KR102284202B1 - Electric drive device for vehicles including hydraulic system - Google Patents

Abstract

The present invention relates to an electric drive device including a hydraulic system for a vehicle. The electric drive device including the hydraulic system for the vehicle comprises: a housing; an electric machine which includes a motor shaft rotatably supported by the housing; a first speed reducing unit which includes a first transmission shaft, which can be rotated and driven by the motor shaft, and which is configured to be operated by a hydraulic pressure and to change the rotary driving force of the motor shaft into a predetermined first transmission ratio and transmit it; a second speed reducing unit which includes a second transmission shaft, which can be rotated and driven by the motor shaft, and which is configured to be operated by a hydraulic pressure and to change the rotary driving force of the motor shaft into predetermined second transmission ratio and transmit it; a double clutch unit which includes a first output clutch and a second output clutch, which are respectively configured to receive the rotary driving force of the first transmission shaft or the second transmission shaft, to be operated by a hydraulic pressure, and to selectively rotate and drive one or more of a first output shaft and a second output shaft by the transmitted rotary driving force; and a hydraulic system which supplies oil for generating a hydraulic pressure for operating the first speed reducing unit, the second speed reducing unit, and the double clutch unit. The present invention aims to provide an electric drive device including a hydraulic system for a vehicle, which is able to have a simple structure and control a hydraulic pressure in a stable manner.

Description

Electric drive device for vehicles including hydraulic system

The present invention relates to an electric drive device for transmitting power of an electric machine such as a motor.

An electric machine such as a motor is being used as a power source to replace an existing internal combustion engine or parallel to an internal combustion engine, and a vehicle employing such an electric machine as a power source is called an electric vehicle or a hybrid vehicle.

When a motor is used as a power source, a reduction device for reducing the rotational speed of the rotational power of the motor is required. Since the motor can control the rotational speed, an electric drive implemented as a one-stage reduction device is sometimes used, but an electric drive device capable of two-stage deceleration is introduced to improve efficiency. Such an electric drive device may be configured to implement a torque vectoring function capable of independently adjusting the torque transmitted to both drive wheels.

This electric drive includes clutches for deceleration and torque vectoring, and these clutches are configured to be variably actuated by hydraulic pressure. For this reason, an efficient structure for deceleration and torque vectoring and a hydraulic control system for controlling the same are required. In addition, a lubrication structure capable of effectively supplying oil to parts requiring lubrication and cooling in the electric drive device is required.

US Registered Patent 10,493,978 (2019.12.03.) US Registered Patent 10,753,405 (2020.08.25.) US Patent Publication 2020/0370638 (2020.11.26.)

SUMMARY OF THE INVENTION An object of the present invention is to provide an electric drive device that has a simple structure, is easy to manufacture, and enables stable hydraulic pressure control.

An electric drive apparatus according to an embodiment of the present invention includes a housing, an electric machine including a motor shaft rotatably supported on the housing, and a first shift shaft rotatably driven by the motor shaft, and is operated by hydraulic pressure and a first speed reduction unit configured to shift and transmit the rotational driving force of the motor shaft at a predetermined first speed ratio, and a second speed change shaft that can be rotationally driven by the motor shaft, and is operated by hydraulic pressure to operate the motor A second reduction unit configured to shift and transmit the rotational driving force of the shaft at a predetermined second transmission ratio, the first shifting shaft or the second shifting shaft receives the rotational driving force and is actuated by hydraulic pressure to operate the transmitted rotational driving force A double clutch unit including a first output clutch and a second output clutch each configured to selectively rotationally drive one or more of the first output shaft and the second output shaft by: 2 includes a reduction unit and a hydraulic system for supplying oil to generate hydraulic pressure for operating the double clutch unit.

The first reduction unit operates to selectively engage a first input gear meshed with a driving gear provided on the motor shaft, and a rotationally constrained engagement between the first input gear and the first shift shaft. It may further include a first reduction clutch, wherein the second reduction portion is a second input gear meshed with the driving gear, and the second input gear and the second gear shift shaft is rotatably constrained by the fastening is selectively achieved It may further include a second deceleration clutch that operates so as to reduce the speed. The hydraulic system supplies the oil having an independently controlled hydraulic pressure to independently control the first reduction clutch, the second reduction clutch, the first output clutch, and the second output clutch. The first reduction clutch, the second reduction clutch, the first output clutch, and the second output clutch may be configured to be respectively supplied.

The hydraulic system may include an oil reservoir storing the oil, an oil pump pumping and supplying the oil stored in the oil reservoir, and controlling the pressure of the oil pumped by the oil pump to supply it to the first shift clutch. A first solenoid valve configured to be able to, a second solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the second shift clutch, the pressure of the oil pumped by the oil pump a third solenoid valve configured to supply to the first output clutch by controlling may include

The hydraulic system is configured to detect the pressure of the oil supplied from the first to fourth solenoid valves to the first reduction clutch, the second reduction clutch, the first output clutch, and the second output clutch, respectively. The first to fourth pressure sensors may be further included.

The first output shaft, the second output shaft, and the motor shaft may be arranged coaxially with respect to a first rotation axis. The first shift shaft may define a second rotation shaft parallel to the first rotation shaft, and the second shift shaft may define a third rotation shaft parallel to the first rotation shaft. The first reduction clutch may include a first piston configured to be movable in the direction of the second rotation shaft by hydraulic pressure supplied through the first solenoid valve, and the second reduction clutch may include the second solenoid valve. It may include a second piston configured to be movable in the direction of the third rotation shaft by the hydraulic pressure supplied through the. The first and second output clutches may include third and fourth pistons configured to be respectively movable in the direction of the first rotation shaft by hydraulic pressure supplied through the third and fourth solenoid valves, respectively.

The third and fourth pistons may be configured to receive a force to move toward each other by hydraulic pressure supplied through the third and fourth solenoid valves.

The first reduction clutch includes a first clutch housing configured to rotate together with the first shift shaft, a first clutch hub configured to rotate together with the first input gear, and the first clutch housing and the first clutch hub. A first clutch plate package configured to be selectively connected to be rotationally constrained, and a first force transmission member configured to be moved by movement of the first piston to press the first clutch plate package. there is. The second reduction clutch includes a second clutch housing configured to rotate together with the second shift shaft, a second clutch hub configured to rotate together with the second input gear, and the second clutch housing and the second clutch hub. A second clutch plate package configured to be selectively connected to be rotationally constrained, and a second force transmission member configured to be moved by movement of the second piston to press the second clutch plate package. there is.

The first clutch plate package and the first piston may be disposed on both sides of the first input gear, respectively. The first force transmission member may press the first clutch plate package through a body portion disposed between the first input gear and the first piston, and a through hole protruding from the body portion and formed in the input gear. It may include a protrusion that is formed to be able to. The second clutch plate package and the second piston may be disposed on both sides of the second input gear, respectively. The second force transmitting member may press the second clutch plate package through a body portion disposed between the second input gear and the second piston, and a through hole protruding from the body portion and formed in the input gear. It may include a protrusion that is formed to be able to.

The hydraulic system may be configured to supply a portion of the supplied oil into the housing for lubrication of the first reduction unit and the second reduction unit.

The hydraulic system includes an oil reservoir that stores the oil, an oil pump that pumps and supplies the oil stored in the oil reservoir, and a solenoid that regulates the pressure of the oil pumped by the oil pump and supplies it into the housing. It may include a valve.

The first reduction unit operates to selectively engage a first input gear meshed with a driving gear provided on the motor shaft, and a rotationally constrained engagement between the first input gear and the first shift shaft. It may further include a first reduction clutch. The second reduction unit includes a second input gear meshed with the driving gear, and a second reduction clutch that operates to selectively engage rotationally constrained engagement between the second input gear and the second shift shaft. may include more. The housing may form an oil inlet hole for the inflow of the oil supplied by the solenoid valve, and the oil introduced through the oil inlet hole of the housing may be transferred to the first reduction unit and the second reduction unit. It may further include first and second oil guide members for guiding, respectively, so as to move in different paths.

The first and second shift shafts may be rotatably supported by first and second bearings, respectively. The first and second shift shafts have an insertion hole extending in the longitudinal direction, and at least one oil communication communicating with the insertion hole and communicating with the insertion hole to move oil for lubrication introduced into the insertion hole. Each may include a hole. The first and second oil guide members may be configured to guide the flow of the oil so that the oil introduced through the oil inlet hole moves to the insertion hole and the bearing, respectively.

