In some forms, an electric motor may be employed to drive the cam plate 254 to a desired rotational position and then maintain the cam plate 254 in this rotational position. Optionally, the cam plate 254 includes a stop member (not shown) that abuts against a mating stop member (not shown) that is coupled to the housing 40 when the electric motor rotates or drives the cam plate 254 to a desired rotational position. not) can be configured to have. However, in the example provided, sensor target 306b , sensor 328 , and lock actuator 262 are employed to maintain cam plate 254 in a desired rotational position such that power to the electric motor does not need to be maintained. .

The placement of the cam plate 254 into each of the first and second rotational positions may be sensed by a sensor 328 , which may generate a corresponding sensor signal in response thereto. For example, placement of the cam plate 254 in the first rotational position orients the sensor target 306a relative to the sensor 328 and the sensor 328 in response generates a first sensor signal, while Placing the cam plate 254 in the two rotational position orients the sensor target 306b relative to the sensor 328 which in response generates a second sensor signal. In response to receiving the second sensor signal, a controller (not shown) engages the cam plate 254 by a torsion spring 258 to inhibit rotation of the cam plate 254 out of the second rotational position. The lock actuator 262 may be controlled to couple the lock actuator 262 to the cam plate 254 (due to the applied moment).

10 and 12 , lock actuator 262 may include any means to inhibit rotation of cam plate 254 relative to housing 40 . In the example provided, the lock actuator 262 includes a solenoid assembly 400 and a lock opening 402 . The solenoid assembly 400 may be coupled to the housing 40 , and may include a solenoid 410 , a solenoid plunger 412 , and a solenoid spring 414 . The solenoid plunger 412 is movable in the solenoid 410 between an extended or latched position and a retracted or unlatched position. Solenoid spring 414 biases solenoid plunger 412 to an extended or latched position. The locking opening 402 is formed in the second face of the annular plate 300 and is configured to receive the solenoid plunger 412 therein when the cam plate 254 is in the second rotational position. In the example shown, the solenoid plunger 412 has a tip 420 defined by a spherical radius, and the locking opening 402 has a frusto-conical sidewall 422 . The contours of the tip 420 of the solenoid plunger 412 and the sidewall 422 of the locking opening 402 are routed through the torsion spring 258 when the solenoid 410 or electric motor is not energized to the solenoid plunger 412. Allows to be driven towards the retracted or unlatched position.

5 , 7 , and 12 , when no electric power is provided to the electric motor or solenoid 410 during operation of the drive unit 30 , the torsion spring 258 acts as a cam as shown in FIG. The deepest portion of 312 biases the cam plate 254 into a first rotational position where the deepest portion aligns with the cam follower 250 , and thus the plunger 206 as shown in FIG. ) is disposed in its extended position to contact the pawl body 220 and the pawl 204 is disposed about the pivot axle 226 such that the pawl teeth 222 engage the parking gear 202 . In this state, the countershaft 72 is locked substantially non-rotatably to the housing 40 and transmitted through each pawl tooth 222 and each parking gear 202 due to the configuration of the parking lock mechanism 200 . load is the same. In this state, the sensor target 306a is aligned with the sensor 328 , which in response generates a first sensor signal. The first sensor signal may be received by a controller (not shown) and indicates that the cam plate 254 is in a rotational position that causes the parking lock mechanism 200 to lock the countershaft 72 to the housing 40 . can be employed to determine. The solenoid spring 414 of the lock actuator 262 biases the tip 420 of the solenoid plunger 412 against the second face of the annular plate 300 .

To unlock the countershaft 72 from the housing 40 to allow rotation of the countershaft 72 relative to the housing 40 , the cam plate 254 in a first direction of rotation about the axis of rotation of the cam plate. Power may be applied to the electric motor to drive the output pinion to cause a corresponding rotation of ). Rotation of the cam plate 254 in the first direction of rotation aligns a groove or progressively shallower portion of the cam 312 with respect to the cam follower 250 as shown in FIG. from its extended position toward its retracted position. Due to the tapered configuration of the first body portion 232 and transition portion 234 of the plunger 206 and the moment applied to the pawl 204 by the torsion spring 258, the pawl teeth 222 cause the plunger ( It is gradually moved away from the teeth 216 of the parking gear 202 as the 206 progressively moves toward its retracted position. As shown in FIGS. 8 and 9 , the placement of the pawl 204 in contact with the second body portion 236 of the plunger 206 is such that the parking gear 202 and consequently the countershaft 72 are connected to the housing 40 . Position the pawl teeth 222 away from the parking gear 202 in a position that can rotate freely with respect to the . Further rotation of the cam plate 254 in the first rotational direction positions the cam plate 254 in a second rotational position, the second rotational position orients the sensor target 306b relative to the sensor 328 so that the sensor ( 328) in response thereto to generate a second sensor signal. In response to receiving the second sensor signal, the controller may provide power to the solenoid 410 to drive the solenoid plunger 412 into the lock opening 402 and maintain the solenoid plunger 412 in this position. Optionally, the controller may also terminate the supply of power to the motor. The moment applied to the cam plate 254 by the torsion spring 258 to urge the cam plate 254 toward the first rotational position locks the solenoid plunger 412 into the locking opening ( 402) is insufficient to press out.

