KR102626241B1 - Electric drive module with transmission having parallel twin gear pairs sharing load to a final drive gear - Google Patents

Abstract

An electric drive module comprising an electric motor, a differential assembly, and a transmission that transfers rotational power between the electric motor and the differential assembly. The transmission has first and second reduction units. The first reduction unit has a drive gear rotatable about the first axis, and a pair of first reduction gears each meshed with the drive gear rotatable about the second axis. The second axes are spaced apart and parallel to the first axis. The second reduction unit 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 meshingly coupled to the driven gear and non-rotatably coupled to an associated one of the first reduction gears.

Description

Electric drive module with a transmission having a parallel twin gear pair sharing the load for the final drive gear {ELECTRIC DRIVE MODULE WITH TRANSMISSION HAVING PARALLEL TWIN GEAR PAIRS SHARING LOAD TO A FINAL DRIVE GEAR}

Cross-reference to related applications

This application is a circumvention-part continuation application of International Patent Application No. PCT/US2020/062541, filed on November 30, 2020, which enjoys the benefit of U.S. Provisional Patent Application No. 62/942496, filed on December 2, 2019. This application also benefits from U.S. Provisional Patent Application No. 63/161218, filed March 15, 2021, and U.S. Provisional Patent Application No. 63/161164, filed March 15, 2021. The disclosures of the applications cited above are incorporated by reference as if each application were fully and fully described herein.

Field

The present disclosure relates to an electric drive module having a transmission with a parallel gear pair sharing the load for the final drive gear.

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

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

This section provides a general overview of the disclosure and is not a comprehensive disclosure of the complete scope or features of the disclosure.

In one form, the present disclosure provides an electric drive module that includes an electric motor, a differential assembly, and a transmission that transfers rotational power between the electric motor and the differential assembly. The transmission has first and second reduction units. The first reduction unit has a drive gear rotatable about the first axis, and a pair of first reduction gears each meshed with the drive gear rotatable about the second axis. The second axes are spaced apart and parallel to the first axis. The second reduction unit 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 meshingly coupled to the driven gear and non-rotatably coupled to an associated one of the first reduction gears.

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

The drawings described herein are intended to illustrate only selected embodiments rather than all possible implementations and are not intended to limit the scope of the disclosure.
1 is a schematic diagram of an example vehicle having an electric drive module constructed in accordance with the teachings of the present disclosure.
Figure 2 is a perspective view of a partially fragmented portion of the electric drive module of Figure 1 showing the electric motor and transmission in more detail;
FIG. 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.
Figure 4 is a schematic diagram of a portion of an electric drive module similar to Figure 1, but showing the general relative positioning of the electric motor, transmission and differential assembly.
FIG. 4A is a schematic diagram of a portion of the electric drive module of FIG. 1 illustrating the relative positioning of the electric motor, transmission and differential assembly shown in FIG. 2. FIG.
Figure 5 is a perspective view of a portion of the electric drive module of Figure 1 showing an optional parking lock mechanism;
Figure 6 is a plan view of a portion of a parking lock mechanism showing a pawl disposed in conjunction with a pair of parking gears to secure a countershaft of an electric drive module;
Figure 7 is a cross-sectional view taken through a portion of a parking lock mechanism, showing a cam plate oriented in a first rotational position and a pair of plungers disposed in an extended position.
Figure 8 is a perspective view of a portion of a parking lock mechanism showing the pawls disengaged from a pair of parking gears to allow rotation of the countershaft of the electric drive module.
Figure 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.
Figure 10 is a partial cross-sectional perspective view of the parking lock mechanism.
Figure 11 is a perspective view of a portion of the parking lock mechanism showing the first side of the cam plate in more detail.
Figure 12 is a cross-sectional view of a portion of the parking lock mechanism showing the lock actuator in more detail.
Figure 13 is a perspective view of a portion of the cam plate showing a locking opening formed in a second side of the cam plate.
Figure 14 is a perspective view of a portion of a parking lock mechanism showing the plunger in an extended position and the pawl in an engaged position.
15 is a perspective view of another electric drive module constructed in accordance with the teachings of this disclosure.
Figure 16 is a cross-sectional view taken along line 16-16 in Figure 15.
Figure 17 is a cross-sectional view taken along line 17-17 in Figure 15.
18 is a perspective view of another electric drive module constructed in accordance with the teachings of this disclosure.
Figure 19 is a cross-sectional view of the electric drive module of Figure 18.
Figure 20 is an elevation view of a portion of the electric drive module of Figure 18 showing part of the drive unit in more detail.
Figure 21 is a perspective view of part of the electric drive module of Figure 18 showing part of the drive unit in more detail.
Figure 22 is a perspective view of a part of the drive unit shown in Figure 21 showing in more detail the shaft member and the first reduction gear of the transmission;
Figure 23 is a perspective cross-sectional view of the shaft member and the first reduction gear.
Figure 24 is a perspective cross-sectional view showing a portion of the drive unit including the shaft member, the first reduction gear, and the housing.
Figure 25 is a perspective cross-sectional view showing a portion of the drive unit including the shaft member, the second reduction gear, and the housing.
Figure 26 is an elevation view of a portion of the housing of the electric drive module of Figure 18;
27 is a top view of another electric drive module constructed in accordance with the teachings of this disclosure.
Figure 28 is an elevation view of a portion of the electric drive module of Figure 27;
Figure 29 is a side view of a portion of the electric drive module of Figure 27;
Corresponding reference numbers indicate corresponding parts throughout the various figures.