The first and second oil guide members may each include a pipe part that is at least partially inserted into the insertion hole of the first and second shift shafts, and a bottom plate part extending radially outward from one end of the pipe part. can

The pipe part may form a first oil movement hole communicating with the insertion hole, and the bottom plate part may form a second oil movement hole formed in a portion facing the first and second bearings, respectively.

The bottom plate part may be inserted into a groove formed in the housing and fixed to the housing.

The bottom plate portion may include a flange extending parallel to the direction of the rotation shafts of the first and second shift shafts from the radially outer end, and the flange may be installed to be in close contact with the inner surface of the groove.

The bottom plate may be installed in a state supported by a clasp formed in the groove, and an oil flow space may be formed between the bottom plate and the bottom of the groove.

The first and second speed reduction units may further include first and second sleeve members respectively fastened to the first and second shift shafts, wherein the first and second sleeve members include the first and second shift shafts. It may include at least one oil communication hole respectively communicating with the oil communication hole formed in the shaft.

The at least one oil communication hole formed in the first and second shift shafts is a first oil communication hole and a second oil communication hole respectively formed at different positions along the direction of the rotation shafts of the first and second shift shafts. may include, wherein the at least one oil communication hole formed in the first and second sleeve members includes a third oil communication hole and the second oil communication hole formed at a position corresponding to the first oil communication hole. A fourth oil communication hole formed at a position corresponding to may be provided, respectively.

The third oil communication hole may be formed at a position capable of supplying the oil to the first reduction clutch and the second reduction clutch, respectively, and the fourth oil communication hole may supply the oil to the first and second input gears. It may be formed at a position that can be supplied to a bearing supporting the .

The first reduction clutch includes a first clutch housing each configured to rotate together with the first shift shaft, a first clutch hub each configured to rotate together with the first input gear, and the first clutch housing and the first gearbox. and a first clutch plate package configured to selectively connect the clutch hub to be rotationally constrained. The second reduction clutch includes a second clutch housing each configured to rotate with the second shift shaft, a second clutch hub each configured to rotate with the second input gear, and the second clutch housing and the second clutch housing. and a second clutch plate package configured to selectively connect the clutch hub to be rotationally constrained. The first and second clutch hubs may have oil communication holes formed to be supplied to the first and second clutch plate packages supplied through the third oil communication hole, respectively, and the first and second oil communication holes may be provided, respectively. The clutch housing may each include an oil scattering hole formed to scatter the oil passing through the first and second clutch plate packages to the outside by rotation.

An electric driving device according to another embodiment of the present invention includes a housing, an electric machine including a motor shaft rotatably supported by the housing, and a first shift shaft that can be rotationally driven by the motor shaft, and is operated by hydraulic pressure. and a first speed reduction unit configured to be operated to transmit and transmit the rotational driving force of the motor shaft at a predetermined first speed ratio, and a second speed change shaft capable of being rotationally driven by the motor shaft. A second reduction unit configured to shift and transmit the rotational driving force of the motor shaft at a predetermined second transmission ratio, the first transmission shaft or the second transmission shaft receives the rotational driving force and is operated by hydraulic pressure to rotate the transmitted rotation A double clutch unit including a first output clutch and a second output clutch each configured to selectively rotationally drive at least one of the first output shaft and the second output shaft by a driving force, and the first reduction unit; and a hydraulic system for supplying oil for generating hydraulic pressure for operating the second reduction unit and the double clutch unit, and for lubricating the first and second reduction units. The hydraulic system may include an oil reservoir storing the oil, an oil pump pumping and supplying the oil stored in the oil reservoir, and controlling the pressure of the oil pumped by the oil pump to supply it to the first shift clutch. A first solenoid valve configured to be able to, a second solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the second shift clutch, the pressure of the oil pumped by the oil pump a third solenoid valve configured to supply to the first output clutch by controlling and a fifth solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the housing to lubricate the first and second reduction units.

The hydraulic system controls the pressure of the oil supplied into the first reduction clutch, the second reduction clutch, the first output clutch, the second output clutch, and the housing from the first to fifth solenoid valves, respectively. It may further include first to fifth pressure sensors for detecting.

The electric driving device according to another embodiment of the present invention guides the oil introduced into the housing after passing through the fifth solenoid valve to move to different paths of the first reduction unit and the second reduction unit, respectively. It may further include first and second oil guide members.

The electric drive device according to the present invention has a simple structure and is easy to manufacture, as well as stable hydraulic control.

1 shows a cross-sectional view of an electric drive device according to an embodiment of the present invention.
2 is a perspective view of a first reduction unit of the electric drive device according to an embodiment of the present invention.
FIG. 3 is a cross-sectional view taken along line III-III of FIG. 2 .
4 is an exploded perspective view of a first reduction unit of the electric driving device according to an embodiment of the present invention.
5 is a cross-sectional view illustrating a part of a first reduction unit mounted on a housing of an electric drive device and a lubrication structure according to an embodiment of the present invention.
6 is a perspective view of an oil guide member of a lubrication structure of an electric drive device according to an embodiment of the present invention.
7 is a perspective view of a first reduction unit, a second reduction unit, and a double clutch unit of the electric drive device according to an embodiment of the present invention.
8 is a perspective view of a double clutch unit of an electric drive device according to an embodiment of the present invention.
9 is a cross-sectional view taken along line IX-IX of FIG. 8 .
10 is an exploded perspective view of a double clutch unit of an electric drive device according to an embodiment of the present invention.

With reference to the accompanying drawings, the embodiments of the present invention will be described in detail so that those of ordinary skill in the art to which the present invention pertains can easily implement them. However, the present invention may be embodied in many different forms and is not limited to the described embodiments.

An electric drive device 1 may be configured to drive a driving axle of a vehicle. The electric drive device 1 may be independently used as a device for driving a vehicle, or may be applied to a vehicle using an existing internal combustion engine as a power source and used as a device for driving the vehicle together with the internal combustion engine.

1 shows a cross-sectional view of an electric drive device according to an embodiment of the present invention. 1 is a cross-sectional view taken along a V-shaped cut line connecting three rotation shafts (X1, X2, X3) of the electric drive device according to an embodiment of the present invention. Referring to FIG. 1 , an electric drive device 1 according to an embodiment of the present invention includes a transmission unit 2 that can be rotationally driven by an electric machine such as a motor 10 , and and a double clutch unit 3 which can be rotationally driven by the transmission unit. The double clutch unit may be driven by actuators 4 and 5 respectively. The electric drive device 1 may further include a housing 6 accommodating the shift unit 2 and the double clutch unit 3 .

The motor may include a stator and a rotatable rotor. The rotor is configured to be rotated by application of a current supplied from a battery of the vehicle, and the rotor is connected to the motor shaft 7 in a power transmission manner to rotate the motor shaft 7 . Although not specified in the drawings, the motor shaft 7 may be arranged coaxially with the motor 10 and fastened to the output element of the motor so as to be rotationally driven about the rotation axis X1 by the output element of the motor 10 . can be For example, the motor shaft 7 can be connected to the output element of the motor in the manner of a gear engagement, spline engagement or the like.

Although not shown in FIG. 1 , the housing 6 may further include a housing for accommodating the motor in a right part of the housing 6 shown in FIG. 1 , and the motor shaft 7 is rotatable by a bearing. It may be supported on the housing 6 . The housing 6 may include a first housing 11 and a second housing 12 that are fastened to each other, and the first and second housings 11 and 12 may be fastened to each other using separate fastening members, and may be welded to each other. They may be fastened to each other in such a way.

The rotational motion of the motor shaft 7 is transmitted to the double clutch unit 3 via the shift unit 2 . That is, the rotational driving force of the motor is transmitted to the double clutch unit 3 through the motor shaft 7 and the shift unit 2, and the double clutch unit 3 converts the transmitted torque to the two output shafts 8 and 9. It is structured so that it can be divided into Furthermore, the output shafts 8 and 9 may be respectively connected to side shafts (not shown) which are connected to the driving wheels of the vehicle via a constant velocity joint (not shown).

