CN216715148U - Transfer case and vehicle - Google Patents

Abstract

The utility model relates to the technical field of vehicle transmission devices, in particular to a transfer case and a vehicle. The transfer case comprises a first output shaft, a second output shaft, a transmission mechanism, a clutch assembly, a cam mechanism and an actuating mechanism; the transmission mechanism is connected with the first output shaft, the second output shaft and the clutch assembly and is used for transmitting the torque of the first output shaft to the second output shaft; the clutch assembly and the cam mechanism are arranged on a first output shaft, the first output shaft is arranged in parallel with the actuating mechanism, and the cam mechanism is positioned on one side of the actuating mechanism; the actuating mechanism is used for pushing the cam mechanism to rotate around a first direction, and the first direction rotation of the cam mechanism controls the engagement degree of the clutch assembly so as to control the torque distribution between the first output shaft and the second output shaft. The space fit size of the cam mechanism can be reduced by positioning the cam mechanism on one side of the actuating mechanism in the transfer case, so that the occupied space can be reduced, and the internal structure of the transfer case is more compact.

Description

Transfer case and vehicle

Technical Field

The utility model relates to the technical field of vehicle transmission devices, in particular to a transfer case and a vehicle.

Background

Vehicles are mainly used for carrying people and/or goods, and have been widely used with rapid development of economy and technology. Moreover, the requirements of people on the vehicle are not only limited on simple travel, but also have higher pursuits on comfort, driving operability and dynamic property, the vehicle is required to have good fuel economy on urban roads, and strong power on far-going cross-country, so that more vehicle types begin to develop from two-drive to four-drive in the past, and a transfer case is used in the vehicle for realizing the four-drive function of the vehicle. The transfer case has a plurality of types, which can be divided into three main types according to structure and function, namely a real-time transfer case, a time-sharing transfer case and a full-time transfer case. The time-sharing transfer case needs a driver to manually switch a four-wheel drive mode according to different vehicle conditions, so that the time-sharing transfer case is good in economy and complex in operation; the full-time transfer case has no two-drive mode, has good driving controllability, but has poor economy; the timely transfer case combines the advantages of the time-sharing transfer case and the full-time transfer case, the vehicle can automatically switch two-drive and four-drive according to vehicle conditions, the pressing force of the clutch can be controlled under different vehicle conditions to match and output different torques, the fuel economy is improved, the mechanical hard lock can be connected when the vehicle is off-road, the applicable road conditions are wider, and therefore the occupied proportion of the timely transfer case is increased day by day.

The timely transfer case usually uses a wet clutch to realize the AUTO mode of automatically switching two-drive four-drive, the clutch can be automatically switched on and off by a motor, and the motor-controlled clutch has high response speed but has the defect of large occupied space.

SUMMERY OF THE UTILITY MODEL

In view of the above, the present invention is directed to a transfer case, so as to solve or partially solve the problem that the existing timely transfer case occupies a large space.

In order to achieve the purpose, the technical scheme of the utility model is realized as follows:

a transfer case comprises a first output shaft, a second output shaft, a transmission mechanism, a clutch assembly, a cam mechanism and an actuating mechanism;

the transmission mechanism is connected with the first output shaft, the second output shaft and the clutch assembly and is used for transmitting the torque of the first output shaft to the second output shaft;

the clutch assembly and the cam mechanism are arranged on the first output shaft, the first output shaft is arranged in parallel with the actuating mechanism, and the cam mechanism is positioned on one side of the actuating mechanism;

the actuating mechanism is used for pushing the cam mechanism to rotate around a first direction, and the first direction rotation of the cam mechanism controls the engagement degree of the clutch assembly so as to control the torque distribution between the first output shaft and the second output shaft.

Furthermore, the cam mechanism comprises a first cam disc and a second cam disc, the first cam disc and the second cam disc are arranged oppositely, a central shaft hole of the first cam disc is rotationally sleeved on a boss along a central shaft hole of the second cam disc, and the second cam disc is rotationally sleeved on the first output shaft;

the actuating mechanism is used for pushing the first cam disc to rotate in the first direction, so that the first cam disc moves axially along the first output shaft to control the engagement degree of the clutch assembly.

