WO2018121291A1

WO2018121291A1 - Differential, and vehicle

Info

Publication number: WO2018121291A1
Application number: PCT/CN2017/116565
Authority: WO
Inventors: 凌和平; 翟震; 黄长安; 罗永孟
Original assignee: 比亚迪股份有限公司
Priority date: 2016-12-27
Filing date: 2017-12-15
Publication date: 2018-07-05
Also published as: CN108240451A; CN108240451B

Abstract

A differential (100), and vehicle (10000). The differential (100) comprises: two planetary gear mechanisms, wherein ring gears (13, 23) are used as a power output end, an input portion and two planet carriers (11, 21) are coaxially arranged, and the input portion is linked to the two planet carriers (11, 21); a power engagement device (400) comprising a first and second engagement portion (410, 420), wherein the first engagement portion (410) is connected to one of the two ring gears (13, 23), the second engagement portion (420) rotates synchronously with the two planet carriers (11, 21), and the two planet carriers (11, 21) form a power input end of the differential (100); and an engagement portion drive device (500) comprising a drive pin (510) and a drive portion, wherein the drive portion is configured to drive the drive pin (510) to drive the second engagement portion (420) to move along an axle direction toward the first engagement portion (410), such that the second engagement portion (420) is engaged with the first engagement portion (410). In this way, the differential of the present invention can lock two half axles to improve the ability of a vehicle to handle rough terrain.

Description

Differential and vehicle

Cross-reference to related applications

The present application claims priority to Chinese Patent Application No. 20161122929, filed on Dec.

Technical field

The present invention relates to the field of vehicle technology, and in particular, to a differential and a vehicle having the same.

Background technique

In the related technology, the new energy vehicle adopts a distributed driving mode, and the two motors respectively drive the wheels on both sides, and the rotational speed and torque of the left and right wheels can be independently adjusted by the controller, thus canceling the differential, but in a certain In some slippery road conditions, it is still necessary to lock the left and right axles to improve vehicle passing. If the conventional electric lock-type differential is applied to a distributed-powered new energy vehicle, the differential function of the differential is wasted, and the conventional electric lock-type differential has a complicated structure and many components. Take up more space.

Summary of the invention

The present invention aims to solve at least one of the technical problems in the related art to some extent. To this end, the present invention proposes a differential that can lock the two half shafts and improve the ability of the vehicle to escape.

The invention further proposes a vehicle.

A differential according to the present invention includes: a first planet carrier, a first planet gear, and a first ring gear, the first planet gear being disposed on the first planet carrier, the first planet gear and the first planet gear a first ring gear meshes; a second planet carrier, a second planet gear and a second ring gear, the second planet gear being disposed on the second planet carrier, the second planet gear and the second ring gear Engaging and engaging the second planet gear with the first planet gear; wherein the first ring gear and the second ring gear constitute two power output ends of the differential, the first planet carrier And the second planet carrier constitutes a power input end of the differential; the power engagement device includes a first engagement portion and a second engagement portion, the first engagement portion and the first ring gear One of the second ring gears is connected, the second engaging portion rotates in synchronization with the first planet carrier and the second planet carrier; the joint driving device includes: a driving pin and a driving portion The driving pin is disposed to be wrapable with the first planet carrier and the second planet carrier And the axis of rotation relative to the first carrier and the second carrier to move axially, the two ends of the drive pin with the drive portion and the second mating engagement portion, the driving portion is provided The driving of the driving pin drives the second engaging portion to move in a direction toward the first engaging portion in the axial direction, thereby engaging the second engaging portion with the first engaging portion.

According to the differential of the present invention, when the engaging portion driving device drives the second engaging portion to engage with the first engaging portion, the output rotational speeds of the first ring gear and the second ring gear are the same, so that the two half shafts can be synchronized. This can help improve the vehicle's ability to get out of trouble.

A vehicle according to the present invention includes the above differential.

DRAWINGS

1 is an exploded view of a differential according to an embodiment of the present invention;

2 is a front elevational view of a differential in accordance with an embodiment of the present invention;

3 is a schematic diagram of a planar principle of a differential according to an embodiment of the present invention;

4 is a partial perspective view of a differential according to an embodiment of the present invention, in which the first ring gear and the first planet carrier are removed;

Figure 5 is a partial front elevational view of the differential, mainly showing the first planet carrier, the first planet gears, and the second planet carrier and the second planet gear, etc., in accordance with an embodiment of the present invention;

Figure 6 is a schematic view showing the meshing of the first planetary gear and the second planetary gear;

Figure 7 is a schematic diagram of the engagement of the first planetary gear and the second planetary gear;

Figure 8 is a perspective view of a first ring gear or a second ring gear according to still another embodiment of the present invention;

Figure 9 is a perspective view of a first ring gear or a second ring gear according to still another embodiment of the present invention;

Figure 10 is a schematic illustration of a power drive system in accordance with an embodiment of the present invention;

Figure 11 is a schematic illustration of a vehicle in accordance with an embodiment of the present invention;

Figure 12 is a schematic illustration of a power drive system in accordance with the present invention;

Figure 13 is a schematic view of a differential, a power engaging device, and a joint driving device;

Figure 14 is a schematic view showing the structure of the follower portion.

detailed description

The embodiments of the present invention are described in detail below, and the examples of the embodiments are illustrated in the drawings, wherein the same or similar reference numerals are used to refer to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are intended to be illustrative of the invention and are not to be construed as limiting.