The motor shaft 7 may be configured as a hollow shaft having a through hole 13 extending in the longitudinal direction, and may be supported on the housing 6 by a bearing 77 so as to be rotatable about the rotation axis X1. there is. One output shaft 8 of the two output shafts 8 , 9 can be arranged coaxially in the through hole 13 of the motor shaft 7 , in this respect the electric drive device according to the embodiment of the present invention (1) may be referred to as a coaxial type.

A drive gear 14 is provided on the motor shaft 7 to rotate together with the motor shaft 7 . The driving gear 14 may extend in the circumferential direction of the motor shaft 7 to have a ring shape, whereby the driving gear 14 rotates about the rotation shaft X1 together with the motor shaft 7 . can do.

According to an embodiment of the present invention, the shift unit 2 includes a first speed reduction portion 15 and a second speed reduction portion 16 . The first reduction unit 15 and the second reduction unit 16 are configured to transmit the rotation of the motor shaft 7 to the double clutch unit 3 by decelerating the rotation of the motor shaft 7 at different rotational speeds, respectively. The first and second reduction units 15 and 16 may implement deceleration through a gear device that reduces rotational speed through tooth engagement of gears.

The first reduction unit 15 includes an input gear 17 , a shift shaft 18 and an output gear 19 as shown in FIGS. 2 to 4 , and likewise, the second reduction unit 16 is also an input gear 21 , a shift shaft 22 and an output gear 23 .

The input gears 17 and 21 are respectively meshed with the driving gear 14 to be rotationally driven by the driving gear 14 . The shift shafts 18 and 22 are disposed in the housing 6 so as to be rotatable about the rotation shafts X2 and X3 extending parallel to the rotation shaft X1 of the motor shaft 7 , respectively. As shown in FIG. 1 , the shift shafts 18 and 22 are inserted into the through-holes formed in the central portions of the input gears 17 and 21 so as to be coaxially arranged with the input gears 17 and 21 . The shift shafts 18 , 22 are rotatably supported on the housing 6 by bearings, for example bevel roller bearings 81 , 82 , 83 , 84 . 1 and 4 , the bevel roller bearing 82 may be supported on the housing 6 by a support ring 87 . Needle bearings 25 and 26 are interposed between the input gears 17 and 21 and the shift shafts 18 and 22 to enable relative rotation of the input gears 17 and 21 and the shift shafts 18 and 22 . 1 and 4 , a sleeve member 88 may be fastened to the shift shaft 18 , and a needle bearing 25 is disposed between the sleeve member 88 and the input gear 17 so that the input gear ( 17 ) may be rotatably supported on the shift shaft 18 .

The input gears 17 , 21 are configured to be selectively rotationally fixed to the shift shafts 18 , 22 via the clutch units 27 , 28 . That is, when the clutch units 27 and 28 are in an operating state, that is, in a state of transmitting rotational force, the rotation of the input gears 17 and 21 is transmitted to the shift shafts 18 and 22 through the clutch units 27 and 28, When the clutch units 27 and 28 are in a state in which they do not transmit rotational force, the input gears 17 and 21 rotate together with the drive gear 14 without rotating the shift shafts 18 and 22 .

The two clutch units 27 and 28 provided in the first and second reduction units 15 and 16, respectively, have the same structure and operate in the same manner. The clutch units 27 , 28 may be configured to be hydraulically operable. 1 to 3, the clutch units 27, 28 include a clutch housing 29, 33, a clutch hub 30, 34, a force transmitting member ( 31 , 35 , pistons 32 , 36 and clutch plate packages 42 , 43 respectively. Further, the clutch units 27 and 28 are disposed between the force transmitting members 31 and 35 and the pistons 32 and 36 and axial bearings 37 and 39 for rotatably supporting the force transmitting members 31 and 35 . and return springs 38 and 89 for returning the force transmitting members 31 and 35 .

The pistons 32 and 36 may have an annular shape and may be movably disposed in the annular hydraulic chambers 40 and 41 formed in the housing 6 to enable hydraulic supply in the axial direction (X2, X3). there is.

The force transmission member 31 transmits the axial force generated by the movement of the piston 32 to the clutch plate package 42 disposed in the clutch housing 29 . As shown in FIG. 4 , the force transmitting member 31 has a ring-shaped disk-shaped body portion 49 facing the piston 32 , and a plurality of protrusions protruding in the axial direction from the inner end of the body portion 49 . (50) may be included.

3 and 4 , the clutch plate package 42 includes a plurality of outer plates 44 and a plurality of inner plates 45 that are alternately arranged in the axial direction, that is, in the direction of the rotation axis X2 . The outer plate 44 is fastened to the clutch housing 29 so that it is axially movable and circumferentially constrained, and the inner plate 45 is fastened to the clutch hub 30 so that it is axially movable and circumferentially constrained. do. Similarly, the clutch package 43 of the second reduction unit 16 also includes a plurality of outer plates and a plurality of inner plates with each other, the outer plate being fastened to the clutch housing 33 and the inner plate fastened to the clutch hub.

The clutch hubs 30 and 34 may be fixedly fastened to the input gear 17 or integrally formed with the input gear 17 so as to rotate about the rotation shaft X2 together with the input gear 17, and the clutch housing ( 29 and 30 may be fixedly fastened to the shift shaft 18 to rotate about the rotation shaft X2 together with the shift shaft 18 .

The plurality of protrusions 50 may be arranged at equal intervals in the circumferential direction on the surface of the body portion 49 , and each protrusion 50 penetrates through an axial through-hole 52 formed in the input gear 17 to the clutch. It extends to a space in which the clutch plate package 42 in the housing 29 is located. The force transmission member 31 is fastened to the input gear 17 to rotate together with the input gear 17 by a protrusion 50 that is fastened to the axial through-hole 52 of the input gear 17 . At the same time, the force transmission member 31 is axially X2 relative to the input gear 17 so as to transmit the axial acting force of the piston 32 to the clutch plate package 42 disposed in the clutch housing 29 . It is configured to be able to move relative to At this time, the protrusion 50 of the force transmission member 31 may be configured to act on a pressure plate 48 axially movably disposed within the clutch housing 29 adjacent the clutch plate package 42 . . Meanwhile, the other side of the clutch plate package 42 may be supported on a support plate 47 supported in the axial direction by an axial bearing 46 supported on the clutch housing 29 .

When hydraulic pressure is supplied to the hydraulic chamber 40, an axial movement of the piston 32 (leftward movement in FIG. 3) occurs, and the axial movement of the piston 32 causes an axial movement of the force transmission member 31, The protrusion 50 of the force transmission member 31 presses the clutch plate package 42 . When the clutch plate package 42 is pressed, the outer plate 44 and the inner plate 45 come into contact with each other so that the clutch hub 30 and the clutch housing 29 rotate together about the rotation shaft X2. Thereby, the shift shaft 18 can rotate together with the input gear 17 .

The return spring 38 returns the force transmission member 31 relative to the input gear 17 away from the clutch plate package 42 . The return spring 38 may be a plate spring that elastically supports the force transmission member 31 with respect to the input gear 17 . In this case, a snap ring 51 for limiting the return behavior of the force transmitting member 31 may be fastened to the protrusion 50 of the force transmitting member 31 . 1 and 3 , the snap ring 51 fastened to the protrusion 50 of the force transmission member 31 comes into contact with the input gear 17 , whereby an additional return operation of the force transmission member 31 is performed. can be blocked.

The output gears 19 , 23 are fastened to the shift shafts 18 , 22 while being rotationally fixed to rotate together with the shift shafts 18 , 22 . The output gears 19 and 23 may be integrally formed as a part of the shift shafts 18 and 22 or may be separately formed and fastened to the shift shafts 18 and 22 . The output gears 19 and 23 may be annular gears formed along the circumferential direction on the outer peripheral surfaces of the shift shafts 18 and 22 and may be integrally formed with the shift shafts 18 and 22 . 1 and 7, the output gears 19 and 23 are two annular gears 54, 55), respectively. Accordingly, the clutch housing 56 serving as an input element of the double clutch unit 3 can be rotated by the rotation of the shift shafts 18 and 23 . At this time, the output gears 19 and 23 of the shift shafts 18 and 22 and the annular gears 54 and 55 of the clutch unit 3 meshed therewith may include helical teeth, and the desired deceleration is achieved. It may be formed to have a tooth ratio.