Furthermore, a first gradually-changing groove is formed in the disc surface of the first cam disc, a second gradually-changing groove is formed in the disc surface of the second cam disc, the first gradually-changing groove and the second gradually-changing groove are arranged in a reverse mode, and the first gradually-changing groove and the second gradually-changing groove are both in a water-drop shape;

the cam mechanism further comprises a ball body, and in an initial state of the first cam plate, the ball body is positioned in a large area in two side walls of the first gradual change groove and a large area in two side walls of the second gradual change groove;

the actuating mechanism pushes the first cam disc to rotate in the first direction, the ball body moves towards a small area of the two side walls along the first gradually-changing groove, and moves towards a small area of the two side walls along the second gradually-changing groove, and the ball body enables the first cam disc to move axially along the first output shaft.

Furthermore, the end part, far away from the first output shaft, of the first cam plate is a cam driving end, and the cam driving end is used for being connected with the actuating mechanism and driven by the actuating mechanism to rotate so as to enable the first cam plate to rotate;

the end part, far away from the first output shaft, of the second cam disc is a cam limiting end, and when the first cam disc rotates in the first direction, the cam limiting end is used for limiting the position of the second cam disc;

the cam driving end and the cam limiting end are both located on one side of the actuating mechanism.

Further, the actuating mechanism comprises a shift shaft and a cam, the cam is coaxially and fixedly connected with the shift shaft, the outer peripheral surface of the cam is suitable for being in contact connection with the cam driving end, and the cam rotates to push the first cam disc to rotate.

Further, around the first direction, a first arc section, a second arc section and a third arc section which are connected end to end are formed on the periphery of the cam;

the first arc section is of an arc structure which is sunken towards the inside of the cam;

the second section of arc part is of an arc structure protruding outwards the cam and is connected by a plurality of groups of arcs which are tangent and have gradually larger radius;

the third arc section is of an arc structure which is sunken towards the inside of the cam.

Further, the cam mechanism further comprises a contact bearing, and the cam driving end is in contact connection with the cam through the contact bearing.

Furthermore, the actuating mechanism further comprises a worm wheel, a worm and an actuating motor, an output shaft of the actuating motor is in transmission connection with the worm, the worm is in meshing transmission connection with the worm wheel, and the worm wheel is sleeved on the gear shifting shaft in an interference manner and the cam is sleeved on the extending portion of the central shaft hole of the worm wheel in an interference manner.

Further, the transfer case further includes an input shaft, a planetary gear mechanism provided on the input shaft, a power switching member and a lock sleeve provided on the first output shaft, the input shaft being formed as a sun gear of the planetary gear mechanism;

the power switching member enables the first output shaft to be selectively engaged with the input shaft or a carrier of the planetary gear mechanism through the actuator so as to enable switching of high and low gears, or enables the locking sleeve to be engaged with the transmission mechanism through the actuator so as to enable locking of the first output shaft with the second output shaft.

Compared with the prior art, the transfer case has the following advantages:

when the transfer case works, the actuating mechanism pushes the cam mechanism to rotate around the first direction, the first direction rotation of the cam mechanism controls the engagement degree of the clutch assembly, and when the clutch assembly is engaged, the transmission mechanism transmits the torque of the first output shaft to the second output shaft, so that the torque distribution between the first output shaft and the second output shaft is realized. The cam mechanism is positioned on one side of the actuating mechanism, so that the space fit size of the cam mechanism can be reduced, the occupied space can be reduced, and the internal structure of the transfer case is more compact.

Another object of the present invention is to provide a vehicle to solve or partially solve the problem of the timely transfer case used in the existing vehicle having a large occupied space.

In order to achieve the purpose, the technical scheme of the utility model is realized as follows:

a vehicle comprises the transfer case.

The vehicle has the same advantages as the transfer case described above over the prior art and will not be described in detail here.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the utility model and, together with the description, serve to explain the utility model and not to limit the utility model. In the drawings:

fig. 1 is a schematic structural diagram of a transfer case according to an embodiment of the utility model;

fig. 2 is a schematic structural view of the transfer case at a first output shaft and a shift shaft according to the embodiment of the utility model;

FIG. 3 is a schematic view of the cam mechanism of the present invention in a housing;

FIG. 4 is a schematic structural view of the cam mechanism of the present invention;

FIG. 5 is a schematic illustration of the configuration of a first cam plate of the present invention;

FIG. 6 is a schematic illustration of the construction of a second cam plate according to the present invention;

FIG. 7 is a schematic view of the cam of the present invention;

fig. 8 is a schematic structural diagram of the actuator of the present invention.