In order to lock the countershaft 72 back to the housing 40 to suppress rotation of the countershaft 72 with respect to the housing 40, the supply of electric power to the solenoid 410 is terminated. The moment applied to the cam plate 254 by the torsion spring 258 to urge the cam plate 254 toward the first rotational position overcomes the force applied to the solenoid plunger 412 by the solenoid spring 414 and It is sufficient to force the solenoid plunger 412 out of the locking opening 402 . The moment applied to the cam plate 254 by the torsion spring 258 causes the cam plate 254 to rotate in a second rotational direction opposite to the first rotational direction. Rotation of the cam plate 254 in the second rotational direction causes the gear teeth of the gear portion 302 to back-drive the output pinion as the cam plate 254 rotates toward and to the first rotational position. (back-drive) can be done. Rotation of the cam plate 254 in the second direction of rotation also aligns the groove or progressively deeper portion of the cam 312 with respect to the cam follower 250 so that the plunger 206 extends its extension from its retracted position. move to position. Due to the tapered configuration of the transition portion 234 and the first body portion 232 of each plunger 206, the pawl body 220 and the plunger ( Contact between 206 drives pawl 204 about pivot axle 226 such that pawl teeth 222 rotate toward their respective parking gear 202 . The pawl teeth 222 can move directly into the valley 218 of the parking gear 202 in a situation where the parking gear 202 is oriented in the receptive position. In another situation, movement of the pawl teeth 222 into the valley 218 is such that the parking gear 202 is at a position where each pawl tooth 222 contacts a tooth of an associated one of the parking gears 202 . It can be blocked because it is oriented to However, the plunger biasing spring 208 engages the plunger 206 in its extended position (the outer surface of the first body portion 232 is coupled to the pawl 204 when the countershaft 72 is rotated slightly) to the pawl teeth ( 222 ) to the parking gear 202 (which drives it to engage with the parking gear 202 ).

The foregoing description of the embodiments has been presented for purposes of illustration and description. It is not intended to be exhaustive or to limit the present disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment, and where applicable, even if not specifically shown or described, are interchangeable and may be used in a selected embodiment. The same content can also be changed in numerous ways. Such modifications are not to be considered as a departure from the present disclosure, and all such modifications are intended to be included within the scope of the present disclosure.

Claims (20)