According to the embodiment of the present invention, it can be seen that two reduction ratios can be implemented through the shift unit 2 . The first reduction unit 15 and the second reduction unit 16 have one shift shaft 18 and 23 and two gear pairs, respectively. The first reduction unit 15 includes a first pair of gears having a first transmission ratio by meshing the drive gear 14 of the motor shaft 7 with the input gear 17 , and the output gear 19 of the shift shaft 18 . ) and the second gear pair having the second transmission ratio by the meshing of the annular gear 54 of the double clutch unit 3 . At this time, the input gear 17 of the first reduction unit 15 has more gear teeth than the drive gear 14 of the motor shaft 7 , so that a first transmission ratio of a predetermined reduction ratio is made, and also the double clutch unit 3 The annular gear 54 of the shift shaft 18 has more gear teeth than the output gear 19 of the shift shaft 18, so that the second transmission ratio of the predetermined reduction ratio is made. As a result, the first reduction unit 15 implements the final transmission ratio by the combination of the first transmission ratio and the second transmission ratio. The second reduction unit 16 also similarly has two transmission ratios, namely, a first transmission ratio by the meshing of the drive gear 14 of the motor shaft 7 and the input gear 21 and the output gear 23 of the transmission shaft 22 . ) and the second transmission ratio by the meshing of the annular gear 55 of the double clutch unit 3 to implement the final transmission ratio. At this time, the input gear 17 of the first reduction unit 15 and the input gear 21 of the second reduction unit 16 may have the same number of gear teeth, and the output gear of the first reduction unit 15 . (19) is an annular shape of the double clutch unit (3) having a smaller number of gear teeth than the output gear (23) of the second reduction part (16) and meshing with the output gear (19) of the first reduction part (15) The gear 54 may have more gear teeth than the annular gear 55 of the double clutch unit 3 meshed with the output gear 23 of the second reduction unit 16 . Due to the number of these gear teeth, the first reduction unit 15 has a larger reduction ratio than that of the second reduction unit 16 . The reduction ratio of the first reduction unit 15 and the second reduction unit 16 may be appropriately set as necessary.

The double clutch unit 3 may include two clutches that can each operate independently. 1 and 7 to 9 , the double clutch unit 3 includes a clutch housing 56 as an input element, and two clutch hubs as an output element, namely first and second clutch hubs 57 and 58 . includes The first clutch hub 57 is fastened to the first output shaft 8 in a rotationally fixed manner, and the first output shaft 8 transmits the applied torque to the side shaft (not shown) through a constant velocity joint (not shown). not available) can be transmitted. Likewise, the second clutch hub 58 may be fastened to the second output shaft 9 in a rotationally fixed manner. The two clutch hubs 57 , 58 may be rotatably supported about an axis of rotation X1 relative to each other by means of an axial bearing 129 . The axial bearing 129 has a ring shape and may be interposed between the clutch hubs 57 and 58 to rotatably support the clutch hubs 57 and 58 relative to each other.

The two annular gears 54 and 55 described above are respectively formed on the outer circumferential surface of the clutch housing 56, and the clutch housing 56 rotates from the shift shafts 18 and 22 via the two annular gears 54 and 55. motive power is transmitted. The clutch housing 56 is supported by clutch bearings 59 and 60 so as to be rotationally driven by the shift shafts 18 and 22 . The clutch bearings 59 and 60 may be implemented as bevel roller bearings configured to be able to introduce an axial force into the housing 6 while supporting it.

Torque may be transmitted from the clutch housing 56 to the first and second clutch hubs 57 and 58 respectively via two clutch plate packages, first and second clutch plate packages 64 and 65 . Each clutch plate package 64 , 65 includes a plurality of outer plates 66 and a plurality of inner plates 67 which are alternately arranged in the axial direction, that is, in the direction of the rotation axis X1 . The outer and inner plates 66 and 67 may each have a ring-shaped disk shape. The outer plate 66 is fastened to the clutch housing 56 to be axially movable and circumferentially constrained, and the inner plate 67 to be axially movable and circumferentially constrained to the clutch hubs 57 and 58. is signed on The first clutch hub 57 is fastened to the first output shaft 8 in a rotationally constrained manner, for example, in a spline-engaged manner, so as to be able to rotationally drive the first output shaft 8, and the second clutch hub ( 58 is fastened to the second output shaft 9 in a rotationally constrained manner, for example in a spline engagement manner, so as to drive the second output shaft 9 to rotate. The double clutch unit 3 can be arranged coaxially with respect to the motor, and the clutch housing 56 is coaxial with the axis of rotation X1 of the motor shaft 7 by means of clutch bearings 59 and 60. 6) can be rotatably supported within. The first and second clutch hubs 57 , 58 , respectively rotating together with the first and second output shafts 8 and 9 , are provided by radial bearings 85 , 86 to be rotatable relative to the clutch housing 56 . It is rotatably supported by the clutch housing 56 .

The clutch housing 56 includes a first clutch housing 61 and a second clutch housing 62 disposed to face each other, and the first and second clutch housings 61 and 62 are connected by fastening bolts 63 to each other. They are fastened to each other and rotate together around the axis of rotation (X1). The fastening bolts 63 extend in a direction parallel to the rotation shaft X1 and may be provided in plurality. Since the two clutch housings 61 and 62 are in close contact with each other in the axial direction and are fastened by the fastening bolt 63, the concentricity of the two clutch housings 61 and 62 may be improved.

The first and second clutch housings 61 , 62 are arranged coaxially with the first and second output shafts 8 , 9 . The first and second clutch housings 61 and 62 are fastened to each other to form a substantially cylindrical space, and the clutch hubs 57 and 58 and the clutch plate packages 64 and 65 are provided with the first and second clutch housings ( 61 and 62).

7 to 10 , the first and second clutch housings 61 and 62 are connected to the output gear 19 of the first reduction unit 15 and the output gear 22 of the second reduction unit 16 . Annular gears 54 and 55 respectively meshed with each other are provided. The two annular gears 54 and 55 are respectively disposed to be coaxial with the rotation shaft X1 and may be formed to have different sizes and/or number of teeth. When the clutch unit 27 of the first reduction unit 15 or the clutch unit 28 of the second reduction unit 16 is in the power transmission state, the annular gears 54, 55 of the two clutch housings 61, 62 ) as one of the rotational power is transmitted, and the first and second clutch housings 61 and 62 fastened to each other to rotate together rotate together by the transmitted rotational power. When one or more of the two clutch plate packages 64 and 65 of the double clutch unit 3 are in the power transmission state with the clutch housings 61 and 62 rotating, the first output shaft 8 and the second output Rotational power is output through one or more of the shafts 9 .

Referring to FIGS. 1 and 9 , the first clutch housing 61 is disposed at the clutch coupling part 68 to which the outer clutch plate 66 is fastened, and at the end of the clutch coupling part 68 (the right end in FIG. 9 ). It may include a cover portion 69 extending radially inward, and further may further include a sleeve portion 70 extending in an axial direction from an inner end of the cover portion 69 . The clutch coupling part 68 and the cover part 69 form a space in which the clutch plate package 64 is disposed, and the sleeve part 70 forms a through hole through which the first output shaft 8 passes. The annular gear 54 meshed with the output gear 19 of the first reduction unit 15 may be formed on the outer peripheral surface of the clutch coupling unit 68 . In addition, the second clutch housing 62 includes a clutch engaging portion 71 to which the outer clutch plate 66 is fastened, and a cover portion extending radially inward from an end (left end in FIG. 9 ) of the clutch engaging portion 71 . It may include 72 , and further may further include a sleeve portion 73 extending in the axial direction from the inner end of the cover portion 72 . The clutch coupling part 71 and the cover part 72 form a space in which the clutch plate package 65 is disposed, and the sleeve part 73 forms a through hole through which the second output shaft 9 passes. The sleeve portion 70 of the first clutch housing 61 and the sleeve portion 73 of the second clutch housing 62 are rotatably supported by clutch bearings 59 and 60, respectively.

The two clutches of the double clutch unit 3 can be operated independently of each other by the two actuators 4 and 5 . To this end, the two actuators 4, 5 can be independently controlled by a hydraulic circuit controlled by a control unit (not shown), whereby via the first clutch plate package 64 the first clutch hub ( 57) and the torque transmitted to the second clutch hub 58 through the second clutch plate package 65 may be variably set independently of each other. Thereby, so-called torque vectoring, which can vary the torque of each drive wheel, is implemented. The two actuators 4 and 5 are respectively disposed axially outside the first and second clutch housings 61 and 62 and are supported in opposite directions along the rotation axis X1 with respect to the structure constituting the housing 6 . can be Since the two actuators 4 and 5 are identical in construction and operation, only one actuator will be described below.