Description of reference numerals:

1-a first output shaft; 2-a second output shaft;

31-a drive sprocket; 32-a driven sprocket; 33-a chain;

41-clutch outer hub; 42-clutch inner hub; 43-clutch pressure plate;

51-a first cam plate; 511-a first tapering groove; 512-cam drive end; 52-second cam plate; 521-a second tapered slot; 522-cam limit end; 53-sphere; 54-contact bearing;

61-shift shaft; 62-a cam; 621-first arc section; 622-second arc section; 623-a third arc section; 63-a worm gear; 66-a shift fork; 671-rotating hub; 672-a support plate; 673-energy storage spring; 68-a shifting block;

7-an input shaft; 8-a planetary gear mechanism; 9-a power switching member; 91-a connecting part; 10-a locking sleeve; 11-shell.

Detailed Description

It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.

In addition, the front and rear mentioned in the embodiment of the utility model refer to the front and rear with respect to the forward direction of the vehicle.

The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.

In the prior art, a gear shifting actuating mechanism of the transfer case adopts a multi-stage gear to lift and twist a driving clutch to be connected and disconnected, so that the defects of large occupied space and higher cost are overcome, and the difficulty in developing initial products on the space arrangement of the whole car is increased. The gear shifting actuating mechanism also adopts the rotating hub molded lines to realize the connection and disconnection of the clutch at the high-low gear side so as to switch the high-low gear, but because the binding force required by the clutch is large, the rotating hub molded lines are easy to block, parts are easy to deform, the processing difficulty and the cost are improved accordingly, and the gear shifting actuating mechanism is not suitable for transverse extension.

Referring to fig. 1, an embodiment of the present application provides a transfer case, which includes a first output shaft 1, a second output shaft 2, a transmission mechanism, a clutch assembly, a cam mechanism, and an actuating mechanism; the transmission mechanism is connected with the first output shaft 1, the second output shaft 2 and the clutch assembly and is used for transmitting the torque of the first output shaft 1 to the second output shaft 2; the clutch assembly and the cam mechanism are arranged on the first output shaft 1, the first output shaft 1 is arranged in parallel with the actuating mechanism, and the cam mechanism is positioned on one side of the actuating mechanism; the actuator is used to urge the cam mechanism to rotate in a first direction, which controls the degree of engagement of the clutch assembly to enable control of the torque distribution between the first output shaft 1 and the second output shaft 2.

Specifically, the transfer case is a gear train, and power is transmitted to each drive axle through the first output shaft 1 and the second output shaft 2, for example, power is transmitted to the first output shaft 1 to the rear axle, and power is transmitted to the second output shaft 2 to the front axle.

Wherein the first direction is the direction indicated by arrow B in fig. 3.

When the transfer case works, the actuating mechanism pushes the cam mechanism to rotate around the first direction, the first direction rotation of the cam mechanism controls the engagement degree of the clutch assembly, and when the clutch assembly is engaged, the transmission mechanism transmits the torque of the first output shaft 1 to the second output shaft 2, so that the torque distribution between the first output shaft 1 and the second output shaft 2 is realized. The cam mechanism is positioned on one side of the actuating mechanism, so that the space fit size of the cam mechanism can be reduced, the occupied space can be reduced, and the internal structure of the transfer case is more compact.

Referring to fig. 1 to 4, in one embodiment, the cam mechanism includes a first cam plate 51 and a second cam plate 52, the first cam plate 51 and the second cam plate 52 are arranged oppositely, a central shaft hole of the first cam plate 51 is rotatably sleeved on a boss along the central shaft hole of the second cam plate 52, and the second cam plate 52 is rotatably sleeved on the first output shaft 1; the actuator is used to urge the first cam plate 51 to rotate in a first direction to move the first cam plate 51 axially along the first output shaft 1 to control the degree of engagement of the clutch assembly.

First cam plate 51 and second cam plate 52 are disposed on one side of the actuator, and the occupied space can be reduced by reducing the overlapping angle of first cam plate 51 and second cam plate 52 in consideration of the rotation angle of first cam plate 51 and the dimensional fit. As shown in fig. 4, the coincidence angle is an angle shown by a.

