JP2023159283A - Electric drive module with a transmission with twin parallel gear pairs sharing the load with respect to the final drive gear - Google Patents

Abstract

An electric drive module designed to be relatively compact is provided. An electric drive module includes an electric motor, a differential assembly, and a transmission that transmits rotational power between the electric motor and the differential assembly, the transmission including a first reduction gear and a differential assembly. a second reduction gear, the first reduction gear having a drive gear rotatable about the first axis; and a drive gear each meshingly engaged with the drive gear and rotatable about the respective second axis. and a pair of first reduction gears. The second axes are spaced apart and parallel to the first axis, and the second reduction gear 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, and each of the second reduction gears is in meshing engagement with the driven gear and Non-rotatably coupled to the associated. [Selection diagram] Figure 2

Description

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS This application claims the benefit of U.S. Provisional Patent Application No. 62/942,496, filed December 2, 2019, the disclosure of which is detailed herein. Incorporated by reference as if fully set forth.

[0002] The present disclosure relates to an electric drive module that includes a transmission having a parallel gear pair that shares the load with respect to the final drive gear.

[0003] This section provides background information related to this disclosure, which is not necessarily prior art.

[0004] It is known in the art to provide an electric drive module having an electric motor that drives a differential assembly through a transmission. Known electric drive module configurations include coaxial configurations in which the output shaft of the electric motor, the differential assembly, and the input and output of the transmission are arranged around a common axis of rotation, or the output shaft of the electric motor, the differential The assembly, and the transmission inputs and outputs, can have a configuration in which they are arranged around two or more rotational axes that are parallel to each other. Although such configurations are well suited for their intended purpose, there may not be enough lateral or transverse or radial space to accommodate them in some vehicles; Or it can be somewhat difficult to fit. Accordingly, there is a need in the art for electrical drive modules that are designed to be relatively compact.

[0005] This section provides a general summary of the disclosure and is not a disclosure that encompasses its complete scope or all of its features.

[0006] In one form, the present disclosure provides an electric drive module that includes an electric motor, a differential assembly, and a transmission that transmits rotational power between the electric motor and the differential assembly. The transmission has a first reduction gear and a second reduction gear. The first reduction gear includes a drive gear rotatable about a first axis, and a pair of first reduction gears each meshingly engaged with the drive gear and rotatable about a respective second axis. has. The second axes are spaced apart and parallel to the first axis. The second reduction gear 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 of the second reduction gears is in meshing engagement with the driven gear and is also non-rotatably coupled to an associated one of the first reduction gears.

[0007] Further areas of applicability will become apparent from the description provided herein. The descriptions and specific examples in this summary are intended for illustrative purposes only and are not intended to limit the scope of the disclosure.

[0008] The drawings described herein are merely to illustrate selected embodiments, rather than all possible implementations, and are not intended to limit the scope of the disclosure. do not have.

[0009] FIG. 1 is a schematic illustration of an example vehicle having an electric drive module constructed in accordance with the teachings of this disclosure. [0010] FIG. 2 is a partially exploded perspective view of the electric drive module of FIG. 1 showing the electric motor and transmission in more detail. [0011] FIG. 2 is a cross-sectional view of a portion of the electric drive module of FIG. 1 showing the final drive gears and differential assembly of the transmission. [0012] FIG. 2 is a schematic diagram of a portion of the electric drive module of FIG. 1 showing the relative positions of the electric motor, transmission, and differential assembly. [0013] FIG. 2 is a perspective view of a portion of the electric drive module of FIG. 1 showing an optional parking lock mechanism. [0014] FIG. 3 is a plan view of a portion of a parking lock mechanism showing a pawl positioned in engagement with a pair of parking gears to secure an intermediate shaft of an electric drive module. [0015] FIG. 3 is a cross-sectional view 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. [0016] FIG. 3 is a perspective view of a portion of the parking lock mechanism showing the pawl disengaged from a pair of parking gears to allow rotation of the intermediate shaft of the electric drive module. [0017] FIG. 4 is a cross-sectional view 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. [0018] FIG. 2 is a partially cutaway perspective view of the parking lock mechanism. [0019] FIG. 3 is a perspective view of a portion of the parking lock mechanism showing the first side of the cam plate in more detail. [0020] FIG. 3 is a cross-sectional view of a portion of the parking lock mechanism showing the lock actuator in more detail. [0021] FIG. 3 is a perspective view of a portion of a cam plate showing a lock opening formed in a second surface of the cam plate. [0022] FIG. 3 is a perspective view of a portion of the parking lock mechanism showing the plunger in an extended position and the pawl in an engaged position.

[0023] Corresponding reference numerals indicate corresponding parts throughout the several views of the drawings.