The force transmission members 101 , 102 transmit the axial force generated by the actuators 4 , 5 to the clutch plate packages 64 , 65 disposed within the clutch housings 61 , 62 . The force transmission members 101 , 102 are arranged to be movable in the axial direction X1 by an axial force generated by the actuators 4 , 5 . 9 and 10 , the force transmitting members 101 and 102 are disk-shaped body parts 103 and 104 facing the cover parts 69 and 72 of the clutch housings 61 and 62, and the body part. It may include a plurality of projections (105, 106) formed to protrude from (103, 104) in the axial direction. The plurality of protrusions 105 and 106 may be arranged at equal intervals in the circumferential direction on the surface of the body parts 103 and 104 , and each of the protrusions 105 , 106 includes the cover part 69 of the clutch housing 61 , 62 . , 72 through the axial through-holes 107 and 108 formed in the clutch housings 61 and 62 to extend into the space in which the clutch plate packages 64 and 65 are located. The force transmitting members 101 and 102 are rotated together with the clutch housings 61 and 62 by the protrusions 105 and 106 inserted into the axial through-holes 107 and 108 of the clutch housings 61 and 62 to rotate together. It is fastened to (61, 62). At the same time, the force transmitting members 101 and 102 transmit the axial acting force of the actuators 4 and 5 disposed outside the clutch housings 61 and 62 to the clutch plate packages disposed within the clutch housings 61 and 62. 64 and 65 are configured to be movable relative to the clutch housings 61 and 62 in the axial direction.

The protrusions 105 , 106 of the force transmission members 101 , 102 are axially movably disposed within the clutch housing 61 , 62 adjacent the clutch plate package 64 , 65 , and the pressure plates 109 , 110 . It can be configured to act on. Meanwhile, the reaction plate 111 is installed in the clutch housing 56 to be positioned between the two clutch plate packages 64 and 65 in a state in which the axial movement is blocked. The reaction plate 111 may have a ring-shaped disk shape, and its radially outer end is inserted into the annular groove 112 formed between the first clutch housing 61 and the second clutch housing 62 to block the axial movement. The clutch plate packages 64 and 65 respectively disposed on both sides of the reaction plate 111 are respectively supported by the reaction plate 111 in the axial direction.

The actuators 4 and 5 may be implemented as hydraulically operated actuators, and each of the actuators 4 and 5 includes a piston 113 and 114 movable in the axial direction X1 by hydraulic pressure. The piston indicated by reference numeral 113 is pushed and moved along the axial direction X1 to the left in FIG. 7 by hydraulic pressure, and the piston indicated by reference numeral 114 is moved in the axial direction X1 to the right in FIG. 7 by hydraulic pressure by means of hydraulic pressure. is pushed along The pistons 113 and 114 may have a ring shape as a whole, and may be disposed in the ring-shaped cylinder chambers 115 and 116 formed in the housing 6 as shown in FIG. 1 . The pistons 113 , 114 may be axially supported via support plates 119 , 120 against a retaining ring 117 , 118 that is fastened to the clutch housing 6 . Hydraulic flow paths 121 and 122 for supplying hydraulic pressure to the space between the pistons 113 and 114 and the support plates 119 and 120 may be formed in the clutch housing 6 . The pistons 113 and 114 may move in the axial direction X1 toward the clutch housings 61 and 62 by hydraulic pressure flowing into the space between the support plates 119 and 120 and the pistons 113 and 114 .

On the other hand, the axial bearings 123 and 124 are interposed between the pistons 113 and 114 and the force transmission members 101 and 102 in an axially movable state, and the axial force of the pistons 113 and 114 is It is transmitted to the force transmission member (101, 102) through the directional bearings (123, 124). When the pistons 113 , 114 move toward the clutch housings 61 , 62 , the axial bearings 123 , 124 , and the force transmission members 101 , 102 are pushed by the pistons 113 , 114 together in the axial direction. Move.

When the actuators 4 and 5 do not operate, that is, when hydraulic pressure is not supplied to the space between the pistons 113 and 114 and the support plates 119 and 120, the pistons 113 and 114 are connected to the clutch housing 61, Return springs 127, 128 may be provided for returning away from 62). 1 and 8 , the return springs 127 and 128 apply a force to the pistons 113 and 114 to cause the pistons 113 and 114 to move away from the clutch housings 61 and 62. It elastically supports the pistons 113 , 114 against the housing 6 , more specifically the piston housings 131 , 132 . The pistons 113 and 114 are spaced apart from the force transmitting members 101 and 102 by the elastic restoring force of the return springs 127 and 128 when the actuators 4 and 5 are not in operation to apply an axial force to the force transmitting member 101 . , 102) is not applied. 1 and 7 , the return springs 127 and 128 elastically support the pistons 113 and 114 relative to the piston housings 131 and 132 away from the clutch housings 61 and 62 . It may be a plate spring. 9 shows a state in which the pistons 113 and 114 are pushed by the elastic restoring force of the return springs 127 and 128 and are in close contact with the support plates 119 and 120, and in this state, the pistons 113 and 114 are forced It does not transmit an axial acting force to the transmission members 101 , 102 . On the other hand, when hydraulic pressure is supplied to the space between the support plates 119 and 120 and the pistons 113 and 114 , the pistons 113 and 114 press the return springs 127 and 128 toward the clutch housings 61 and 62 . It moves to move the force transmitting members 101 and 102 . As a result, the force transmission members 101 and 102 press the clutch plate packages 64 and 65 to operate the clutch.

9, the clutch hubs 57 and 58 are outer sleeves 141 and 142, inner sleeves 143 and 144, and a connection part connecting the outer sleeves 141 and 142 and the inner sleeves 143 and 144. 145, 146). The outer sleeves 141 and 142 may extend in parallel with the axial direction X1 to have a hollow cylinder shape, and the clutch plate packages 64 and 65 may be fastened to the outer peripheral surfaces of the outer sleeves 141 and 142 . The inner sleeves 143 and 144 may extend in parallel with the axial direction X1 from the radially inner side of the outer sleeves 141 and 142 to have a hollow cylinder shape. 1 and 9, the inner sleeves (143, 144) form an axial through-hole into which the output shafts (8, 9) are inserted, and the output shafts (8, 8, 9) and spline structures 171 and 172 for spline coupling with each other may be formed. The clutch hubs 57 and 58 and the output shafts 8 and 9 rotate together about the axis of rotation X1 by spline engagement. Radial bearings 85 and 86 rotatably support the outer peripheral surfaces of the inner sleeves 143 and 144 and the clutch housings 61 and 62 relative to each other, whereby the clutch housings 61 and 62 and the clutch hub 57 are rotatably supported. , 58) can be achieved. The connecting portions 145 and 146 extend in a radial direction to connect one end of the outer sleeves 141 and 142 and one end of the inner sleeves 143 and 144 . The connecting portions 145 and 146 of the two clutch hubs 57 and 58 are arranged to face each other, and the axial bearing 129 is arranged to be supported by the two connecting portions 145 and 146, respectively. This allows the two clutch hubs 57 and 58 to rotate relative to each other and to rotate independently.

The pistons 113 and 114 are configured to enable an enlargement of an effective area on which hydraulic pressure acts without increasing the axial and radial lengths of the electric drive device. 8 and 9, the pistons 113 and 114 in the axial direction (X1) and the radially outer edge region of the body parts (151, 153) having an annular shape, and the body parts (151, 153) and It includes a plurality of protrusions 152 and 154 extending side by side. The outer surfaces of the body parts 151 and 153 facing the support plates 119 and 120 in the axial direction are surfaces on which hydraulic pressure acts, and the protrusions 152 and 154 apply the axial force to the bearings 123 and 124. It is a part that performs a function of transmitting the force through the force transmission member (101, 102). Since the protrusions 152 and 154 protrude from the edge regions of the body parts 151 and 153, an effective area of the body parts 151 and 153 on which hydraulic pressure acts can be sufficiently secured.