A differential 100 according to an embodiment of the present invention will be described in detail below with reference to FIGS. 1-11. The differential 100 can be used for inter-wheel differential or inter-axle differential for the example of inter-wheel differential. The differential 100 enables the left and right drive wheels to roll at different angular velocities when the vehicle is turning or traveling on uneven roads to ensure a pure rolling motion between the drive wheels on both sides and the ground.

As shown in FIG. 1, a differential 100 according to some embodiments of the present invention may include a first planet carrier 11, a first planet gear 12 and a first ring gear 13, and a second planet carrier 21, a second planet gear 22, and a Two ring gears 23.

In conjunction with the embodiment of Figures 1 and 5, both the first planet carrier 11 and the second planet carrier 21 can be configured as a circular plate-like structure, which can reduce the axial dimension of the differential 100 to some extent. In some embodiments, the first planet carrier 11 and the second planet carrier 21 may be of a split structure, and since the separate widgets are relatively easy to shape, separately machining the first planet carrier 11 and the second planet carrier 21 separately may simplify manufacturing. Process, improve processing accuracy.

As shown in FIGS. 1, 3, 5 and in conjunction with FIGS. 6-7, the first planet gears 12 are disposed on the first planet carrier 11, for example, each of the first planet gears 12 is provided with a first planet gear axle 14 The two ends of the first planetary axle 14 are rotatably supported on the first planet carrier 11 and the second planet carrier 21, respectively, such that both ends of the first planetary axle 14 are rotatably supported by bearings In the shaft holes corresponding to each other on the first planet carrier 11 and the second planet carrier 21, the first planet gear 12 can be fixed to the corresponding first planet gear shaft 14 at this time. Thereby, the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved by the first planetary axle 14 such that the first planet carrier 11 and the second planet carrier 21 maintain the same speed and the same direction (ie, the first The carrier 11 and the second carrier 21 are interlocked). Moreover, with this connection, the first planet carrier 11 and the second planet carrier 21 can support the first planetary axle 14 well, preventing the first planetary axle 14 from being disconnected from the single planet carrier, thereby causing the differential 100 to fail. .

Referring to FIG. 3, the first planet gear 12 meshes with the first ring gear 13, specifically in the form of internal engagement, that is, the first planet gear 12 is located inside the first ring gear 13 and with the teeth on the first ring gear 13. Engage. The first planetary gears 12 are preferably plural and are distributed equidistantly inside the first ring gear 13 in the circumferential direction. For example, as a preferred embodiment, the first planetary gears 12 may be three and any adjacent ones. The angle between the two first planet wheels 12 is 120°.

Similarly, as shown in FIG. 1, FIG. 3, FIG. 5 and in conjunction with FIGS. 6-7, the second planet gears 22 are disposed on the second planet carrier 21, for example, each of the second planet gears 22 is configured with a second. The planetary axles 24, such as the two ends of the second planetary axle 24, are rotatably supported by bearings in respective axial bores of the first planet carrier 11 and the second planet carrier 21, at which time the second planet gear 22 can be fixed to the corresponding second planetary axle 24. Thereby, the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved by the second planetary gear shaft 24, so that the first planet carrier 11 and the second planet carrier 21 maintain the same speed and the same direction. Moreover, with this connection, the first planet carrier 11 and the second planet carrier 21 can support the second planetary axle 24 well, preventing the second planetary axle 24 from being disconnected from the single planet carrier, thereby causing the differential 100 to fail. .

In addition, in other embodiments of the present invention, in order to keep the first carrier 11 and the second carrier 21 movable at the same speed and in the same direction, the first planet carrier 11 and the second planet carrier 21 may also be passed through the intermediate member. Directly fixed connection, that is, the same speed and co-directional movement of the first planet carrier 11 and the second planet carrier 21 in the above embodiment may be achieved by the first planetary axle 14 and the second planetary axle 24, and The embodiment can realize the same speed and the same direction movement of the first planet carrier 11 and the second planet carrier 21 directly by providing the intermediate component, for example, the intermediate component can be located on the first planet carrier 11 and the second planet carrier. Between 21 and respectively welded and fixed to the first planet carrier 11 and the second planet carrier 21.