Referring to Figure 1 of the drawings, an exemplary vehicle having a drive module constructed in accordance with the teachings of the present disclosure is generally indicated at 10. Vehicle 10 may include a front or primary driveline 14 and a rear or secondary driveline 16. Front driveline 14 may include engine 18 and transmission 20 and may be configured to drive the front or primary set of drive wheels 22. The rear driveline 16 may include an electric drive module 24 that can be configured to drive the rear or secondary set of drive wheels 26 as needed or on an “on demand” basis. . In this example the front wheels 22 are associated with the primary driveline 14 and the rear wheels 26 are associated with the secondary driveline 16, but alternatively the rear wheels may be driven by the primary driveline. It will be understood that the front wheels can be driven by the secondary driveline. Additionally, although the electric drive module 24 is shown in this example as being configured to drive a secondary set of drive wheels on a part-time basis, a drive module constructed in accordance with the present teachings may serve as the sole means of propulsion for the vehicle or other means of propulsion. It will be appreciated that the drive may be employed to drive a set (front, rear or other) of wheels (e.g. a front or a set of wheels) on a full time basis. The electric drive module 24 may include a drive unit 30 and a pair of output shafts 32.

2 and 3, drive unit 30 may include a housing 40, a motor assembly 42, a transmission 44, and a differential assembly 46. Housing 40 may form a structure on which other components of drive unit 30 are mounted. 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. Motor assembly 42 may include any type of electric motor, such as a permanent magnet motor. Motor assembly 42 may be mounted on a flange (not specifically shown) on housing 40, disposed along the motor output or first axis of rotation 58 (FIG. 4), and may be received within housing 40. It may have a motor output shaft 56.

2 and 4, transmission 44 includes one or more transmission stages or reduction units that provide a transmission input driven by the output shaft of motor assembly 42 and a transmission output driving differential assembly 46. It can be included. Transmission 44 may include one or more transmission stages or reduction units to provide multiple levels of gear reduction and may optionally include one or more multi-speed transmission stages. Additionally, optionally, a clutch (not shown) may be employed between the transmission output and differential assembly 46 to selectively de-couple differential assembly 46 from motor assembly 42. there is. In the example provided, transmission 44 includes a drive gear or input pinion 60, a plurality of first reduction gears 62, a plurality of second reduction gears 64, and a driven gear or final drive gear 66. do. Input pinion 60 may be coupled to the output shaft of motor assembly 42 for rotation therewith. The first reduction gear 62 is in meshing engagement with the input pinion 60, has more teeth than the input pinion 60, and has a pitch diameter that is relatively larger 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 (twin) 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 on the housing 40 to rotate about a second rotation axis 74 parallel to and offset from the first axis of rotation 58. You can. Each countershaft 72 may be supported by a pair of bearings that may be mounted in housing 40. Each countershaft 72 may be formed as a separate component that can be assembled to a corresponding one of the composite reduction gears 70, or may be formed as a single piece and integrally with a corresponding one of the composite reduction gears 70. You will understand that it can be done. In the example shown in FIG. 2 , the rotation axis 74 and the first rotation axis 58 of the compound gear 70 are disposed in the plane P. Figure 4 shows a general example of a transmission 44 in which the second axis of rotation 74 is parallel to but offset from the first axis of rotation 58 so that all three axes are not located in a common plane. FIG. 4A is similar to the drawing of FIG. 4 but shows the positions of the first and second rotation axes 58 and 74 more accurately.

Final drive gear 66 may be supported by housing 40 to rotate about output shaft 76. In the example provided, the output axis 76 is parallel to and offset from the second axis of rotation 74 and the first axis of rotation 58; 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 are input To offset the axial forces on the compound reduction gear 70 associated with the transmission of rotational power between the pinion 60 and the first reduction gear 62 and between the second reduction gear 64 and the final drive gear 66. The catalog is opposite handed. 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 Figure 3, differential assembly 46 may include a differential input member and a pair of differential output members. The differential input members may be coupled to final drive gear 66 for rotation therewith about output shaft 76, while each differential output member is coupled for rotation with a corresponding one of output shafts 32. It can be ringed. In the particular example provided, differential assembly 46 includes differential case 80 and differential gearset 82. Differential case 80 may function as a differential input member and may be supported for rotation on housing 40 about output shaft 76 by a pair of bearings 84. Although bearing 84 is shown in the example provided as being a tapered roller bearing, it will be appreciated that bearing 84 could alternatively be configured as an angular ball bearing or as a ball bearing. The differential gear set 82 may include a pair of differential pinions 90 and a pair of side gears 92. The differential pinion 90 can be accommodated in the differential case 80 and is rotatably disposed on a cross pin 94 mounted on the differential case 80. Cross pin 94 may extend at least partially through differential case 80 and is oriented perpendicular to output axis 76. 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 with respect to the differential case 80 about the output shaft 76. Each side gear 92 is meshed with a differential pinion 90.