Referring to FIG. 9 , the piston housing 131 , 132 includes a first axial extension 161 , 162 , a radial extension 163 , 164 and a second axial extension 165 , 166 . . The first axial extensions 161 , 162 and the second axial extensions 165 , 166 respectively extend along the axial direction X1 at different radial positions. As shown in FIG. 9 , the second axial extensions 165 , 166 have a greater radial position than the first axial extensions 161 , 162 , i.e. a position further away from the axial direction X1 in the axial direction. Extending to (X1), the radial extensions 163 and 164 are radially connected to one end of the first axial extension 161 and 162 and one end of the second axial extension 165 and 166. is extended to Referring to FIG. 9 , the first axial extension portions 161 and 162 face radially inner ends of the body portions 151 and 152 of the pistons 113 and 114 , and the radial extension portions 163 and 164 . faces the axial side of the body portions 151 and 152 of the pistons 113 and 114 . and the second axial extensions 165 , 166 face radially inner ends of the projections 152 , 154 of the pistons 113 , 114 . By the shape and arrangement of the pistons 113 and 114 and the piston housings 131 and 132, the radial inner space of the second axial extensions 165 and 166 of the piston housings 131 and 132 can be utilized. , in the embodiment of the present invention, clutch bearings 59 and 60 for supporting the clutch housings 161 and 162 are disposed in this space as shown in FIG. 9 .

More specifically, the second axial extensions 165 , 166 of the piston housings 131 , 132 are disposed radially outwardly than the sleeve portions 70 , 73 of the clutch housings 57 , 58 , while at the same time the piston The second axial extensions 165 , 166 of the housings 131 , 132 and the sleeve portions 70 , 73 of the clutch housings 57 , 58 are arranged to at least partially overlap in the axial direction. Thereby, an annular bearing accommodating space (181, 182) is formed between the second axial extension portions (165, 166) of the piston housings (131, 132) and the sleeve portions (70, 73) of the clutch housings (57, 58). is formed, and clutch bearings 59 and 60 are disposed in the bearing accommodating spaces 181 and 182, respectively. Thereby, as shown in FIG. 9, the clutch bearings 59, 60 are disposed in the radially inner space of the protrusions 153, 154 of the pistons 113, 114 and the force transmission members 101, 102, Accordingly, the radial size of the entire system can be reduced. At this time, the clutch bearings 59 and 60 may be bevel roller bearings, and the bevel roller bearings 59 and 60 include the sleeves 70 and 73 of the clutch housings 57 and 58 and the piston housings 131 and 132 . 2 The cover portions 69 and 70 of the clutch housings 57 and 58 and the radial extensions 163 and 164 of the piston housings 131 and 132 are respectively supported in the radial direction by the axial extensions 165 and 166, respectively. ) can be respectively supported in the axial direction. With this structure, the clutch bearing 59 that supports the clutch housings 57 and 58 without significantly increasing the radial and axial dimensions of the entire device while ensuring a sufficient effective area of the pistons 113 and 114 on which the hydraulic pressure acts is secured. , 60) can be secured.

Also, as shown in Figure 9, the radial inner peripheral surface of the body portion (103, 104) of the force transmission member (101, 102), and the piston (113, 114) and the force transmission member (101, 102) interposed between The radial inner peripheral surfaces of the axial bearings 123 and 124 are disposed to face the outer peripheral surfaces of the second axial extensions 165 and 166 of the piston housings 131 and 132 . A compact structure is obtained by the structure and arrangement of the piston housings 131 and 132, the pistons 113 and 114, the bearings 123 and 124, and the force transmission members 101 and 102.

The two clutches of the clutch unit 27 of the first reduction unit 15, the clutch unit 28 of the second reduction unit 16, and the double clutch unit 3 described above are configured to be actuated by hydraulic pressure. , the hydraulic control system 200 controls the operation of two clutches of the clutch unit 27 of the first reduction unit 15 , the clutch unit 28 of the second reduction unit 16 , and the double clutch unit 3 . configured to generate hydraulic pressure for Specifically, the hydraulic control system 200 includes the piston 32 of the clutch unit 27 , the piston 36 of the clutch unit 28 , the piston 113 of the first actuator 4 , and the second actuator 5 . It works to supply hydraulic pressure that causes a linear movement of the piston 114 of The oil pump 202 may be configured to operate by a control signal from a control unit (not shown).

Referring to FIG. 1 , the hydraulic control system 200 includes an oil reservoir 201 for storing working oil, and an oil pump for pumping and discharging oil stored in the oil reservoir 201 . (202). The oil pump 202 may be an electric oil pump operated in an electric manner, and the electric oil pump may use a motor as a power source and may be used for operation of the clutch units 27 , 28 , 3 through control of the rotation speed of the electric motor. It is configured to variably generate hydraulic pressure and flow rate of oil. The temperature sensor 203 installed in the oil reservoir 201 detects the temperature of the oil stored in the oil reservoir 201 and outputs a corresponding signal.

The working oil pumped by the oil pump 202 is supplied through the oil supply passage 301 . A check valve 204 for preventing a reverse flow of the working oil may be installed in the oil passage 301 . The check valve 204 is configured to prevent a backflow of the working oil discharged from the oil pump 202 .

A relief valve 205 may be installed in the oil return passage 302 connecting the oil supply passage 301 and the oil reservoir 201 . The relief valve 205 is configured to form a flow path through which oil is returned to the oil reservoir 201 through the oil return flow path 302 when the pressure of the oil in the oil supply flow passage 301 reaches a predetermined pressure, and thus It serves to prevent the pressure of the oil in the oil supply passage 301 from being excessively increased by this.

An accumulator 206 may be installed in the oil passage 303 connected to the oil supply passage 301 . The accumulator 206 functions to accumulate hydraulic energy by storing a part of the working oil supplied through the oil supply passage 301 . In addition, the accumulator 206 reduces the pulsation of the oil pump 202 and functions to supplement the supply oil flow rate during shifting. Meanwhile, a flow path 304 for supplying oil for lubrication as a component requiring lubrication may be connected to the oil supply flow path 301 .

The pumped working oil flows through the oil supply passage 301 into four clutch units, namely, the clutch unit 27 of the first reduction unit 15 , the clutch unit 28 of the second reduction unit 16 , and the double clutch unit It is supplied to the four solenoid valves (211, 213, 221, 223) that operate to supply the working oil to the two clutch units of (3), respectively. Each of the solenoid valves 211 , 213 , 221 , and 223 may be a proportional pressure control valve capable of hydraulic control.

The solenoid valve indicated by reference numeral 211 controls the hydraulic pressure of the working oil supplied through the oil supply passage 301 to be supplied to the clutch unit 27 of the first reduction unit 15 through the oil supply passage 311 . do. The solenoid valve indicated by reference numeral 213 controls the hydraulic pressure of the working oil supplied through the oil supply passage 301 to be supplied to the clutch unit 28 of the second reduction unit 16 through the oil supply passage 313 . do. The solenoid valve indicated by reference numeral 221 controls the hydraulic pressure of the working oil supplied through the oil supply passage 301 to be supplied to the first actuator 4 of the double clutch unit 3 through the oil supply passage 321 . do. The solenoid valve indicated by reference numeral 223 controls the hydraulic pressure of the hydraulic oil supplied through the oil supply passage 301 to be supplied to the second actuator 5 of the double clutch unit 3 through the oil supply passage 323 . do. The working oil discharged from the solenoid valves 211 and 213 is supplied to the hydraulic chambers 40 and 41 in which the pistons 32 and 36 are disposed through the oil supply passages 311 and 313, and the pistons 32 and 36 are linear Creates a pressure that causes movement. The working oil discharged from the solenoid valves 221 and 223 is supplied to the cylinder chambers 115 and 116 in which the pistons 113 and 114 are disposed through the oil supply passages 321 and 323, and the pistons 113 and 114 are linear. Creates a pressure that causes movement.

The pressure sensors 212 , 213 , 222 , and 224 are installed in the oil supply passages 311 , 313 , 321 , and 323 to detect the pressure of the hydraulic oil supplied to the clutch units 27 , 28 and 3 . The control unit may perform feedback control so that the operation of the oil pump 202 and the solenoid valve 211, 213, 221, 223 is corrected based on the pressure signal of the pressure sensor 212, 213, 222, 224. there is.