In practical application, the central shaft hole of the second cam disc 52 is rotatably sleeved on the first output shaft 1 through a needle bearing, the central shaft hole of the first cam disc 51 is rotatably sleeved on a boss along the central shaft hole of the second cam disc 52, and the first cam disc 51 can rotate relative to the second cam disc 52 and can axially move along the first output shaft 1.

Referring to fig. 5 and 6, in one embodiment, a first tapered groove 511 is formed on the disc surface of the first cam plate 51, a second tapered groove 521 is formed on the disc surface of the second cam plate 52, the first tapered groove 511 and the second tapered groove 521 are arranged in opposite directions, and the first tapered groove 511 and the second tapered groove 521 are both in a drop shape; the cam mechanism further includes a spherical body 53, and in the initial state of the first cam plate 51, the spherical body 53 is located in a region of the first gradually-varying groove 511 having a large size and a region of the second gradually-varying groove 521 having a large size; the actuator pushes the first cam plate 51 to rotate in the first direction, and the ball 53 moves along the first gradually-varying groove 511 toward the smaller of the two side walls and along the second gradually-varying groove 521 toward the smaller of the two side walls, and the ball 53 moves the first cam plate 51 in the axial direction of the first output shaft 1.

The initial state of the first cam plate 51 is a state in which the first cam plate 51 is not rotated and not axially moved.

It is understood that, in practical applications, in order to achieve different use requirements, the number of the first gradually-changing groove 511 and the second gradually-changing groove 521 can be adjusted accordingly, as shown in fig. 5 and 6, 5 first gradually-changing grooves 511 and 5 second gradually-changing grooves 521 are provided, and the number of the first gradually-changing groove 511 and the second gradually-changing groove 521 provided in the embodiment of the present invention is not limited.

First gradual change groove 511 and second gradual change groove 521 all are the drop form, all set up around the axis equipartition of first output shaft 1, as shown in fig. 5, and the direction that arrow B shows is first direction, and in the first direction, the distance between two lateral walls of first gradual change groove 511 increases gradually, and the region that the size is little in two lateral walls is located the rear, and the region that the size is big in two lateral walls is located the place ahead. In order to match the movement of the ball 53, the first and second gradually-changing grooves 511 and 521 have gradually-changing depths, and a region having a large size among the two sidewalls has a large depth, and a region having a small size among the two sidewalls has a small size.

Referring to fig. 1 to 6, when the first cam plate 51 rotates in the direction B, the second cam plate 52 is fixed by the housing 11, a rotational speed difference is generated between the first cam plate 51 and the second cam plate 52, the ball 53 between the first cam plate 51 and the second cam plate 52 moves along the first tapered groove 511 and the second tapered groove 521, and the first cam plate 51 moves axially along the first output shaft 1 during the movement of the ball 53.

Referring to fig. 2 to 6, in an embodiment, an end of the first cam plate 51 away from the first output shaft 1 is a cam driving end 512, and the cam driving end 512 is used for being connected with an actuator and driven by the actuator to rotate so as to rotate the first cam plate 51; the end part of the second cam plate 52 far away from the first output shaft 1 is a cam limiting end 522, and when the first cam plate 51 rotates around the first direction, the cam limiting end 522 is used for limiting the position of the second cam plate 52; the cam driving end 512 and the cam limiting end 522 are both located on one side of the actuator.

Referring to fig. 3, when first cam plate 51 rotates in the first direction, second cam plate 52 abuts against housing 11, and housing 11 limits second cam plate 52 by means of cam limiting end 522, so that second cam plate 52 and housing 11 are kept unchanged in position. The cam driving end 512 and the cam limiting end 522 are both positioned at one side of the actuating mechanism, so that the space overlapping amount of the rotating arms of the first cam plate 51 and the second cam plate 52 is increased, the space can be reduced, the installation is simple and convenient, the bearing torque of the cam driving end is improved, and larger torque can be transmitted.

In this practical application, compared with the gear train type shifting mechanism, the cam mechanism can realize a speed ratio of more than 15 and can transmit large torque in a space with an axial distance of 20mm, the cam mechanism can realize a speed ratio of 20, and the self-bearing torque reaches 250 Nm. When the worm wheel 63 and the worm structure are matched, the total speed ratio is close to 1400, and the provided speed ratio is larger.