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

Drive unit 30 includes a differential output member (e.g., side gear 92) and output shaft 32 over a predetermined range of rotational speeds having a predetermined maximum value or magnitude. It is configured to run. The transmission 44 is such that when the drive unit 30 drives the differential output member at a rotational speed equal to the predetermined maximum magnitude, the motor output shaft 56 rotates at a rotational speed of more than 19,000 revolutions per minute, but without any engagement. The pitch line speed between the gear sets (i.e., between the drive gear 60 and the first reduction gear 62, or between the second reduction gear 64 and the driven gear 66) is less than or equal to 37 meters per second. It is structured as possible. Preferably, when the drive unit 30 is operated to drive the differential output member at a rotational speed equal to the predetermined maximum magnitude, the rotational speed of the motor output shaft 56 is 20,000 revolutions per minute or more, more preferably 1 Above 22,000 revolutions per minute, more preferably above 24,000 revolutions per minute, the pitch line speed between each set of meshing gears is less than or equal to 37 meters per second. Preferably, the pitch line speed between each set of meshing gears is such that when drive unit 30 is operated to drive the differential output member at a rotational speed equal to the predetermined maximum magnitude (i.e., motor output shaft 56) (when the rotational speed is more than any rotational speed detailed in the above description) is less than or equal to 35 meters per second. In view of the foregoing, transmission 44 advantageously allows the use of motor assemblies that are relatively small in size and have output capacities with relatively low torque and relatively high rotational speeds (i.e., relatively less expensive motor assemblies). . Additionally, the configuration of the transmission 44 is also important due to the combination of two gears (i.e., the second reduction gear 64) and the final drive gear 66. In this regard, the combination of the two second reduction gears 64 with the final drive gear 66 reduces the load on the teeth of the final drive gear 66. In other words, compound or twin gears 70 that are parallel to each other share the load transmitted to the final drive gear 66. This causes all external dimensions of the final drive gear 66 to be reduced by a factor equal to the square root of the number 2 (i.e. by 26%) compared to a configuration in which the final drive gear 66 is coupled by a single gear. This reduction in size can be very advantageous in reducing the overall size of the transmission 44 so that the transmission can be more easily packaged within a vehicle.

The configuration of transmission 44 is advantageous in several aspects. 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 thereby reduces the input pinion 60 and the first reduction gear in a positive manner. 62) Affects 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 (as opposed to a configuration where the entire load is transmitted to the final drive gear 66 by a single gear). 2 Allows a reduction in the size of the reduction gear 64. As a result, the arrangement of the gearing between the motor assembly 42 and the final drive gear 66 allows a reduction in the package size of the drive unit 30, and furthermore these gears are relatively larger than the components of known electric drive units. It can be made smaller and/or made of 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 includes a pawl pivotably coupled to the housing 40 and a differential assembly 46 rotatable about an output shaft 76 or on a final drive gear 66. It may be constructed in a conventional manner with a toothed locking wheel rotatably coupled to the component. The pawls can be pivoted into and out of engagement with teeth on the toothed locking wheel to inhibit rotation of final drive gear 66 relative to housing 40. Alternatively, the parking lock mechanism may be configured to selectively lock countershaft 72 to housing 40. A scissor-type mechanism or a teeter-totter lever mechanism may be employed to simultaneously lock the countershafts 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 countershafts 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 pole teeth 222 disposed at both 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 gears 202 (i.e., each pawl tooth 222 is coupled to an associated one of the parking gears 202). 218) and an engagement position (FIG. 6) that rotationally locks the parking gear 202 and the countershaft 72 relative to the housing 40, and the pawl 204 is positioned within the parking gear 202 relative to the housing 40. or between the disengaged positions (FIG. 8) where each pawl tooth 222 extends beyond the teeth 216 on an associated one of the parking gears 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 in housing 40 and extends through pawl 204 into actuator 210. The pawl 204 is positioned somewhat on the pivot axle 226 to ensure that the load transmitted through the parking lock mechanism 200 is shared equally by the parking gear 202 and equally by the pawl teeth 222. It can be loosely accepted. The pawl 204 can 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 pivot axle 226 and coupled to housing 40 and 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. . Guide portion 230 may be disposed on the first axial end of plunger 206 and may be cylindrical in shape with a first diameter. The first body portion 232 can be placed between the guide portion 230 and the transition portion 234 and sized in any desired manner. For example, first body portion 232 may be generally cylindrical in shape with a desired diameter, such as 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 inclined by a desired amount, such as from 2 to 30 degrees, preferably from 5 to 15 degrees. A base (where first body portion 232 intersects guide portion 230) has a relatively shallow cone angle between 230 and transition portion 234 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, but has a second diameter that is smaller than the first diameter. The transition portion 234 may be formed in a truncated cone shape to taper between the first body portion 232 and the 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 biasing spring 208 is a helical coil compression spring, but it will be understood that other types of springs may be used in place of or in addition to helical coil compression springs.

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

Each plunger 206 has an extended position (shown in FIGS. 6 and 7 ) and a retracted position (shown in FIGS. 6 and 7 ) in which the first body portion 232 of each plunger 206 is disposed in the rotational path of the pawl body 220 8 and 9) is movable along its longitudinal axis relative to the housing 40. 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 cone), the plunger biasing spring 208 is configured such that the outer surface of the first body portion 232 of each plunger 206 is aligned with the pawl body 220. will press the plunger 206 outward from the plunger opening 244 to contact the . When the plunger 206 is placed in its retracted position, the pawl 204 can be rotated to the disengaged position via the 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 plungers 206.