On the other hand, a solenoid valve 241 for supplying the pumped working oil into the housing 6 for lubrication is provided. The solenoid valve 241 is arranged to receive oil from the oil supply passage 301, and the working oil discharged from the solenoid valve 241 is supplied into the housing 6 through the oil supply passages 331 and 332. can At this time, as shown in FIGS. 1 and 5 , the oil supply passages 331 and 332 are formed in one end of the shift shafts 18 and 22 and an oil inlet hole 95 formed in a portion facing the right end in FIG. 1 . ) can be connected to

An oil guide member 90 for guiding the flow of oil introduced through the oil inlet hole 95 is provided. The oil guide member 90 may be fitted into the groove 98 formed in the housing 6 . The oil guide member 90 may be configured to form two oil flow channels that form separate oil flows from each other. 5 and 6 , the oil guide member 90 is formed by extending a pipe portion 92 extending in the direction of the rotational axis X2 and radially outwardly from one end of the pipe portion 92 . and a bottom plate portion 91 that is Accordingly, the tube portion 92 has a hollow cylinder shape, and the bottom plate portion 91 has a circular plate shape from which the center is removed. The pipe part 92 has an oil movement hole 93 extending in the direction of the rotation axis X2, and the bottom plate part 91 also has an oil movement hole 94 extending in a direction parallel to the rotation axis X2. .

The bottom plate portion 91 may have a flange 97 extending in a direction parallel to the rotation shafts X2 and X3 at the edge, and the flange 97 is fitted into the groove 98 of the housing 6 to allow oil A guide member 90 may be fixed to the housing 6 . At this time, a locking protrusion 99 on which the edge region of the bottom plate part 91 is supported may be formed in the groove 98 , and the oil flows between the bottom plate part 91 and the bottom surface of the groove 98 . An oil flow space 96 is formed. 1 and 5 , the bottom plate part 91 faces one end of the shift shaft 18 and the bearing 81 supporting the shift shaft 18 , and the oil movement of the bottom plate part 91 . The hole 94 may be formed in the bottom plate portion 91 to form a passage through which the oil in the oil flow space 96 moves to the bearing 81 . Accordingly, a portion of the oil introduced through the oil inlet hole 95 may be supplied to the bearing 81 through the oil movement hole 94 after filling the oil flow space 96 , and thereby the shift shaft 18 . Lubrication and cooling of the bearing 81 supporting the .

On the other hand, the pipe part 92 is inserted into the insertion hole 501 formed in the shift shaft 18, and at this time, a minute gap exists between the outer circumferential surface of the pipe part 92 and the surface forming the insertion hole 501 to change speed. The shaft 18 is configured to be able to rotate relative to the fixed oil guide member 90 . Referring to FIG. 5 , the pipe part 92 extends by a predetermined distance from the inlet of the insertion hole 501 , and the shift shaft 18 communicates with the insertion hole 501 in an area outside the pipe part 92 . (502, 505) is formed. And the sleeve member 88 fastened to the shift shaft 18 is provided with oil communication holes 503 and 506 respectively communicating with the oil communication holes 502 and 505 of the shift shaft 18 . At this time, the oil communication hole 503 may be disposed to face the inner circumferential surface of the clutch hub 30 of the clutch unit 27 , and a recessed space 507 recessed radially outwardly on the inner circumferential surface of the clutch hub 30 is provided. is formed The recessed space 507 communicates with the oil communication hole 503 of the sleeve member 88 , and the clutch hub 30 has an oil communication hole 504 connecting the inner and outer peripheral surfaces. Thereby, the working oil may be supplied to the clutch package 42 through the oil communication hole 504 .

Another oil communication hole 506 formed in the sleeve member 88 communicates with a space in which a needle bearing 25 for rotatably supporting the input gear 17 is disposed, whereby the working oil flows into the needle bearing 25 . is supplied with

As described above, the oil guide member 90 is provided with two oil passages for supplying working oil, that is, oil passage holes 93 and 94, and lubricated through the two oil passage holes 93 and 94. Oil can be supplied in the direction of the arrow indicated in FIG. 5 to the different points where this is required. In this case, the oil movement hole 93 of the pipe part 92 may be formed to have a larger cross-sectional area than the oil movement hole 94 of the bottom plate part 91 . Due to this, more oil moves through the oil movement hole 93 of the pipe part 92, so that proper lubrication and cooling can be ensured.

On the other hand, the oil supplied to the clutch package 42 in the clutch housing 29 through the oil communication hole 504 is to be scattered into the inner space of the housing 6 through the oil scattering hole 509 formed in the clutch housing 29. can The oil scattering hole 509 may be formed at a position facing the radially outer end of the clutch plate package 42 , and a plurality of oil scattering holes 509 may be formed in the clutch housing 29 along the circumferential direction. there is. The scattered oil may be filled in the lower space in the housing 6 , and the filled oil may be supplied to the oil pump 202 and recirculated. At this time, a temperature sensor 231 for detecting the temperature of the oil filled in the housing 6 may be installed, and the oil temperature sensed by the temperature sensor 231 may be used to estimate the temperature of the electric drive device, It may also be used for feedback control of the oil pump 202 and the solenoid valve 241 . In addition, an air breather 232 may be installed on the upper portion of the housing 6 , and oil vapor or air in the housing 6 may be discharged to the outside through the air breather 232 .

Although the embodiment of the present invention has been described above, the scope of the present invention is not limited thereto, and it is easily changed by a person skilled in the art from the embodiment of the present invention and recognized as equivalent. including all changes and modifications to the scope of

1: Electric drive unit X1, X2, X3: Rotation shaft
2: Shifting unit 3: Double clutch unit
4, 5: Actuator 6: Housing
7: motor shaft 8, 9: output shaft
14: drive gear 15: first reduction unit
16: second reduction unit 17, 21: input gear
18, 19: shift shaft 19, 23: output gear
27, 28: clutch unit 56: clutch housing
61: first clutch housing 62: second clutch housing
57: first clutch hub 58: second clutch hub
64, 65: clutch plate package
101, 102: force transmission member 113, 114: piston
127, 128: return spring 119, 120: support plate
59, 60: clutch bearing 131, 132: piston housing
90: oil guide member 91: bottom plate part
92: pipe part 93, 94: oil transfer hole
95: oil inlet hole 96: oil flow space
201: oil reservoir 202: oil pump
211, 213, 221, 223, 241: solenoid valve
301, 311, 313, 321, 323, 331, 332: oil supply flow path
212, 214, 222, 224: pressure sensor
231: temperature sensor 232: air breather

Claims (24)