[0024] Referring to FIG. 1 of the drawings, an exemplary vehicle having a drive module constructed in accordance with the teachings of the present disclosure is designated generally by the reference numeral 10. Vehicle 10 may include a front or first power transmission 14 and a rear or second power transmission 16 . Front power transmission 14 may include an engine 18 and a transmission 20 and may be configured to drive a front or first set of drive wheels 22 . The rear power transmission 16 may include an electric drive module 24 that may be configured to drive the rear or second set of drive wheels 26 as needed or "on demand." The front wheels 22 are associated in this example with the first power transmission 14 and the rear wheels 26 are associated with the second power transmission 16, although in the alternative the rear wheels are associated with the first power transmission 14. It will be appreciated that the front wheels can be driven by a second power transmission. Additionally, although electric drive module 24 is shown in this example as being configured to drive a second set of drive wheels some of the time, a drive module configured in accordance with the present teachings may The drive (front, rear, or other) of one set of drive wheels (e.g. front wheels or a set of wheels) on a full-time basis, either as the sole means of propulsion or in conjunction with another means of propulsion It will be appreciated that it can also be used to drive wheels. Electric drive module 24 may include a drive unit 30 and a pair of axle shafts 32 .

[0025] Referring to FIGS. 2 and 3, drive unit 30 may include a housing 40, an electric motor 42, a transmission 44, and a differential assembly 46. Housing 40 may define a structure to which other components of drive unit 30 are attached. Housing 40 may be formed from two or more housing elements that may be fixedly coupled together, such as by a plurality of threaded fasteners. Electric motor 42 may be any type of electric motor, such as a permanent magnet motor. Electric motor 42 can be mounted to a flange (not specifically shown) on housing 40 and can be disposed along a first axis of rotation 58 (FIG. 4) and received within housing 40. An output shaft 56 may be included.

[0026] Referring to FIGS. 2 and 4, transmission 44 includes one or more transmission inputs driven by the output shaft of electric motor 42 and a transmission output that drives differential assembly 46. Multiple transmission stages or speed reducers may be provided. Transmission 44 can include one or more transmission stages or reducers that provide multiple levels of gear reduction, and can optionally include one or more multi-speed transmission stages. . Further optionally, a clutch (not shown) may be used between the transmission output and the differential assembly 46 to selectively decouple the differential assembly 46 from the electric motor 42. . In the example provided, the 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. Equipped with Input pinion 60 may be coupled to an output shaft of an electric motor assembly for rotation together. 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 relatively larger pitch diameter than the pitch diameter of the input pinion 60 . Each of the first reduction gears 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 of the compound reduction gears 70 may be disposed on an intermediate shaft or shaft 72 that is parallel to the first axis of rotation 58 and that is mounted to the housing 40 for rotation about an offset second axis of rotation 74. . Each of the intermediate shafts 72 may be supported by a pair of bearings that may be attached to the housing 40. It will also be appreciated that each of the intermediate shafts 72 can be formed as a separate component that can be assembled to a corresponding one of the compound reduction gears 70, or can be integrally formed as a single piece with a corresponding one of the compound reduction gears 70. . The final drive gear 66 may be supported by the housing 40 for rotation about an output axis 76 parallel to and offset from the second axis of rotation 74 and the first axis of rotation 58. In the example provided, input pinion 60, first reduction gear 62, second reduction gear 64, and final drive gear 66 are helical gears, and first reduction gear 62 and second reduction gear 66 are helical gears. The reduction gear 64 is an axis for 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. It rotates in the opposite direction to cancel the directional force. Although transmission 44 is described as using helical gears, it will be appreciated that some or all of these gears may also be configured as spur gears.

[0027] Referring to FIG. 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 the final drive gear 66 for rotation together about the output shaft 76, with each of the differential output members being rotationally coupled to a corresponding one of the axle shafts 32. obtain. In the particular example provided, differential assembly 46 includes a differential case 80 and a differential gear set 82. Differential case 80 can function as a differential input member and can be supported for rotation on housing 40 about output shaft 76 by a pair of bearings 84 . Although bearing 84 is shown as a tapered rolling bearing in the example provided, it will be appreciated that bearing 84 may alternatively be configured as an angular ball bearing, or a ball bearing. Differential gear set 82 may include a pair of differential pinions 90 and a pair of side gears 92. Differential pinion 90 is receivable in differential case 80 and rotatably disposed on a cross pin 94 attached to differential case 80 . Cross pin 94 can extend at least partially through differential case 80 and is oriented perpendicular to output shaft 76 . Side gear 92 is a differential output member in the example provided. Side gear 92 is received within differential case 80 and is rotatable relative to differential case 80 about output shaft 76 . Each of the side gears 92 is meshingly engaged with a differential pinion 90.

[0028] Each of the axial shafts 32 may be non-rotatably but axially slidably engaged to a corresponding one of the side gears 92. In the example provided, each of the axle shafts 32 has a male splined segment 100 that is matingly engaged with an internally splined opening 102 in a corresponding one of the side gears 92. have Each of the axle shafts 32 is configured to transmit rotational power between one of the side gears 92 and an associated one of the wheels of the vehicle.