Referring to fig. 1 to 3, in one embodiment, the actuator includes a shift shaft 61 and a cam 62, the cam 62 is coaxially and fixedly connected with the shift shaft 61, the outer peripheral surface of the cam 62 is suitable for being in contact connection with a cam driving end 512, and the cam 62 rotates to push the first cam plate 51 to rotate.

Referring to fig. 1 to 3, in an embodiment, around the first direction, the cam 62 is formed with a first arc 621, a second arc 622 and a third arc 623 connected end to end on the outer circumference; the first arc 621 is an arc structure recessed into the cam 62; the second arc 622 is an arc structure protruding outward from the cam 62, and the second arc 622 is connected by multiple tangent arcs with gradually larger radius; the third segment 623 has an arc structure recessed into the cam 62.

The cam 62 has an attractive shape, and has the advantages of simple structure and convenience in processing.

Referring to fig. 3-5, in one embodiment, the cam mechanism further includes a contact bearing 54, and the cam driving end 512 is in contact connection with the cam 62 through the contact bearing 54. The contact bearing 54 can reduce friction force between the first cam plate 51 and the cam 62, ensuring stable operation of the transfer case.

Referring to fig. 3, the cam 62 is driven by the shift shaft 61 to rotate counterclockwise, and during the counterclockwise rotation of the cam 62, the first arc 621 and the second arc 622 sequentially push the first cam plate 51 to rotate in the first direction through the contact bearing 54.

In actual assembly, the contact bearings 54 are press-fit onto cam plate pins that are joined to the first cam plate 51 by welding.

When contact bearing 54 slides at first section arc 621, whole car is in the 2H mode, because first section arc 621 adopts the centre concave, the high shape in both ends effectively plays the positioning action to contact bearing 54, prevents to lead to danger and spare part early wear because vibrations or installation machining error cause the transfer case initial malfunction. The second arc 622 is used for controlling the action profile of the clutch assembly, the second arc 622 has the characteristics of the cam 62 and ensures the smoothness of sliding, the occupied space is small, and when the contact bearing 54 moves from the first arc 621 to the second arc 622 and continues to move along the second arc 622, the distance from the contact bearing 54 to the axis of the cam 62 is gradually increased. The third arc section 623 is a molded line matched with high and low gear actions, when the contact bearing 54 moves from the first arc section 621 to the third arc section 623, the distance from the contact bearing 54 to the axis of the cam 62 increases and then decreases, the first cam disc 51 axially moves along the first output shaft 1 while rotating in the first direction in the process of increasing the distance from the contact bearing 54 to the axis of the cam 62, the clutch assembly is not engaged in the process of moving the first cam disc 51 leftward, and no torque distribution is performed between the first output shaft 1 and the second output shaft 2.

Referring to fig. 1 and 8, in an embodiment, the actuator further includes a worm wheel 63, a worm, and an actuator motor, an output shaft of the actuator motor is in transmission connection with the worm, the worm is in meshing transmission connection with the worm wheel 63, the worm wheel 63 is in interference fit with the shift shaft 61, and the cam 62 is in interference fit with an extension of a central shaft hole of the worm wheel 63.

When the worm wheel 63 rotates counterclockwise in fig. 3, the cam 62 is driven to rotate counterclockwise, and the outer profile of the cam 62 contacts the contact bearing 54. The worm is directly connected with the executing motor, the output torque of the executing motor is transmitted to the worm wheel 63 through the worm, and the worm is matched with the worm wheel 63, so that the torque can be amplified in equal proportion according to the speed ratio.

Referring to fig. 1, the transmission mechanism includes a driving sprocket 31, a driven sprocket 32 and a chain 33, the driving sprocket 31 is supported on the first output shaft 1 through a bearing and can rotate relative to the first output shaft 1, the driven sprocket 32 is fixedly connected with the second output shaft 2, the driving sprocket 31 is in transmission connection with the driven sprocket 32 through the chain 33, a locking portion is arranged on one side of the driving sprocket 31, and the right side of the driving sprocket 31 is connected with a clutch outer hub 41 of the clutch assembly.