housing,
an electric machine including a motor shaft rotatably supported on the housing;
a first reduction unit including a first shift shaft that can be rotationally driven by the motor shaft and configured to be operated by hydraulic pressure to shift and transmit the rotational driving force of the motor shaft at a predetermined first speed ratio;
a second reduction unit including a second shift shaft that can be rotationally driven by the motor shaft and configured to be operated by hydraulic pressure to transmit the rotation driving force of the motor shaft by shifting at a predetermined second speed ratio;
Receive the rotational driving force of the first shift shaft or the second shift shaft and operate by hydraulic pressure to selectively rotationally drive one or more of the first output shaft and the second output shaft by the transmitted rotational driving force, respectively a double clutch unit including a first output clutch and a second output clutch configured to; and
A hydraulic system for supplying oil for generating hydraulic pressure for operating the first reduction unit, the second reduction unit, and the double clutch unit
Electric drive comprising a. In claim 1,
The first reduction unit operates to selectively engage a first input gear meshed with a driving gear provided on the motor shaft, and a rotationally constrained engagement between the first input gear and the first shift shaft. Further comprising a first reduction clutch,
The second reduction unit includes a second input gear meshed with the driving gear, and a second reduction clutch that operates to selectively engage rotationally constrained engagement between the second input gear and the second shift shaft. including more,
The hydraulic system supplies the oil having an independently controlled hydraulic pressure to independently control the first reduction clutch, the second reduction clutch, the first output clutch, and the second output clutch. configured to be supplied to the first reduction clutch, the second reduction clutch, the first output clutch, and the second output clutch, respectively.
electric drive. In claim 2,
the hydraulic system
an oil reservoir for storing the oil;
an oil pump pumping and supplying the oil stored in the oil reservoir;
a first solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the first shift clutch;
a second solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the second shift clutch;
a third solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the first output clutch; and
a fourth solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the second output clutch
Electric drive comprising a. In claim 3,
The hydraulic system is configured to detect the pressure of the oil supplied from the first to fourth solenoid valves to the first reduction clutch, the second reduction clutch, the first output clutch, and the second output clutch, respectively. The electric drive device further comprising 1 to 4 pressure sensors. In claim 3,
The first output shaft, the second output shaft and the motor shaft are arranged coaxially about a first rotational axis,
The first shift shaft defines a second rotation axis parallel to the first rotation axis,
The second shift shaft defines a third rotation axis parallel to the first rotation axis,
The first reduction clutch includes a first piston configured to be movable in the direction of the second rotational shaft by hydraulic pressure supplied through the first solenoid valve,
The second reduction clutch includes a second piston configured to be movable in the direction of the third rotational shaft by hydraulic pressure supplied through the second solenoid valve,
The first and second output clutches include third and fourth pistons configured to be respectively movable in the direction of the first rotational shaft by hydraulic pressure supplied through the third and fourth solenoid valves, respectively
electric drive. In claim 5,
The third and fourth pistons are configured to receive a force to move in a direction closer to each other by hydraulic pressure supplied through the third and fourth solenoid valves. In claim 5,
The first reduction clutch includes a first clutch housing configured to rotate together with the first shift shaft, a first clutch hub configured to rotate together with the first input gear, and the first clutch housing and the first clutch hub. A first clutch plate package configured to be selectively connected to be rotationally constrained, and a first force transmission member configured to be moved by movement of the first piston to press the first clutch plate package,
The second reduction clutch includes a second clutch housing configured to rotate together with the second shift shaft, a second clutch hub configured to rotate together with the second input gear, and the second clutch housing and the second clutch hub. A second clutch plate package configured to be selectively connected to be rotationally constrained, and a second force transmission member configured to be moved by movement of the second piston to press the second clutch plate package.
electric drive. In claim 7,
The first clutch plate package and the first piston are respectively disposed on both sides of the first input gear,
The first force transmission member may press the first clutch plate package through a body portion disposed between the first input gear and the first piston, and a through hole protruding from the body portion and formed in the input gear. It includes a protrusion formed to be able to
The second clutch plate package and the second piston are respectively disposed on both sides of the second input gear,
The second force transmitting member may press the second clutch plate package through a body portion disposed between the second input gear and the second piston, and a through hole protruding from the body portion and formed in the input gear. including a protrusion formed so that
electric drive. In claim 1,
and the hydraulic system is configured to supply a portion of the supplied oil into the housing for lubrication of the first reduction unit and the second reduction unit. In claim 9,
the hydraulic system
an oil reservoir for storing the oil;
an oil pump for pumping and supplying the oil stored in the oil reservoir, and
A solenoid valve that regulates the pressure of the oil pumped by the oil pump and supplies it into the housing
Electric drive comprising a. In claim 10,
The first reduction unit operates to selectively engage a first input gear meshed with a driving gear provided on the motor shaft, and a rotationally constrained engagement between the first input gear and the first shift shaft. Further comprising a first reduction clutch,
The second reduction unit includes a second input gear meshed with the driving gear, and a second reduction clutch that operates to selectively engage rotationally constrained engagement between the second input gear and the second shift shaft. including more,
The housing forms an oil inlet hole for the inflow of the oil supplied by the solenoid valve,
and first and second oil guide members respectively guiding the oil introduced through the oil inlet hole of the housing to move in different paths of the first and second reduction units. . In claim 11,
The first and second shift shafts are rotatably supported by first and second bearings, respectively;
The first and second shift shafts have an insertion hole extending in the longitudinal direction, and at least one oil communication communicating with the insertion hole and communicating with the insertion hole to move oil for lubrication introduced into the insertion hole. each of the halls,
The first and second oil guide members are each configured to guide the flow of the oil so that the oil introduced through the oil inlet hole moves to the insertion hole and the bearing, respectively.
electric drive. In claim 12,
The first and second oil guide members are
a tube portion which is respectively at least partially inserted into the insertion hole of the first and second shift shafts, and
A bottom plate portion extending radially outward from one end of the pipe portion
Each included electric drive unit. In claim 13,
The pipe portion forms a first oil movement hole communicating with the insertion hole,
The bottom plate part forms a second oil movement hole formed in a portion facing each of the first and second bearings.
electric drive. In claim 13,
The bottom plate part is fitted into a groove formed in the housing and is fixed to the housing. In claim 15,
The bottom plate portion has a flange extending parallel to the direction of the rotation shaft of the first and second shift shafts at the radially outer end,
The flange is installed to be in close contact with the inner surface of the groove.
electric drive. 17. In claim 16,
The bottom plate part is installed in a state supported by the locking jaw formed in the groove,
An oil flow space is formed between the bottom plate part and the bottom of the groove.
electric drive. In claim 12,
The first and second reduction units further include first and second sleeve members respectively fastened to the first and second shift shafts,
wherein the first and second sleeve members include at least one oil communication hole respectively communicating with the oil communication hole formed in the first and second shift shafts.
electric drive. In claim 18,
The at least one oil communication hole formed in the first and second shift shafts is a first oil communication hole and a second oil communication hole respectively formed at different positions along the direction of the rotation shafts of the first and second shift shafts. including,
The at least one oil communication hole formed in the first and second sleeve members is formed at a position corresponding to the third oil communication hole and the second oil communication hole formed at a position corresponding to the first oil communication hole each having a fourth oil communication hole
electric drive. In paragraph 19,
The third oil communication hole is formed at a position capable of supplying the oil to the first reduction clutch and the second reduction clutch, respectively;
The fourth oil communication hole is formed at a position capable of supplying the oil to the bearings supporting the first and second input gears, respectively.
electric drive. 21. In claim 20,
The first reduction clutch includes a first clutch housing each configured to rotate together with the first shift shaft, a first clutch hub each configured to rotate together with the first input gear, and the first clutch housing and the first gearbox. a first clutch plate package configured to selectively and rotationally constrain the clutch hub;
The second reduction clutch includes a second clutch housing each configured to rotate with the second shift shaft, a second clutch hub each configured to rotate with the second input gear, and the second clutch housing and the second clutch housing. a second clutch plate package configured to selectively and rotationally constrain the clutch hub;
The first and second clutch hubs each have oil communication holes formed to be supplied to the first and second clutch plate packages supplied through the third oil communication hole, respectively;
The first and second clutch housings each have oil scattering holes formed to scatter the oil that has passed through the first and second clutch plate packages to the outside by rotation.
electric drive. housing,
an electric machine including a motor shaft rotatably supported on the housing;
a first reduction unit including a first shift shaft that can be rotationally driven by the motor shaft and configured to be operated by hydraulic pressure to transmit the rotation driving force of the motor shaft by shifting at a predetermined first speed ratio;
a second reduction unit including a second shift shaft that can be rotationally driven by the motor shaft and configured to be operated by hydraulic pressure to shift and transmit the rotation driving force of the motor shaft at a predetermined second speed ratio;
Receive the rotational driving force of the first shift shaft or the second shift shaft and operate by hydraulic pressure to selectively rotationally drive one or more of the first output shaft and the second output shaft by the transmitted rotational driving force, respectively a double clutch unit comprising a first output clutch and a second output clutch configured to; and
A hydraulic system for supplying oil for generating hydraulic pressure for operating the first reduction unit, the second reduction unit, and the double clutch unit and for lubricating the first and second reduction units
including,
the hydraulic system
an oil reservoir for storing the oil;
an oil pump pumping and supplying the oil stored in the oil reservoir;
a first solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the first shift clutch;
a second solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the second shift clutch;
a third solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the first output clutch;
a fourth solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the second output clutch, and
a fifth solenoid valve configured to control the pressure of the oil pumped by the oil pump and supply it to the housing to lubricate the first and second reduction units
Electric drive comprising a. 23. In claim 22,
The hydraulic system controls the pressure of the oil supplied into the first reduction clutch, the second reduction clutch, the first output clutch, the second output clutch, and the housing from the first to fifth solenoid valves, respectively. The electric drive device further comprising first to fifth pressure sensors for detecting. In claim 23,
Further comprising first and second oil guide members for guiding the oil introduced into the housing after passing through the fifth solenoid valve to move to different paths of the first reduction unit and the second reduction unit, respectively electric drive.

Images