[0029] The configuration of transmission 44 is advantageous in several aspects. For example, the compound reduction gear 70 may use a relatively high speed electric motor and a relatively small input pinion, which reduces the pitch line speed and thus bends the input pinion 60 and the first reduction gear 62. Positive influence on stress, load capacity and service life. As another example, the load on the final drive gear 66 may be 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). Conversely) the dimensions of the second reduction gear 64 can be reduced. As a result, the gear mounting arrangement between the electric motor 42 and the final drive gear 66 reduces the package size of the drive unit 30, and furthermore, these gears are more compact than known electric drive unit components. It may be relatively small and/or formed from less expensive materials, thereby reducing the cost and mass of the electric drive module 24.

[0030] If desired, a parking lock mechanism (not shown) may be incorporated into the electric drive module 24. 2 and 4, the parking lock mechanism includes a pawl pivotally coupled to the housing 40 and a differential assembly 46 rotatable to the final drive gear 66 or about the output shaft 76. It may be constructed in a conventional manner with a toothed locking wheel rotatably coupled to the component. The pawl can pivot into and out of engagement with the teeth on the toothed locking wheel to prevent rotation of the final drive gear 66 relative to the housing 40. Alternatively, the parking lock mechanism may also be configured to selectively lock intermediate shaft 72 to housing 40. A scissor mechanism or a seesawing lever mechanism may be used to simultaneously lock intermediate shaft 72 to housing 40.

[0031] Referring to FIGS. 5-7, an optional parking lock mechanism 200 may be incorporated into the drive unit 30. Parking lock mechanism 200 can 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 .

[0032] Each of the parking gears 202 may be non-rotatably coupled to an associated one of the intermediate shafts 72 and define a plurality of teeth 216 and a plurality of valleys 218. Each of the valleys 218 is disposed between each pair of teeth 216.

[0033] Pawl 204 includes a pawl body 220 and a pair of engagement teeth 222 disposed at opposite ends of pawl body 220. The pawl body 220 is configured such that the pawl 204 is configured such that each of the engagement teeth 222 engages an associated one of the parking gear 202 (i.e., each engagement tooth 222 is received within a valley 218 of an associated one of the parking gear 202). ), whereby the engagement position (FIG. 6) rotationally locks parking gear 202 and intermediate shaft 72 to housing 40 and each engagement tooth 222 disengages tooth 216 of the associated one of parking gear 202. , the housing 40 of the drive unit 30 such that the pawl 204 can be moved relative to the housing 40 between a disengaged position (FIG. 8) in which it does not block rotation of the parking gear 202 or the intermediate shaft 72. pivotally coupled to. In the example provided, a pivot shaft 226 is attached to the housing 40 and extends through the pawl 204 and into the actuator 210. Pawl 204 is somewhat loosely received on pivot shaft 226 to ensure that the load transmitted through parking lock mechanism 200 is shared equally by parking gear 202 as well as by engagement teeth 222. Pawl 204 may be biased about pivot axis 226 toward a desired rotational position, such as a disengaged position. In the example provided, a helical torsion spring 258 is disposed about pivot axis 226 and engaged with housing 40 and pawl body 220.

[0034] Referring to FIG. 7, each of the plungers 206 can have a plunger body that includes a guide portion 230, a first body portion 232, a transition portion 234, and a second body portion 236. Guide portion 230 is disposed at a first axial end of plunger 206 and may be cylindrical in shape with a first diameter. A first body portion 232 is disposed between the guide portion 230 and the transition portion 234 and can be dimensioned as desired. For example, first body portion 232 may have a generally cylindrical shape having a desired diameter, such as a first diameter. In the example provided, the first body portion 232 is frustoconically shaped, has a base (where the first body portion 232 intersects the guide portion 230), and has a diameter equal to a first diameter. The diameter and outer surface of the first body portion 232 are adjusted between the guide portion 230 and the transition portion 234 by a desired amount, such as from 2 degrees to 30 degrees, preferably from 5 degrees to 15 degrees, of the central axis of the plunger 206. and a relatively shallow cone angle that tapers inward in the direction.

[0035] The second body portion 236 may also be cylindrical in shape, but have a second diameter that is smaller than the first diameter. The transition portion 234 may be frustoconically shaped to taper between the first body portion 232 and the second body portion 236. A spring opening 240 is formed in a first axial end of plunger 206 and is dimensioned to receive a corresponding one of plunger biasing springs 208 therein. In the example provided, each of the plunger biasing springs 208 is a helical coil compression spring, but it will be appreciated that other types of springs may be used in place of or in addition to a helical coil compression spring. .

[0036] Each plunger 206 and plunger biasing spring 208 is received within a plunger opening 244 within housing 40. In the example shown, housing 40 includes a pair of optional plunger bushings 246 that may be formed from a suitable material, such as hardened steel. Each of the plunger bushings 246 defines a plunger opening 244 that is dimensioned to receive the first body portion 232 of a corresponding one of the plungers 206 and a corresponding one of the plunger biasing springs 208. Plunger opening 244 may be a blind hole, such that plunger bushing 246 defines an inner wall 248 against which the end of a corresponding one of plunger biasing springs 208 can abut.