an electric drive module (24),
electric motor 42;
differential assembly 46; and
A transmission (44) for transmitting rotational power between an electric motor (42) and a differential assembly (46), the transmission (44) including a first reduction portion and a second reduction portion, the first reduction portion (60) and a pair of first reduction gears 62 , the drive gear 60 being rotatable about a first shaft 58 , each first reduction gear 62 meshing with the drive gear 60 . coupled and rotatable about a respective second axis 74 , the second axes 74 being spaced apart from each other and parallel to the first axis 58 , the second reduction portion comprising a driven gear 66 and a pair with a second reduction gear 64 of An electric drive module (24) having a transmission (44) meshingly coupled to the driven gear (66) and non-rotatably coupled to an associated one of the first reduction gears (62). According to claim 1,
The electric motor 42 includes an output shaft 56 , the drive gear 60 being coupled to the output shaft 56 for rotation together about a first axis 58 . 3. The method of claim 2,
The differential assembly 46 includes a differential input member 80 , the driven gear 66 being an electrically driven module 24 coupled to the differential input member 80 for co-rotation about a third axis 76 . . 4. The method of claim 3,
The differential assembly 46 is an electric drive module 24 including a differential gearset 82 . 5. The method of claim 4,
The differential gearset 82 is an electric drive module 24 including a plurality of differential pinions 90 meshed with a pair of side gears 92 . 6. The method of claim 5,
A pair of differential pinions (90) are mounted on a cross pin (94) mounted on a differential input member (80) for an electric drive module (24). According to claim 1,
The differential assembly 46 includes a differential input member 80 , the driven gear 66 being an electrically driven module 24 coupled to the differential input member 80 for co-rotation about a third axis 76 . . 8. The method of claim 7,
The differential assembly 46 is an electric drive module 24 including a differential gearset 82 . 9. The method of claim 8,
The differential gearset 82 is an electric drive module 24 including a plurality of differential pinions 90 meshed with a pair of side gears 92 . 10. The method of claim 9,
A pair of differential pinions (90) are mounted on a cross pin (94) mounted on a differential input member (80) for an electric drive module (24). According to claim 1,
a housing 40 in which the transmission 22 and differential assembly 46 are received;
a pair of parking gears (202), each parking gear (202) being non-rotatably coupled to an associated one of the second reduction gears (64);
A pawl 204 having a pair of pawl teeth 222 , the pawl 204 coupled to a housing 40 , each pawl tooth 222 having a corresponding one of the parking gear 202 . a pawl 204 pivotable between an engaged position in which it is engaged and a disengaged position in which the pawl teeth 222 are disengaged from the parking gear 202; and
A pair of plungers 206 movable between a first position and a second position, each plunger 206 having a first body portion 232 and a second body portion having a smaller diameter than the first body portion 232 . 236 , wherein contact between the first body portion 232 of the plunger 206 and the pawl 204 places the pawl 204 in an engaged position, the pawl 204 locating the second body portion 232 of the plunger 206 . The electric drive module (24) further comprising a pair of plungers (206) disposed in the disengaged position when the body portion (236) contacts the pawl (204). 12. The method of claim 11,
When the pawl 204 is in the engaged position, the first load transmitted between the first of the pawl teeth 222 and the first parking gear of the parking gear 202 is the second of the pawl teeth 222 . An electric drive module (24) equal to the second load transferred between the two pawl teeth and the second of the parking gears (202). 12. The method of claim 11,
The pawl 204 is pivotably disposed on the pivot axle 226 , and the fit between the pawl 204 and the pivot axle 226 is the load transferred between the pawl teeth 222 and the parking gear 202 . An electric drive module (24) that allows non-rotational movement of the pawl (204) relative to the pivot axle (226) to equalize. 12. The method of claim 11,
The first body portion 232 of the plunger 206 is an electric drive module 24 in the shape of a truncated cone. 15. The method of claim 14,
Each plunger 206 further includes a transition portion 234 disposed between the first body portion 232 and the second body portion 236 , the transition portion 234 being truncated cone-shaped, the first body The cone angle of the portion 232 is less than the cone angle of the transition portion 234 . 12. The method of claim 11,
and an actuator (210) for controlling movement of the plunger (206) between the first position and the second position, the actuator (210) comprising an actuator hub (252), a cam plate (254), and a plurality of cams a follower 250 , an actuator hub 252 coupled to the housing 40 , and a cam plate 254 rotatable about the actuator hub 252 and forming a pair of cams 312 . and each cam 312 is a circumferentially extending groove having a depth that tapers between the first circumferential end 320 and the second circumferential end 322, and each cam follower 250 includes a cam ( An electric drive module 24 received in a corresponding one of 312 and disposed in line with an associated one of the plungers 206 . 17. The method of claim 16,
Each cam follower 250 is an electric drive module 24 fixedly coupled to an associated one of the plungers 206 . 17. The method of claim 16,
Actuator 210 further includes a torsion spring 258 disposed between actuator hub 252 and cam plate 254 , which torsion spring 258 holds cam plate 254 relative to actuator hub 252 . 1 Electrical drive module (24) biasing towards a rotational position. 17. The method of claim 16,
Actuator 210 further includes lock actuator 262 , lock actuator 262 has solenoid assembly 400 and lock opening 402 , solenoid assembly 400 has solenoid plunger 412 , lock An opening 402 is formed in the cam plate 254 , and the solenoid assembly 400 allows the cam plate 254 to align the second circumferential end 322 of the cam 312 with the cam follower 250 . An electric drive module (24) energized to allow the solenoid plunger (412) to be received into the locking opening (402) and coupled to the cam plate (254) when rotated to the rotational position. 17. The method of claim 16,
An electric drive module (24) with a bearing (256) disposed radially between the actuator hub (252) and the cam plate (254).

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