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

7 and 9, each cam follower 250 may be placed in series with an associated one of the plungers 206. In the example provided, each cam follower 250 is formed as one piece and integrally with an associated one of the plungers 206. More specifically, the cam follower 250 can be 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 pole 204 pivots. In the example provided, actuator hub 252 is press-fitted into pivot axle 226. Actuator hub 252 may include a central portion 270, a bearing mount 272, and a locking actuator mount 274. Central portion 270 may define a pivot axle opening 280 and a threaded opening 282 that are aligned along a common axis. Pivot axle opening 280 is formed through a first axial side of central portion 270 and is sized to couple to pivot axle 226 in a press-fit manner. A threaded opening 282 is formed through a second opposing axial side of the central portion 270 . A bearing mount 272 may be disposed concentrically around the central portion 270 and coupled to the central portion 270 through a flange member 284 or alternatively through a plurality of spokes or webs. You can. Bearing mount 272 has an outer circumferential surface 286, a shoulder 288 extending radially outwardly from the outer circumferential surface, and a retaining ring groove 290 formed into the outer circumferential surface 286. The locking actuator mount 274 may have a bean-shaped (i.e., kidney bean) shape, as best seen in Figure 5, and may be fixedly coupled to the bearing mount 272 so as to be radially offset from the central portion 270. (e.g., can be formed as a single entity 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 and 306b. It can be included. Annular plate 300 may be formed from any suitable material. The annular plate 300 may have an inner circumferential surface 310 and may form a pair of cams 312 . Each cam 312 is formed into a first side 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 side of the annular plate 300 . Each cam 312 may be tapered between a first circumferential end 320 (FIG. 11) of the groove with the deepest groove and a second opposing circumferential end 322 (FIG. 11) of the groove with the shallowest groove. there is. Each cam follower 250 has a cam 312 (i.e., a groove) such that rotation of the cam plate 254 about the axis around which the pawl 204 pivots causes a corresponding linear movement of the plunger 206. ) can be accepted within the corresponding one. More specifically, the cam longitudinally into the deepest portion of the associated one of the cams 312 (i.e., the first circumferential end 320 of the groove forming the associated one of the cams 312) as shown in FIG. The arrangement of the East 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 the cam follower 250 in the shallowest portion (i.e., the second circumferential end of the groove forming the associated one of the cams 312) counteracts the bias of the corresponding one of the plunger biasing springs 208. The corresponding one of the plungers 206 is positioned 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 inner circumferential surface 310. In the example provided, the gear teeth are formed monolithically and integrally 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 pillar 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 on annular plate 300 and detected by sensor 328 (FIG. 10) when cam plate 254 is in a predetermined rotational position relative to housing 40. It is 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.

7, bearings 256 are configured to support cam plate 254 for rotation about 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 inner bearing race 330 and outer bearing race 332. The inner bearing race 330 may be received on the outer circumferential surface 286 of the bearing mount 272 and abutted against the shoulder 288. If desired, inner bearing race 330 may be press-fitted to outer circumferential surface 286 of bearing mount 272. An outer retaining ring 336 may be received within the retaining ring groove 290 and can inhibit axial movement of the inner bearing race 330 on the actuator hub 252 in a direction away from the shoulder 288. Outer bearing race 332 may be coupled to cam plate 254 in any desired manner. For example, the outer bearing race 332 may be press-fitted or adhesively bonded to the inner circumferential surface 310 of the annular plate 300. Alternatively, if the annular plate is formed of a plastic material, the annular plate 300 may be overmolded on the outer bearing race 332 such that the outer bearing race 332 is adhesively bonded to the annular plate 300. .

5 and 7, the torsion spring 258 can be wound around the central portion 270 and includes a first tang 340 and a cam plate that can be repelled against the actuator hub 252. It may have a second tang 342 capable of repelling against the torsion spring mount 304 on 254 . In the example provided, first tang 340 is received within a hole formed in flange member 284. Torsion spring 258 may be secured to central portion 270 via a washer 346 and a threaded fastener 348 that is threaded into a threaded opening 282 of central portion 270. The torsion spring 258 is configured to rotationally bias the cam plate 254 about its rotation axis toward a first rotational position, wherein the first rotational position moves the deepest portion of the cam 312 toward the cam follower 250. It may be a position that is 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 the rotation of the cam plate 254 about the rotation axis of the cam plate between the first rotation position and the second rotation position. The rotary actuator 260 may include a rotary electric motor (not specifically shown) and an output pinion (not specifically shown) meshingly coupled to the gear teeth of the gear portion 302 of the cam plate 254. . An electric motor may be coupled (e.g., mounted) to housing 40. The output pinion may be driven directly by the electric motor (e.g., the output pinion is mounted on the output shaft of the electric motor) or via one or more gears (not shown) disposed in the power transmission path between the electric motor and the output pinion. It can be driven through a transmission (not shown).

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

The placement of cam plate 254 into each of the first and second rotational positions may be sensed by sensor 328, and sensor 328 may in response generate a corresponding sensor signal. For example, placement of cam plate 254 in a first rotational position orients sensor target 306a relative to sensor 328 and sensor 328 in response generates a first sensor signal, while Placing the cam plate 254 in the two rotation position orients the sensor target 306b relative to the sensor 328 and the sensor 328 generates a second sensor signal in response. In response to receiving the second sensor signal, a controller (not shown) may act to inhibit rotation of the cam plate 254 out of the second rotational position (i.e., tighten the cam plate 254 by means of a torsion spring 258). The locking actuator 262 can be controlled to couple the locking 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, locking actuator 262 includes a solenoid assembly 400 and a locking opening 402. Solenoid assembly 400 may be coupled to housing 40 and may include solenoid 410 , solenoid plunger 412 and solenoid spring 414 . Solenoid plunger 412 is moveable in 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 on the second side 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 truncated conical sidewall 422. The tip 420 of the solenoid plunger 412 and the contour of the side wall 422 of the locking opening 402 are configured to allow the solenoid plunger 412 to move through the torsion spring 258 when power is not provided to the solenoid 410 or the electric motor. Allows to be driven towards the retracted or unlatched position.