[0037] Each of the plungers 206 is arranged in an extended position (shown in FIGS. 6 and 7), in which the respective first body portion 232 of the plunger 206 is positioned in the rotational path of the pawl body 220, and in a retracted position (shown in FIGS. 8 and 9) along its longitudinal direction relative to the housing 40. Engagement teeth 222 need to be engaged with parking gear 202 to place plunger 206 in the extended position. When the outer surface of first body portion 232 is tapered (frustoconically shaped), plunger biasing spring 208 urges plunger 206 outwardly from plunger opening 244 and 1 such that the outer surface of body portion 232 contacts pawl body 220. When plunger 206 is placed in its retracted position, pawl 204 may be rotated to a disengaged position by torsion spring 258. The pawl 204 can contact the second body portion 236 of one or both of the plungers 206 when the pawl 204 is in the disengaged position.

[0038] Referring to FIGS. 7 and 10, actuator 210 is configured to control movement of plunger 206 between an extended position and a retracted position. Actuator 210 may include 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.

[0039] Referring to FIGS. 7 and 9, each of the cam followers 250 may be placed in line with an associated one of the plungers 206. In the example provided, each of the cam followers 250 is unitarily formed with an associated one of the plungers 206. More specifically, cam follower 250 can be a spherical radius on a second axial end of plunger 206 opposite the first axial end.

[0040] Actuator hub 252 may be fixedly coupled to housing 40 concentrically with the axis about which pawl 204 pivots. In the example provided, actuator hub 252 is a press fit onto pivot shaft 226 . Actuator hub 252 can include a central portion 270, a bearing mount 272, and a lock actuator mount 274. Central portion 270 may define a pivot aperture 280 aligned along a common axis and a threaded aperture 282. A pivot aperture 280 is formed through a first axis side of central portion 270 and is dimensioned to engage pivot axle 226 with a press fit. A threaded opening 282 is formed through a second, axially opposite side of central portion 270 . Bearing mount 272 may be disposed concentrically around center portion 270 and coupled to center portion 270 via flange member 284 or alternatively via a plurality of spokes or webs. Bearing mounting portion 272 includes an outer circumferential surface 286 , a shoulder 288 extending radially outward from the outer circumferential surface, and a retaining ring groove 290 formed in outer circumferential surface 286 . has. The lock actuator mounting portion 274, best seen in FIG. They may be fixedly coupled (eg, integrally formed).

[0041] Referring to FIGS. 5, 7, and 11, the cam plate 254 includes an annular plate 300, a gear portion 302, a torsion spring mounting portion 304, and a pair of sensor targets 306a, 306b. I can do it. Annular plate 300 may be formed from any suitable material. Annular plate 300 may have an inner circumferential surface 310 and may define a pair of cams 312 . Each of the cams 312 is formed into a first surface of the annular plate 300 facing toward the cam follower 250 and plunger 206 . Each of the cams 312 may be a circumferentially extending groove in the first surface of the annular plate 300. Each of the cams 312 has a first circumferential end 320 (FIG. 11) of the groove where the groove is deepest and a second opposite circumferential end 322 (FIG. 11) of the groove where the groove is shallowest. ) can be tapered between. Each of the cam followers 250 is received within a corresponding one of the cams 312 (i.e., grooves), so that rotation of the cam plate 254 about the axis about which the pawl 204 pivots causes a corresponding linear movement of the plunger 206. will occur. More specifically, as shown in FIG. ) allows a corresponding one of the plunger biasing springs 208 to force an associated one of the plungers 206 to its extended position, but as shown in FIG. Positioning the cam follower 250 at the shallowest portion of the associated one (i.e., at the second circumferential end of the groove forming the associated one of the cams 312) causes the corresponding one of the plungers 206 to become plunger-biased. The spring 208 is placed in its retracted position against the biasing of its counterpart. 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 integrally with the annular plate 300 as a single piece. The gear teeth can be arranged around the entire circumference of the annular plate 300, as shown in the example provided, or can also be formed around sectors of the annular plate 300. The torsion spring mount 304 can be a cylindrical post or protrusion that can extend from a second side of the annular plate 300, opposite the first side. Each of sensor targets 306a, 306b can be attached to annular plate 300 and configured to be sensed by sensor 328 (FIG. 10) when cam plate 254 is in a predetermined rotational position relative to housing 40. be done. In the example provided, each of sensor targets 306a, 306b is a magnet and sensor 328 is a Hall effect sensor coupled to housing 40.

[0042] 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 inner bearing race 330 and outer bearing race 332. Inner bearing race 330 is received on outer circumferential surface 286 of bearing mounting portion 272 and may abut shoulder 288 . If desired, the inner bearing raceway 330 may be press fit onto the outer circumferential surface 286 of the bearing mounting portion 272. An outer retaining ring 336 is received within the retaining ring groove 290 and can prevent 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, outer bearing race 332 may be press fit or adhesively bonded to inner circumferential surface 310 of annular plate 300. Alternatively, in examples where the annular plate is formed from a plastic material, the annular plate 300 is formed from an outer ring such that the outer bearing raceway 332 is cohesively joined to the annular plate 300. The bearing raceway 332 may be overmolded.