The clutch assembly comprises a clutch and a clutch pressure plate 43, the clutch comprises a clutch outer hub 41, an outer friction plate, a clutch inner hub 42 and an inner friction plate, the clutch outer hub 41 is fixedly connected with the outer friction plate, the clutch inner hub 42 is fixedly connected with the inner friction plate, and the inner friction plate and the outer friction plate are arranged in a staggered mode. The left side of the clutch outer hub 41 is fixedly connected with the right side of the driving chain wheel 31, and the clutch inner hub 42 is fixedly connected with the first output shaft 1. The first cam plate 51 is moved leftward in the axial direction of the first output shaft 1 by the clutch pressure plate 43 to increase the degree of pressing between the outer and inner friction plates, so that the clutch outer hub 41 and the clutch inner hub 42 are rotated synchronously. In actual use, a return spring is provided between the first cam plate 51 and the clutch inner hub 42, and the return spring provides the first cam plate 51 with a pushing force away from the clutch pressure plate 43.

Referring to fig. 1 to 3, in one embodiment, the transfer case further includes an input shaft 7, a planetary gear mechanism 8 provided on the input shaft 7, a power switching member 9 and a lock sleeve 10 provided on the first output shaft 1, the input shaft 7 being formed as a sun gear of the planetary gear mechanism 8; the power switching member 9 selectively engages the first output shaft 1 with the input shaft 7 or the carrier of the planetary gear mechanism 8 through an actuator to enable switching between the high and low gears, or the power switching member 9 engages the locking sleeve 10 with the transmission mechanism through an actuator to enable locking of the first output shaft 1 with the second output shaft 2.

Planetary gear 8 includes the sun gear, the planet wheel, planet carrier and ring gear, and input shaft 7 forms the sun gear of planetary gear 8 in this embodiment, and input shaft 7 has internal spline and external spline, and input shaft 7 external spline is connected with a plurality of planet wheel meshing transmission, a plurality of planet wheels still with the internal spline meshing of ring gear, a plurality of planet wheel fixed support are on the planet carrier, the planet carrier is formed with the internal spline.

The power switching member 9 has an internal spline and an external spline, and referring to fig. 2, a connecting portion 91 is provided on the right side of the power switching member 9, and the power switching member 9 is slidably connected to the first output shaft 1 via the internal spline, and is movable in the axial direction of the first output shaft 1 so that the external spline thereof is engaged with the internal spline of the sun gear or the internal spline of the carrier, and outputs a high speed gear when engaged with the internal spline of the sun gear and a low speed gear when engaged with the internal spline of the carrier. And when the power switching piece 9 axially slides to the right side shown in fig. 1, the power switching piece 9 is meshed with the internal spline of the planet carrier and simultaneously pushes the locking sleeve 10 to slide rightwards, the locking sleeve 10 is meshed with the locking part of the driving sprocket 31 to be locked, the first output shaft 1 and the second output shaft 2 are locked, and the power output to the first output shaft 1 is transmitted to the second output shaft 2 through the transmission mechanism.

As shown in fig. 1, 2 and 8, the actuator of the present application can be divided into three parts according to functional division, the first part is a driving part and comprises the actuator motor, the worm wheel 63 and the worm in the above embodiments, and the torque is amplified in equal proportion according to the speed ratio by matching the worm wheel 63 and the worm.

The second part is the part that controls engagement and disengagement of the clutch assembly and includes the cam 62 in the embodiment described above.

The third part is a part for controlling high and low gear shifting and mechanical locking, and comprises a shifting fork 66, a hub assembly and a shifting block 68, wherein the hub assembly is arranged in an inner cavity of the shifting fork 66. The rotary hub assembly comprises a rotary hub 671, a supporting plate 672 and an energy storage spring 673, the energy storage spring 673 is located in an inner cavity of the supporting plate 672, the supporting plate 672 is located in an inner cavity of the rotary hub 671, the supporting plate 672 and the energy storage spring 673 are sequentially sleeved and arranged and then assembled on the gear shifting shaft 61, and an inner hole of the rotary hub assembly is formed in the middle of the rotary hub assembly. The gear shifting shaft 61 is provided with a shifting block hole, one end of a shifting block 68 is connected with the shifting block hole in an interference fit mode, and the other end of the shifting block 68 protrudes out of the outer surface of the gear shifting shaft 61.