5, 7, and 12, when power is not provided to the electric motor or solenoid 410 during operation of drive unit 30, torsion spring 258 cams as shown in FIG. biases cam plate 254 to a first rotational position where the deepest portion of 312 is aligned with cam follower 250, such that plunger 206 is aligned with first body portion 232, 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 substantially non-rotatably locked in the housing 40 and, due to the configuration of the parking lock mechanism 200, is transmitted through each pawl tooth 222 and each parking gear 202. The load is the same. In this state, sensor target 306a is aligned with sensor 328, and sensor 328 generates a first sensor signal in response. A first sensor signal may be received by a controller (not shown) and determines 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 make decisions. The solenoid spring 414 of the locking actuator 262 biases the tip 420 of the solenoid plunger 412 against the second side of the annular plate 300.

Cam plate 254 in a first direction of rotation about the axis of rotation of the cam plate to unlock countershaft 72 from housing 40 to allow rotation of countershaft 72 relative to housing 40. 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 the groove or progressively shallower portion of the cam 312 with the cam follower 250, as shown in FIG. 9, causing the plunger 206 to It is made to move from its extended position toward its retracted position. Due to the tapered configuration of the first body portion 232 and the transition portion 234 of the plunger 206 and the moment applied to the pawl 204 by the torsion spring 258, the pawl teeth 222 are formed on the plunger ( As 206 gradually moves toward its retracted position, it is gradually moved away from the teeth 216 of parking gear 202. 8 and 9 , the arrangement of the pawl 204 in contact with the second body portion 236 of the plunger 206 causes the parking gear 202 and, consequently, the countershaft 72 to be positioned against the housing 40. Position the pawl teeth 222 away from the parking gear 202 in a position where they can freely rotate relative to. Additional rotation of the cam plate 254 in the first direction of rotation positions the cam plate 254 in a second rotational position, which orients the sensor target 306b relative to the sensor 328 to 328) generates a second sensor signal in response. 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 locking opening 402 and maintain the solenoid plunger 412 in this position. Optionally, the controller may also terminate power to the motor. A moment applied to the cam plate 254 by the torsion spring 258 to press the cam plate 254 toward the first rotational position moves the solenoid plunger 412 into the locking opening ( 402) It is insufficient to pressurize outward.

To lock the countershaft 72 back to the housing 40 to inhibit rotation of the countershaft 72 relative to the housing 40, the supply of power to the solenoid 410 is terminated. The moment applied to the cam plate 254 by the torsion spring 258 overcomes the force applied to the solenoid plunger 412 by the solenoid spring 414 to urge the cam plate 254 toward the first rotational position. This 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 rotation direction opposite to the first rotation direction. Rotation of the cam plate 254 in the second direction of rotation causes the gear teeth of the gear portion 302 to back-drive the output pinion as the cam plate 254 rotates toward and into 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, such that the plunger 206 extends from its retracted position. Move to location. 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 the pawls 206 drives the pawls 204 about the pivot axle 226 such that the pawl teeth 222 rotate toward their respective parking gears 202. The pawl teeth 222 can move directly into the ribs 218 of the parking gear 202 when the parking gear 202 is oriented in the receiving position. In another situation, movement of the pawl teeth 222 into the trough 218 causes the parking gear 202 to position each pawl tooth 222 in contact with an associated one of the teeth of the parking gear 202. It can be blocked because it is oriented. However, the plunger biasing spring 208 may hold the plunger 206 in its extended position when the countershaft 72 is slightly rotated (the outer surface of the first body portion 232 is coupled to the pawl 204 and the pawl teeth ( 222) is driven to be coupled to the parking gear 202) to provide compliance.

15-17, another electric drive module constructed in accordance with the teachings of this disclosure is generally indicated by reference numeral 24a. The electric drive module 24a is substantially similar to the electric drive module 24 (FIG. 1) described in detail above, except for modifications to the configuration of the transmission 44a and the housing 40a to accommodate the transmission 44a. similar. Transmission 44a employs additional reduction between second reduction gear 64 and final drive gear 66 such that second reduction gear 64 is not directly engaged with final drive gear 66. More specifically, the transmission 44a is non-rotatably coupled to the third reduction gear 62a and the third reduction gear 62a meshing with the second reduction gear 64 of the compound reduction gear 70 and performs final driving. It includes a second compound gear 70a having a fourth reduction gear 64a in meshing engagement with the gear 66. It will be appreciated that each compound gear 70, 70a may be rotationally and axially supported relative to the housing 40a by a pair of bearings (not shown).

18 and 19, a third exemplary electric drive module constructed in accordance with the teachings of this disclosure is generally indicated at 24b. Components, aspects, features and functions of the electric drive module 24b that are not explicitly described herein or shown (partially or fully) in the accompanying drawings are fully described in detail herein as if their disclosure were fully described herein. Co-pending U.S. Patent Application No. 16/751596, filed January 24, 2020, and U.S. Patent Application No. 16/865912, filed May 4, 2020, December 2020, all incorporated by reference as if incorporated by reference. U.S. Patent Application No. 17/128288, filed on April 21, International Patent Application No. PCT/US2020/029925, filed on April 24, 2020, International Patent Application No. PCT/US2020, filed on November 30, 2020 /062541, and/or U.S. Provisional Patent Application No. 63/159511, filed March 11, 2021. You can. Briefly, electric drive module 24b includes a housing 40b, a motor assembly 42b, a transmission 44, a differential assembly 46, and a pair of output shafts 32.