[0043] Referring to FIGS. 5 and 7, the torsion spring 258 is wound around a central portion 270 and includes a first tang 340 that can act against the actuator hub 252 and a cam. and a second protrusion 342 that can act on the torsion spring mount 304 on the plate 254. In the example provided, first projection 340 is received within a hole formed in flange member 284. Torsion spring 258 may be secured to center portion 270 by washer 346 and by threaded fasteners 348 that thread into threaded openings 282 in center portion 270 . Torsion spring 258 is configured to rotationally bias cam plate 254 about its axis of rotation toward a first rotational position, which is a position that directs the deepest portion of cam 312 toward cam follower 250 . can do. Alternatively, torsion spring 258 may also be configured to rotationally bias cam plate 254 about its axis of rotation to a position where the shallowest portion of cam 312 is directed toward cam follower 250 .

[0044] Referring to FIG. 10, a rotary actuator 260 is configured to control rotation of the cam plate 254 about its axis of rotation between a first rotational position and a second rotational position. Rotary actuator 260 includes a rotary electric motor (not specifically shown) and an output pinion (not specifically shown) that is meshingly engaged with gear teeth of gear portion 302 of cam plate 254. be able to. An electric motor may be coupled (eg, attached) to housing 40. The output pinion may be connected either directly (e.g., the output pinion is attached to the output shaft of the electric motor) or with one or more gears (not shown) disposed in the power transmission path between the electric motor and the output pinion. (not shown) or by an electric motor via a transmission (not shown).

[0045] The electric motor may be operated to drive the cam plate 254 to a second rotational position, such as on the opposite side of the cam 312, such as at the shallowest portion of the cam 312, relative to the cam follower 250. The position may be oriented toward the circumferential end. In some forms, an electric motor may be used to drive cam plate 254 to a desired rotational position and then hold cam plate 254 in this rotational position. Optionally, the cam plate 254 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 may be configured with a stop member (not shown). However, in the example provided, sensor target 306b, sensor 328, and lock actuator 262 are used to maintain cam plate 254 in the desired rotational position such that power to the electric motor does not need to be maintained. Ru.

[0046] The placement of cam plate 254 in each of the first and second rotational positions can be sensed by sensor 328, and sensor 328 can generate a corresponding sensor signal in response. . For example, positioning cam plate 254 in a first rotational position directs sensor target 306a toward sensor 328 such that sensor 328 responsively generates a first sensor signal, but in a second rotational position. Placing cam plate 254 in position directs sensor target 306b toward sensor 328, and sensor 328 generates a second sensor signal in response. In response to receiving the second sensor signal, a controller (not shown) controls lock actuator 262 to engage cam plate 254 and out of the second rotational position ( That is, rotation of the cam plate 254 (due to the moment applied to the cam plate 254 by the torsion spring 258) can be prevented.

[0047] Referring to FIGS. 10 and 12, lock actuator 262 may include any means for preventing rotation of cam plate 254 relative to housing 40. In the example provided, lock actuator 262 includes a solenoid assembly 400 and a lock aperture 402. Solenoid assembly 400 may be coupled to housing 40 and may include a solenoid 410, a solenoid plunger 412, and a solenoid spring 414. Solenoid plunger 412 is movable within solenoid 410 between an extended or locked position and a retracted or unlatched position. Solenoid spring 414 biases solenoid plunger 412 to an extended or locked position. A locking opening 402 is formed in the second surface 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 lock opening 402 has a sidewall 422 that is frustoconically shaped. The profile of the tip 420 of the solenoid plunger 412 and the profile of the sidewall 422 of the lock opening 402 indicate that the solenoid plunger 412 is retracted or unlatched by the torsion spring 258 when power is not provided to the solenoid 410 or the electric motor. drive toward the specified position.

[0048] Referring to FIGS. 5, 7, and 12, during operation of the drive unit 30, when power is not provided to the electric motor or solenoid 410, the torsion spring 258 312 is aligned with the cam follower 250, so that the plunger 206 is disposed in its extended position and the first body portion 232 is aligned with the cam follower 250. , in contact with pawl body 220, pawl 204 is positioned about pivot axis 226 such that engagement teeth 222 engage parking gear 202, as shown in FIG. In this state, the intermediate shaft 72 is effectively non-rotatably locked relative to the housing 40 and, due to the configuration of the parking lock mechanism 200 , the intermediate shaft 72 is engaged by each engagement tooth 222 and each parking gear 202 . The loads will be equal. In this state, sensor target 306a is aligned with sensor 328, and sensor 328 generates a first sensor signal in response. The first sensor signal can be received by a controller (not shown) and used to determine that the cam plate 254 is in a rotational position, which instructs the parking lock mechanism 200 on the intermediate shaft 72. is locked to the housing 40. Solenoid spring 414 of lock actuator 262 biases tip 420 of solenoid plunger 412 against the second surface of annular plate 300 .