The inner hole of the rotating hub assembly is in clearance fit with the gear shifting shaft 61, the rotating hub assembly can slide on the gear shifting shaft 61, a molded line groove is formed in a rotating hub 671 in the rotating hub assembly, the other end of a shifting head 68 penetrates through an energy storage spring 673 and a supporting plate 672 and then is in clearance fit with the molded line groove, when the shifting head 68 rotates along with the gear shifting shaft 61, the shifting head 68 slides in the molded line groove to enable the rotating hub assembly to move axially along the gear shifting shaft 61, the part, located on the outer side of the supporting plate 672, of the energy storage spring 673 is in contact fit with a limiting rib in the inner cavity of a gear shifting fork 66, when the rotating hub assembly continues to move axially along the gear shifting shaft 61 to drive the gear shifting fork to shift 66 together to move axially along the gear shifting shaft 61, the gear shifting fork 66 drives the power piece 9 to move axially along the first output shaft 1 through a shifting connection part 91, and an external spline of the power shifting piece 9 is meshed with an internal spline of a sun wheel or an internal spline of a planet carrier, so that high-low-gear output is realized.

The transfer case in the embodiment of the application can realize the driving modes of 2H, ATUO and 4L-Lock:

2H mode: power is input through the input shaft 7, an external spline of the power switching piece 9 is meshed with an internal spline of the sun wheel, the input shaft 7 transmits the power to the first output shaft 1 and then directly outputs the power to the rear axle, and at the moment, the clutch assembly does not work;

in the ATUO mode: referring to fig. 3, power is input from the input shaft 7, the worm gear 63 is driven by the actuator motor to rotate counterclockwise by the worm, the cam 62 is driven by the rotation of the worm gear 63 to rotate counterclockwise, the contact bearing 54 slides on the outer peripheral surface of the cam 62 during the rotation of the cam 62 to drive the first cam plate 51 to rotate around the first direction, the second cam plate 52 is fixed relative to the housing 11, the first cam plate 51 and the second cam plate 52 rotate relative to each other, the first cam plate 51 moves along the axial direction of the first output shaft 1 during the movement of the ball 53 in the first gradually-changing groove 511 and the second gradually-changing groove 521, and the first cam plate 51 and the clutch assembly control transmission mechanism transmit the torque of the first output shaft 1 to the second output shaft 2.

4L-Lock mode: referring to fig. 3, power is input by the input shaft 7, the execution motor rotates reversely, the worm wheel 63 rotates clockwise to drive the shift shaft 61 to rotate clockwise, the shift fork 66 moves to drive the power switching piece 9 to move away from the sun wheel and move to be engaged with the internal spline of the planet carrier to realize a low-speed gear, the power switching piece 9 moves and simultaneously pushes the locking sleeve 10 to move rightward, the locking sleeve 10 moves rightward to be engaged with the locking part on the driving sprocket 31 to realize locking of the first output shaft 1 and the second output shaft 2, and the torque of the first output shaft 1 is transmitted to the second output shaft 2.

The transfer case in this embodiment to the actuating motor drive, response speed is fast, and is with low costs, adopts worm wheel 63 worm structure to match cam mechanism and realizes providing big moment of torsion at little space range to can shift to the self-locking of target in place after, the motor need not long-time work, extension motor life. Meanwhile, torque is transmitted through the cam mechanism and the cam 62 to control the connection and disconnection of the clutch assembly, the first cam plate 51 and the second cam plate 52 are arranged on one side of the actuating mechanism, and the second cam plate 52 is limited by the shell 11, so that the space is greatly saved. The transfer case reduces the number and the weight of parts, is convenient to assemble and reduces the cost; the structural arrangement is compact, and the integrated design is convenient.

The embodiment of the utility model also provides a vehicle which particularly comprises the transfer case.

Since the vehicle includes the transfer case, the vehicle also has the advantages of the above-described embodiment of the transfer case.

The present invention is not limited to the above preferred embodiments, and any modifications, equivalent substitutions, improvements, etc. within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (10)

1. A transfer case is characterized by comprising a first output shaft (1), a second output shaft (2), a transmission mechanism, a clutch assembly, a cam mechanism and an actuating mechanism;

the transmission mechanism is connected with the first output shaft (1), the second output shaft (2) and the clutch assembly and is used for transmitting the torque of the first output shaft (1) to the second output shaft (2);

the clutch assembly and the cam mechanism are arranged on the first output shaft (1), the first output shaft (1) is arranged in parallel with the actuating mechanism, and the cam mechanism is positioned on one side of the actuating mechanism;

the actuating mechanism is used for pushing the cam mechanism to rotate around a first direction, and the first direction rotation of the cam mechanism controls the engagement degree of the clutch assembly so as to control the torque distribution between the first output shaft (1) and the second output shaft (2).