Housing 40b may define one or more cavities (not specifically shown) in which motor assembly 42b, transmission 44, differential assembly 46, and output shaft 32 may be at least partially housed. . In the example shown, housing 40b includes gearbox cover 500, gearbox 502, motor housing 504, motor housing cover 506, and end cover 508. Gearbox cover 500 and gearbox 502 abut each other and form a cavity in which transmission 44 and differential assembly 46 are received, while gearbox 502, motor housing 504 and motor housing cover. 506 abut each other to form a cavity in which motor assembly 42b is received.

Referring particularly to FIG. 19 , motor assembly 42b includes an electric motor 510 and a motor control unit 512 that includes an inverter 514 . The electric motor 510 includes a stator 516 and a rotor 518 rotatable about a first rotation axis 58. Rotor 518 includes a motor output shaft 56.

19 and 20, transmission 44 may be configured in any desired manner to transfer rotational power between motor output shaft 56 and differential input member 80b of differential assembly 46. Transmission 44 may include one or more fixed reduction units of any desired type, or may be configured as a multi-speed transmission with two or more alternately engageable reduction units (and optionally one or more fixed reduction units). The fixed or multi-speed reduction portion may be configured in any desired manner to cause the axis of rotation of the motor output shaft 56 to be oriented relative to the output axis 76 in a desired manner (e.g., parallel and offset, coincident, transverse, perpendicular, inclined). It can be.

In the example shown in FIGS. 20 and 21, the transmission 44 is a single-speed, multi-speed transmission employing a plurality of helical gears. Transmission 44 includes a transmission input gear 60, a pair of compound gears 70, and a transmission output gear 66 coupled for rotation with a motor output shaft 56. Each compound gear 70 is rotatable about a second rotational axis 74 parallel to and offset from the first rotational axis 58 and meshingly engageable with a transmission input gear 60. It may include a reduction gear 62 and a second reduction gear 64 coupled thereto for rotation with the first reduction gear 62 and in meshing engagement with the transmission output gear 66 .

22 and 23, each compound gear 70 has a second reduction gear 64 formed as a single piece and integrally with the shaft member 530, and a first reduction gear 62 formed by a process such as laser welding. It can be configured to be rotatably coupled to the shaft member 530 in any desired manner. However, the shaft member 530 may be formed unitarily and integrally with the first reduction gear 62 instead of the second reduction gear 64, or the shaft member 530 may be formed as a single piece with the first and second reduction gears 62. , 64) may all be separate components rotatably coupled, or the first and second reduction gears 62, 64 may be formed unitarily and integrally with the shaft member 530. will be. Shaft member 530 may extend axially outwardly from each of the first and second reduction gears 62 and 64. In the particular example provided, shaft member 530 and second reduction gear 64 are the same component in each compound gear 70. However, shaft member 530 and second reduction gear 64 may be unique for each composite gear 70, or may be unique to composite gear 70 (i.e., first and second reduction gears in the example provided) It will be appreciated that 62 and 64) and shaft member 530) may be the same. In some situations, specific teeth on each first reduction gear 62 are meshingly engaged with specific teeth on transmission input gear 60 (or vice versa) and/or specific teeth on each second reduction gear 64 It may be necessary and/or desirable to adjust the timing of the compound gear 70 such that the teeth are meshingly engaged with specific valleys on the transmission output gear 66 (or vice versa). In other situations, it may be desirable to configure the transmission so that compound gear 70 does not need to be timed to either transmission input gear 60 or transmission output gear 66.

Returning to Figures 20 and 21, the first reduction gears 62 may be arranged in opposite phase with respect to each other. In this regard, one of the first reduction gears 62 may be positioned such that one of its teeth is received between and centered between two adjacent teeth on the transmission input gear 60, One of the teeth of gear 60 is disposed between two adjacent teeth on the other of the first reduction gears 62 . However, it will be appreciated that other phase settings may be employed and the teeth of both first reduction gears 62 may be in-phase with each other. The second reduction gears 64 may be arranged in phase with each other. In this regard, one of the teeth on the first of the second reduction gears 64 is received and centered between the first pair of adjacent teeth on the transmission output gear 66, and at the same time the second reduction gear ( One of the teeth on the second reduction gear 64) is received and centered between the second pair of adjacent teeth on the transmission output gear 66. However, other phase settings may be employed, and the teeth of the second reduction gear 64 may have opposite phase orientations, and the phase setting of the second reduction gear 64 may be different from that of the first reduction gear 62. It will be understood that it may be the same or different from .

21, 24, and 25, each composite gear 70 may be supported to rotate with respect to the housing 40b by the first bearing 542 and the second bearing 544. In addition to the ability to handle and transmit radially induced forces between the composite gear 70 and the housing 40b, the first bearing 542 serves as a barrier to the composite gear 70 when rotational power is transmitted through the transmission 44. ) may be a type of ball bearing configured to process and transmit force induced in the axial direction along the second rotation axis 74. For example, first bearing 542 may be some type of angular contact bearing or deep groove ball bearing. The first bearing 542 may be received in a bore 546 formed in the gearbox cover 500, and a snap ring 548 or other type of coupling may be connected to the second rotating shaft 74 (i.e., composite gear 70). is formed on the outer bearing race of the first bearing 542 and the axial end of the gearbox cover 500 to suppress axial movement of the first bearing 542 in the first axial direction along the rotation axis of the It can be fixed to the shoulder to which it is coupled. Housing 40b may further include a bearing cover 550 that can be mounted on gearbox cover 500 to close bore 546 in gearbox cover 500 and cover first bearing 542. there is. If desired, a pad or boss 552 (FIG. 26) radially overlaps and axially overlaps the outer bearing race of first bearing 542 to further support and stabilize first bearing 542. It may be formed on the bearing cover 550 to come into contact with it. Additionally or alternatively, an oil discharge channel in the gearbox cover 500 that allows the lubricant passing through the first bearing 542 to drain into an area such as a sump 562 (FIG. 19). A passage 554 (FIG. 26) may be provided in the bearing cover 550 to allow discharge to 560.