[0049] Power can be applied to the electric motor to drive the output pinion and drive the cam plate to unlock the intermediate shaft 72 from the housing 40 so that the intermediate shaft 72 can rotate relative to the housing 40. 254 is rotated around its rotation axis in a first rotation direction. As shown in FIG. 9, rotation of the cam plate 254 in the second rotational direction progressively positions the plunger 206 into a shallower portion of the groove or cam 312 relative to the cam follower 250. Move from the extended position to the 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 engagement tooth 222 causes the plunger 206 to gradually move toward its retracted position. , the parking gear 202 is gradually moved away from the teeth 216 of the parking gear 202. As shown in FIGS. 8 and 9, the arrangement of the pawl 204 in contact with the second body portion 236 of the plunger 206 moves the engagement teeth 222 away from the parking gear 202 and, therefore, on the intermediate shaft. 72 positions it in a freely rotatable position relative to the housing 40. Further rotation of cam plate 254 in the first rotational direction positions cam plate 254 in a second rotational position, which directs sensor target 306b towards sensor 328, so that sensor 328 responds accordingly. , generates 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 hold the solenoid plunger 412 in this position. can. Optionally, the controller may also terminate supply of power to the motor. To force cam plate 254 toward a first rotational position, the moment applied to cam plate 254 by torsion spring 258 forces solenoid plunger 412 out of lock opening 402 when power is applied to solenoid 410. It is not enough to force

[0050] Power to the solenoid 410 is terminated to relock the intermediate shaft 72 relative to the housing 40 and prevent rotation of the intermediate shaft 72 relative to the housing 40. The moment applied to cam plate 254 by torsion spring 258 to force cam plate 254 toward the first rotational position is sufficient to overcome the force applied to solenoid plunger 412 by solenoid spring 414; Force the solenoid plunger 412 out of the lock opening 402. The moment applied to cam plate 254 by torsion spring 258 causes cam plate 254 to rotate in a second direction of rotation that is opposite to the first direction of rotation. Cam plate 254 rotates toward a first rotational position, and once in that position, rotation of cam plate 254 in a second rotational direction causes gear teeth of gear portion 302 to reverse drive the output pinion. be able to. Rotation of the cam plate 254 in the second rotational direction also progressively positions the groove or deeper portion of the cam 312 relative to the cam follower 250 and moves the plunger 206 from its retracted position to its extended position. . Because of the tapered configuration of each transition portion 234 and first body portion 232 of plunger 206, contact between pawl body 220 and plunger 206 is reduced when cam plate 254 is rotated in the second rotational direction. , drives the pawl 204 about the pivot axis 226 so that the engagement tooth 222 rotates toward its respective parking gear 202 . The engagement teeth 222 can move directly into the valleys 218 of the parking gear 202 in situations where the parking gear 202 is oriented to the receiving position. In other situations, movement of the engagement teeth 222 into the valleys 218 may be blocked because the parking gear 202 has a position where each engagement tooth 222 contacts the teeth of an associated one of the parking gears 202. This is because it suits you. However, the plunger biasing spring 208 provides the flexibility to drive the plunger 206 to its extended position when the intermediate shaft 72 rotates slightly (the outer surface of the first body portion 232 engages the pawl 204). and thereby drive engagement teeth 222 into engagement with parking gear 202).

[0051] The foregoing description of embodiments has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit the disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment and, if applicable, are not specifically shown or stated. are also interchangeable and may be used in selected embodiments. This disclosure may also be varied in many ways. Such changes should not be considered a departure from this disclosure, and all such modifications are intended to be included within the scope of this disclosure.