2. The transfer case of claim 1, wherein the cam mechanism comprises a first cam disc (51) and a second cam disc (52), the first cam disc (51) and the second cam disc (52) are oppositely arranged, a central shaft hole of the first cam disc (51) is rotatably sleeved on a boss along the central shaft hole of the second cam disc (52), and the second cam disc (52) is rotatably sleeved on the first output shaft (1);

the actuating mechanism is used for pushing the first cam plate (51) to rotate around the first direction, so that the first cam plate (51) moves axially along the first output shaft (1) to control the engagement degree of the clutch assembly.

3. The transfer case of claim 2,

a first gradually-changing groove (511) is formed in the disc surface of the first cam disc (51), a second gradually-changing groove (521) is formed in the disc surface of the second cam disc (52), the first gradually-changing groove (511) and the second gradually-changing groove (521) are arranged in opposite directions, and the first gradually-changing groove (511) and the second gradually-changing groove (521) are both in a water-drop shape;

the cam mechanism further comprises a ball body (53), and in the initial state of the first cam plate (51), the ball body (53) is positioned in a large area of two side walls of the first gradually-changing groove (511) and a large area of two side walls of the second gradually-changing groove (521);

the actuating mechanism pushes the first cam plate (51) to rotate around the first direction, the ball body (53) moves to a small-size area in the two side walls along the first gradually-changing groove (511) and moves to a small-size area in the two side walls along the second gradually-changing groove (521), and the ball body (53) enables the first cam plate (51) to move axially along the first output shaft (1).

4. The transfer case of claim 2,

the end part of the first cam plate (51) far away from the first output shaft (1) is a cam driving end (512), and the cam driving end (512) is used for being connected with the actuating mechanism and driven by the actuating mechanism to rotate so as to enable the first cam plate (51) to rotate;

the end part, far away from the first output shaft (1), of the second cam plate (52) is a cam limiting end (522), and when the first cam plate (51) rotates around the first direction, the cam limiting end (522) is used for limiting the position of the second cam plate (52);

the cam driving end (512) and the cam limiting end (522) are both located on one side of the actuating mechanism.

5. The transfer case of claim 4, wherein the actuator comprises a shift shaft (61) and a cam (62), the cam (62) is fixedly connected with the shift shaft (61) coaxially, the outer circumferential surface of the cam (62) is suitable for being in contact connection with the cam driving end (512), and the cam (62) pushes the first cam disc (51) to rotate in a rotating way.

6. The transfer according to claim 5, characterized in that the periphery of the cam (62) is formed with a first segment of arc (621), a second segment of arc (622) and a third segment of arc (623) connected end to end around the first direction;

the first arc part (621) is in an arc structure which is sunken into the cam (62);

the second arc part (622) is of an arc structure protruding outwards the cam (62), and the second arc part (622) is connected by a plurality of groups of arcs which are tangent and have gradually-increased radius;

the third arc section (623) is of an arc structure which is sunken into the cam (62).

7. The transfer case of claim 5, wherein the cam mechanism further comprises a contact bearing (54), the cam drive end (512) being in contact connection with the cam (62) through the contact bearing (54).

8. The transfer case of claim 5, characterized in that the actuator further comprises a worm wheel (63), a worm and an actuator motor, wherein an output shaft of the actuator motor is in transmission connection with the worm, the worm is in meshing transmission connection with the worm wheel (63), the worm wheel is in interference fit with the gear shift shaft (61) and the cam (62) is in interference fit with an extension of the central shaft hole of the worm wheel.

9. The transfer according to claim 1, characterized by further comprising an input shaft (7), a planetary gear mechanism (8) provided on the input shaft (7), a power switching member (9) and a lock sleeve (10) provided on the first output shaft (1), the input shaft (7) being formed as a sun gear of the planetary gear mechanism (8);

the power switching member (9) selectively engages the first output shaft (1) with the input shaft (7) or the carrier of the planetary gear mechanism (8) through the actuator to enable switching between the high and low gears, or the power switching member (9) engages the locking sleeve (10) with the transmission mechanism through the actuator to enable locking of the first output shaft (1) with the second output shaft (2).

10. A vehicle characterized by comprising the transfer case of any one of claims 1 to 9.

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