21 and 25, the second bearing 544 is a type of bearing configured to at least substantially or exclusively process and transmit the force induced in the radial direction between the composite gear 70 and the housing 40b. You can. In the example shown, the second bearing 544 is a roller bearing employing a cylindrical roller between the inner and outer bearing races. The second bearing 544 may be accommodated within the bore 570 formed within the gear case 500. If desired, an inner bearing race 600 may be formed on the shaft member 530 to which the first and second reduction gears 62 and 64 are rotationally coupled.

Referring again to FIGS. 20 and 21 , the second rotation axis 74 (i.e., the rotation axis of the compound gear 70) is the overall speed or gear reduction of the transmission 44, and the electric drive module 24b (FIG. 18) It can be positioned relative to the first axis of rotation 58 in any desired manner to meet or accommodate criteria such as the size of the enclosure that can be packaged and/or the degree to which the teeth of the first reduction gear 62 are evenly loaded. there is. In the example shown, the second rotation axis 74 and the first rotation axis 58 are disposed in plane P, and an even number of teeth are formed on the transmission input gear 60. Configuration in this manner can help balance the load transmitted between each first reduction gear 62 and the transmission input gear 60.

27-29, a portion of a fourth exemplary electric drive module constructed in accordance with the teachings of this disclosure is generally indicated at 24c. Components, aspects, features and functions of the electric drive module 24c that are not explicitly described herein or shown (partially or fully) in the accompanying drawings may be incorporated into the electric drive unit described in any of the foregoing embodiments. It may be configured or function in a manner similar to the components, aspects, features and/or functions of. In this example, the first and second rotation axes 58, 74 are parallel to each other, but not parallel to the output axis 76. Rather, the second rotation axis 74 is tilted relative to the output axis 76 by an inclination angle that is greater than zero, for example 15 degrees. As a result, the second reduction gear 64c and the drive gear 66c of the compound reduction gear 70c are non-cylindrical gears (e.g., beveloids, hypopoloids or other non-orthogonal gears). can be formed. Configuration in this manner causes the motor assembly to extend away from the housing with increasing distance from the input pinion 60 along the first axis of rotation 58 . In the example provided, the non-orthogonal configuration of second reduction gear 64c and drive gear 66c provides additional clearance between one of the tubes of the housing and the end of the motor assembly opposite the input pinion 60. As shown, the housing includes a pair of tubes that press into tubular protrusions formed on the central housing member. A welding slug is received through an opening in the tubular protrusion and welded to an associated one of the tubes to inhibit axial and rotational movement of the tube relative to the central housing member.

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

Claims (13)