[0051] The foregoing description of embodiments has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit the disclosure. Individual elements or features of a particular embodiment are generally not limited to that particular embodiment and, if applicable, are not specifically shown or stated. are also interchangeable and may be used in selected embodiments. This disclosure may also be varied in many ways. Such changes should not be considered a departure from this disclosure, and all such modifications are intended to be included within the scope of this disclosure.
Below, the invention described in the original claims of the present application will be added.
[1] An electric drive module (24),
an electric motor (42);
a differential assembly (46);
a transmission (44) that transmits rotational power between the electric motor (42) and the differential assembly (46); and the transmission (44) includes a first reduction gear and a second reduction gear. and the first reduction gear has a drive gear (60) and a pair of first reduction gears (62), the drive gear (60) being rotatable about a first axis (58). and each of said first reduction gears (62) is in meshing engagement with said drive gear (60) and is rotatable about a respective second axis (74), wherein said first reduction gear (62) is The axes (74) are spaced apart from each other and parallel to the first axis (58), and the second reducer has a driven gear (66) and a pair of second reduction gears (64). the driven gear (66) is rotatable about a third axis (76) parallel to the first axis (58), and each of the second reduction gears (64) comprises: meshingly engaged with said driven gear (66) and non-rotatably coupled to an associated one of said first reduction gear (62);
an electric drive module (24) having an electric drive module (24);
[2] The electric motor (42) includes an output shaft (56), and the drive gear (60) is coupled to the output shaft (56) for rotation together about the first axis (58). The electric drive module (24) according to [1].
[3] The differential assembly (46) includes a differential input member (80), and the driven gear (66) is configured to rotate the driven gears (66) and The electric drive module (24) according to [2], coupled to a differential input member (80).
[4] The electric drive module (24) according to [3], wherein the differential assembly (46) includes a differential gear set (82).
[5] The electric drive module (24) according to [4], wherein the differential gear set (82) includes a plurality of differential pinions (90) meshingly engaged with a pair of side gears (92). .
[6] The electric drive module (24) according to [5], wherein the pair of differential pinions (90) are attached to a cross pin (94) attached to the differential input member (80).
[7] The differential assembly (46) includes a differential input member (80), and the driven gear (66) is configured to rotate between the driven gears (66) and the gears for common rotation about the third axis (76). The electric drive module (24) according to [1], coupled to a differential input member (80).
[8] The electric drive module (24) according to [7], wherein the differential assembly (46) includes a differential gear set (82).
[9] The electric drive module (24) according to [8], wherein the differential gear set (82) includes a plurality of differential pinions (90) meshingly engaged with a pair of side gears (92). .
[10] The electric drive module (24) according to [9], wherein the pair of differential pinions (90) is attached to a cross pin (94) attached to the differential input member (80).
[11] a housing (40) in which the transmission (44) and the differential assembly (46) are received;
a pair of parking gears (202), each of said parking gears (202) being non-rotatably coupled to an associated one of said second reduction gears (64);
A pawl (204) having a pair of engagement teeth (222), said pawl (204) is coupled to said housing (40), and each of said engagement teeth (222) is connected to said parking gear (202). ) and a disengaged position in which said engagement tooth (222) is disengaged from said parking gear (202);
A pair of plungers (206) movable between a first position and a second position, each of said plungers (206) having a first body portion (232) and said first body portion ( 232), wherein the contact between the first body portion (232) of the plunger (206) and the pawl (204) is positioning the pawl (204) in the engaged position, wherein the second body portion (236) of the plunger (206) contacts the pawl (204); , disposed in the disengaged position;
The electric drive module (24) according to [1], further comprising:
[12] When the pawl (204) is in the engaged position, communication is transmitted between a first of the engagement teeth (222) and a first of the parking gear (202). According to [11], the first load is equal to a second load transmitted between a second of said engagement teeth (222) and a second of said parking gear (202). electric drive module (24).
[13] The pawl (204) is pivotally disposed on a pivot shaft (226), and the fit between the pawl (204) and the pivot shaft (226) is arranged such that the pawl (204) is pivotably arranged on a pivot shaft (226). according to [11], allowing a non-rotating movement of the pawl (204) relative to the pawl (226) so that the loads transferred between the engagement tooth (222) and the parking gear (202) are equal. electric drive module (24).
[14] The electric drive module (24) according to [11], wherein the first body portion (232) of the plunger (206) has a truncated cone shape.
[15] Each plunger (206) further comprises a transition portion (234) disposed between said first body portion (232) and said second body portion (236), said transition portion (234) The electric drive module (24) according to [14], wherein the first body portion (232) has a truncated cone shape, and the cone angle of the first body portion (232) is smaller than the cone angle of the transition portion (234). [16] Further comprising an actuator (210) for controlling movement of the plunger (206) between the first position and the second position, the actuator (210) having an actuator hub (252) and an actuator hub (252). , a cam plate (254), and a plurality of cam followers (250), the actuator hub (252) coupled to the housing (40), and the cam plate (254) configured to rotate about the actuator hub (252). is rotatable and also defines a pair of cams (312), each of said cams (312) having a first circumferential end (320) and a second circumferential end (322). a circumferentially extending groove having a depth that tapers between, each of said cam followers (250) being received in a corresponding one of said cam (312) and an associated groove of said plunger (206). The electric drive module (24) according to [11], which is arranged in line with the electric drive module (24).
[17] The electric drive module (24) according to [16], wherein each of said cam followers (250) is fixedly engaged to said associated one of said plungers (206).
[18] The actuator (210) further includes a torsion spring (258) disposed between the actuator hub (252) and the cam plate (254), and the torsion spring (258) 254) toward a first rotational position relative to the actuator hub (252).
[19] The actuator (210) further includes a lock actuator (262), the lock actuator (262) having a solenoid assembly (400) and a lock opening (402), the solenoid assembly ( 400) has a solenoid plunger (412), the locking opening (402) is formed in the cam plate (254), and the solenoid assembly (400) has a solenoid plunger (412) formed in the cam plate (254); When rotated to a rotational position that aligns the second circumferential end (322) of the cam follower (250) with the cam follower (250), the solenoid plunger (412) is biased into the locking opening (412). The electric drive module (24) of [16], wherein the electric drive module (24) is received within (402) and engages the cam plate (254).
[20] The electric drive module (24) of [16], wherein a bearing (256) is disposed radially between the actuator hub (252) and the cam plate (254).

Claims (20)

an electric drive module (24),
an electric motor (42);
a differential assembly (46);
a transmission (44) that transmits rotational power between the electric motor (42) and the differential assembly (46); and the transmission (44) includes a first reduction gear and a second reduction gear. and the first reduction gear has a drive gear (60) and a pair of first reduction gears (62), the drive gear (60) being rotatable about a first axis (58). and each of said first reduction gears (62) is in meshing engagement with said drive gear (60) and is rotatable about a respective second axis (74), wherein said first reduction gear (62) is The axes (74) are spaced apart from each other and parallel to the first axis (58), and the second reducer has a driven gear (66) and a pair of second reduction gears (64). the driven gear (66) is rotatable about a third axis (76) parallel to the first axis (58), and each of the second reduction gears (64) comprises: meshingly engaged with said driven gear (66) and non-rotatably coupled to an associated one of said first reduction gear (62);
an electric drive module (24) having an electric drive module (24); The electric motor (42) includes an output shaft (56), and the drive gear (60) is coupled to the output shaft (56) for rotation together about the first axis (58). Electric drive module (24) according to claim 1. The differential assembly (46) includes a differential input member (80), and the driven gear (66) connects the differential input member for common rotation about the third axis (76). An electric drive module (24) according to claim 2, coupled to the member (80). The electric drive module (24) of claim 3, wherein the differential assembly (46) includes a differential gear set (82). The electric drive module (24) of claim 4, wherein the differential gear set (82) comprises a plurality of differential pinions (90) in meshing engagement with a pair of side gears (92). The electric drive module (24) of claim 5, wherein the pair of differential pinions (90) are attached to cross pins (94) attached to the differential input member (80). The differential assembly (46) includes a differential input member (80), and the driven gear (66) connects the differential input member for common rotation about the third axis (76). An electric drive module (24) according to claim 1, coupled to a member (80). The electric drive module (24) of claim 7, wherein the differential assembly (46) includes a differential gear set (82). The electric drive module (24) of claim 8, wherein the differential gear set (82) comprises a plurality of differential pinions (90) in meshing engagement with a pair of side gears (92). The electric drive module (24) of claim 9, wherein the pair of differential pinions (90) are attached to cross pins (94) attached to the differential input member (80). a housing (40) in which the transmission (44) and the differential assembly (46) are received;
a pair of parking gears (202), each of said parking gears (202) being non-rotatably coupled to an associated one of said second reduction gears (64);
A pawl (204) having a pair of engagement teeth (222), said pawl (204) is coupled to said housing (40), and each of said engagement teeth (222) is connected to said parking gear (202). ) and a disengaged position in which said engagement tooth (222) is disengaged from said parking gear (202);
A pair of plungers (206) movable between a first position and a second position, each of said plungers (206) having a first body portion (232) and said first body portion ( 232), wherein the contact between the first body portion (232) of the plunger (206) and the pawl (204) is positioning the pawl (204) in the engaged position, wherein the second body portion (236) of the plunger (206) contacts the pawl (204); , disposed in the disengaged position;
The electric drive module (24) of claim 1, further comprising:. When the pawl (204) is in the engaged position, a first Electric drive according to claim 11, wherein the load is equal to a second load transmitted between a second one of the engagement teeth (222) and a second one of the parking gear (202). Module (24). The pawl (204) is pivotally disposed on a pivot axis (226), and the fit between the pawl (204) and the pivot axis (226) is Electric drive according to claim 11, allowing a non-rotating movement of the pawl (204) so that the loads transmitted between the engagement tooth (222) and the parking gear (202) are equal. Module (24). The electric drive module (24) of claim 11, wherein the first body portion (232) of the plunger (206) has a frusto-conical shape. Each plunger (206) further comprises a transition portion (234) disposed between said first body portion (232) and said second body portion (236), said transition portion (234) having a conical shape. 15. The electric drive module (24) of claim 14, having a trapezoidal shape and wherein the cone angle of the first body portion (232) is smaller than the cone angle of the transition portion (234). further comprising an actuator (210) for controlling movement of the plunger (206) between the first position and the second position, the actuator (210) having an actuator hub (252) and a cam plate. (254) and a plurality of cam followers (250), the actuator hub (252) coupled to the housing (40), and the cam plate (254) rotatable about the actuator hub (252). and defining a pair of cams (312), each of said cams (312) tapering between a first circumferential end (320) and a second circumferential end (322). a circumferentially extending groove having a depth, each of said cam followers (250) being received in a corresponding one of said cams (312) and one in said plunger (206); Electric drive modules (24) according to claim 11, arranged in rows. 17. The electric drive module (24) of claim 16, wherein each of said cam followers (250) is fixedly engaged to said associated one of said plungers (206). The actuator (210) further includes a torsion spring (258) disposed between the actuator hub (252) and the cam plate (254), the torsion spring (258) , biasing the actuator hub (252) toward a first rotational position. The actuator (210) further includes a lock actuator (262), the lock actuator (262) having a solenoid assembly (400) and a lock opening (402), the solenoid assembly (400) The solenoid assembly (400) has a solenoid plunger (412), the lock opening (402) is formed in the cam plate (254), and the solenoid assembly (400) has a solenoid plunger (412) formed in the cam plate (254). When rotated to a rotational position that aligns the second circumferential end (322) with the cam follower (250), biasing causes the solenoid plunger (412) to engage the lock opening (402). An electric drive module (24) according to claim 16, for receiving therein and engaging said cam plate (254). The electric drive module (24) of claim 16, wherein a bearing (256) is disposed radially between the actuator hub (252) and the cam plate (254).

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