An electric drive module 24b,
A housing assembly 40b including a motor housing 504, a gearbox 502, and a gearbox cover 500, wherein the motor housing 504 defines a motor cavity, and the gearbox 502 and the gearbox cover (500) includes a housing assembly (40b), which cooperates to form a transmission cavity;
A motor assembly (42b) housed within a motor housing (504) and having an electric motor (510) and an inverter (514), wherein the electric motor (510) has a stator (516) and a rotor (518). ) is a motor assembly 42b, having a motor output shaft 56;
a first output shaft 32 rotatable about the output shaft 76; and
A transmission 44 that transmits rotational power between an electric motor 510 and a first output shaft 32, wherein the transmission 44 includes a drive gear 60, a pair of first reduction gears 62, and a pair of first reduction gears 62. a second reduction gear 64, and a driven gear 66, wherein the drive gear 60 rotates with the motor output shaft 56 about the first axis 58. Coupled to, each first reduction gear 62 is meshed with the driving gear 60 and rotatable about each second axis 74, and the second axes 74 are spaced apart from each other and Transmission 44 parallel to a primary axis 58, each second reduction gear 64 meshingly coupled to a driven gear 66 and rotatably coupled to an associated one of the first reduction gears 62. ), including
The driven gear (66) is rotatable about a third axis parallel to the first and second axes (58, 74),
The drive gear 60, the first reduction gear 62, the second reduction gear 64, and the driven gear 66 are helical gears,
The first reduction gear 62 and the second reduction gear 64 are of opposite orientation,
Electric drive module 24b, wherein the first axis 58 and the second axis 74 are arranged in a common plane. According to paragraph 1,
The electric drive module 24b further includes a second output shaft 32 and a differential assembly 46, wherein the differential assembly 46 includes a differential input member 80b coupled for rotation with the driven gear 66; and an electric drive module having first and second differential output members (92), wherein the first and second output shafts (32) are coupled to rotate with the first and second differential output members (92), respectively. (24b). According to paragraph 2,
Electric drive module 24b, wherein differential assembly 46 includes differential gearset 82. According to paragraph 3,
Electric drive module 24b, wherein the differential gear set 82 includes a plurality of differential pinions 90 in meshing engagement with a pair of side gears 92. According to clause 4,
An electric drive module (24b), wherein a pair of differential pinions (90) are mounted on a cross pin (94) that is mounted on a differential input member (80). An electric drive module 24b,
A housing assembly 40b including a motor housing 504, a gearbox 502, and a gearbox cover 500, wherein the motor housing 504 defines a motor cavity, and the gearbox 502 and the gearbox cover (500) includes a housing assembly (40b), which cooperates to form a transmission cavity;
A motor assembly (42b) housed within a motor housing (504) and having an electric motor (510) and an inverter (514), wherein the electric motor (510) has a stator (516) and a rotor (518). ) is a motor assembly 42b, having a motor output shaft 56;
a first output shaft 32 rotatable about the output shaft 76; and
A transmission 44 that transmits rotational power between an electric motor 510 and a first output shaft 32, wherein the transmission 44 includes a drive gear 60, a pair of first reduction gears 62, and a pair of first reduction gears 62. a second reduction gear 64, and a driven gear 66, wherein the drive gear 60 rotates with the motor output shaft 56 about the first axis 58. Coupled to, each first reduction gear 62 is meshed with the driving gear 60 and rotatable about each second axis 74, and the second axes 74 are spaced apart from each other and Transmission 44 parallel to a primary axis 58, each second reduction gear 64 meshingly coupled to a driven gear 66 and rotatably coupled to an associated one of the first reduction gears 62. ), including
The driven gear (66) is rotatable about a third axis parallel to the first and second axes (58, 74),
The electric drive module 24b further includes a second output shaft 32 and a differential assembly 46, wherein the differential assembly 46 includes a differential input member 80b coupled for rotation with the driven gear 66; and first and second differential output members (92), wherein the first and second output shafts (32) are coupled to rotate with the first and second differential output members (92), respectively;
The electric drive module 24b further includes a parking lock mechanism 200 having a first rotatable parking lock gear 202 and a first pawl tooth 222, wherein the first rotatable parking lock gear 202 It has a plurality of first park lock teeth 216, wherein the first pawl teeth 222 are pivotably coupled to the housing assembly 40b and the first park lock gear 202 is rotatable. The first position beyond the locking teeth 216 and the first pawl teeth 222 are disposed between the first parking lock teeth 216 of the first rotatable parking lock gear 202 to form a housing assembly 40b. The electric drive module (24b) is pivotable between a second position inhibiting rotation of the first rotatable parking lock gear (202) relative to the first rotatable parking lock gear (202). According to clause 6,
It further comprises a second rotatable parking lock gear (202) and a second pawl tooth (222), wherein the second rotatable parking lock gear (202) has a plurality of second parking lock teeth (216), The first and second rotatable parking lock gears 202 are each coupled for rotation to an associated one of the second reduction gears 64 and the second pawl teeth 222 are coupled to the first pawl teeth 222. Fixedly coupled, positioning the first pawl teeth 222 in the first position correspondingly causes the second pawl teeth 222 to be connected to the second parking lock teeth of the second rotatable parking lock gear 202. Placing the teeth 216 in a position away from the position and placing the first pawl teeth 222 in the second position correspondingly causes the second pawl teeth 222 to be positioned outside of the second rotatable parking lock gear 202. An electric drive module (24b) positioned between second park lock teeth (216) to inhibit rotation of the second rotatable park lock gear (202) relative to the housing assembly (40b). In clause 7,
When the first pawl teeth 222 are disposed in the second position, the first load transferred between the first pawl teeth 222 and the first rotatable parking lock gear 202 is transferred to the second pawl teeth ( The electric drive module 24b is equal to a second load transmitted between 222) and the second rotatable parking lock gear 202. According to clause 8,
The first pawl teeth 222 are fixedly coupled to a pawl body 220 pivotally disposed on the pivot axle 226, and the fit between the pawl body 220 and the pivot axle 226 is: The ratio of the pawl body 220 relative to the pivot axle 226 to allow the loads transmitted between the first and second pawl teeth 222 and the first and second rotatable parking lock gears 202 to be equalized. Electric drive module 24b, allowing rotational movement. An electric drive module 24b,
Housing (40b);
An electric motor 510 coupled to the housing 40b, the electric motor 510 having a motor output shaft 56 rotatable about a motor axis 58;
a first output shaft (32) rotatable about an output axis (76) parallel to the motor axis (58); and
A transmission 44 accommodated in a housing 40b and transmitting rotational power between an electric motor 510 and a first output shaft 32, wherein the transmission 44 includes an input pinion 60, a pair of first composite a gear 70, and a driven gear 66, wherein the input pinion 60 is coupled to the motor output shaft 56 to rotate with the motor output shaft 56, each first compound gear 70 is rotatable about a first intermediate axis 74 parallel to the motor shaft 58, and each first compound gear 70 is a first reduction gear 62 meshed with the input pinion 60. and a second reduction gear 64 coupled to the first reduction gear 62 to rotate with the first reduction gear 62, wherein the driven gear 66 is received within the housing 40a and the second reduction gear 64 is coupled to the first reduction gear 62 to rotate with the first reduction gear 62. Comprising a transmission (44), meshed by (64),
The load on the driven gear (66) is shared evenly across the second reduction gear (64),
The input pinion 60, first reduction gear 62, second reduction gear 64, and driven gear 66 are helical gears,
The first reduction gear 62 and the second reduction gear 64 are of opposite orientation,
Electric drive module 24b, wherein the motor shaft 58 and the first intermediate shaft 74 are arranged in a common plane. According to clause 10,
further comprising a differential assembly (46) and a second output shaft (32), the differential assembly (46) being disposed within the housing (40a) and having a differential input member (80b) and a pair of differential output members (92); The differential input member 80b is driven by the transmission 44, and each differential output member 92 is rotatable relative to the differential input member 80b about the output shaft 76, and produces first and second outputs. Electric drive module (24b), wherein each of the shafts (32) is coupled for rotation with an associated one of the differential output members (92). According to clause 11,
Electric drive module 24b, wherein differential input member 80b is coupled to rotate with driven gear 66. delete