Referring to FIG. 3, the second planetary gear 22 meshes with the second ring gear 23, specifically in the form of internal engagement, that is, the second planetary gear 22 is located inside the second ring gear 23 and with the teeth on the second ring gear 23. Engage. The second planetary gears 22 are preferably plural and are distributed equidistantly inside the second ring gear 23 in the circumferential direction. For example, as a preferred embodiment, the second planetary gears 22 may be three and any adjacent ones. The angle between the two second planet gears 22 is 120°.

It should be noted that FIG. 3 is a schematic diagram of the plane principle of the differential 100 according to an embodiment of the present invention, wherein the meshing relationship between the first planet gear 12 and the second planet gear 22 is schematically illustrated and The meshing relationship between the first planetary gear 12 and the first ring gear 13, the second planetary gear 22 and the second ring gear 23, as shown in Fig. 3, and at the same time shows the above three meshing relationships, the relative positions of the components The relationship is merely illustrative and does not represent or imply the actual spatial arrangement of the components.

In embodiments where both the first planet gear 12 and the second planet gear 22 are multiple, preferably, the plurality of first planet gears 12 and the plurality of second planet gears 22 are respectively engaged. For example, as shown in FIGS. 1 and 4, the first planetary gear 12 and the second planetary gear 22 are three, and the first first planetary gear 12 can be meshed with the corresponding first second planetary gear 22, The second first planet gear 12 is engageable with the corresponding second second planet gear 22, and the third first planet gear 12 is engageable with the corresponding third second planet gear 22 such that there are multiple sets of meshing with each other The first planetary gear 12 and the second planetary gear 22, when the differential 100 transmits power, the power is transmitted between the plurality of sets of the first planetary gear 12 and the second planetary gear 22 that are meshed with each other to be more stable and reliable.

Further, in another embodiment in which the first planetary gear 12 and the second planetary gear 22 are plural, the plurality of first planetary gears 12 and the plurality of second planetary gears 22 are alternately arranged in the circumferential direction, and are arbitrarily adjacent The first planet gear 12 and the second planet gear 22 mesh. That is, in this embodiment, the plurality of first planetary gears 12 and the plurality of second planetary gears 22 are alternately arranged in the circumferential direction and form an annular shape, and each of the first planetary gears 12 has two adjacent ones thereof. The two planet gears 22 mesh, and similarly, each of the second planet gears 22 meshes with its two adjacent first planet gears 12.

With reference to the embodiment of FIG. 3, the revolution axis O of the first planet gear 12 coincides with the revolution axis O of the second planet gear 22, and the revolution radius of the first planet gear 12 and the second planet gear 22 (ie, the planetary gear The distance of the central axis from the revolution axis O is the same.

In particular, as shown in FIGS. 1-2, 4-4, the first planet gear 12 is in meshing engagement with the second planet gear 22. In other words, for the first planetary gear 12, it not only meshes with the first ring gear 13, but also meshes with the second planetary gear 22, and for the second planetary gear 22, it not only meshes with the second ring gear 23, At the same time, it also meshes with the first planet gear 12.

As shown in FIG. 3, the first ring gear 13 and the second ring gear 23 may constitute two power output ends of the differential 100, and the first carrier 11 and the second carrier 21 correspond to the power of the differential 100. The input end (for example, the first carrier 11 and the second carrier 21 can be rigidly connected together), so that the power output from the external power source can be input from the first carrier 11 and the second carrier 21, and the differential is passed. The differential action of the device 100 can be respectively from the first ring gear 13 and the second ring gear 23 Output. At this time, as an alternative embodiment, the first planet carrier 11 and the second planet carrier 21 may be connected to a power source such as an engine, a motor, etc., and the first ring gear 13 and the second ring gear 23 may pass through a gear transmission structure and corresponding The half shafts are connected, and the half shafts are connected to the corresponding wheels, but are not limited thereto.

Hereinafter, the differential 100 is applied to the inter-wheel differential, and the first ring gear 13 and the second ring gear 23 constitute a power output end of the differential 100, and the first carrier 11 and the second carrier 21 constitute a differential. The power input end of 100 exemplifies the working principle of the differential 100, wherein the first ring gear 13 can be connected to the left half shaft through a gear transmission structure, and the left half shaft can be connected to the left side wheel, the second tooth. The ring 23 can be connected to the right half shaft by a gear transmission structure, and the right half shaft can be connected to the right side wheel, and the power output of the power source such as the engine and/or the motor can be output to the first carrier through the deceleration of the final drive. 11 and the second planet carrier 21. If the vehicle is traveling on a smooth road surface and there is no turning at this time, the left wheel and the right wheel are theoretically rotated at the same speed. At this time, the differential 100 does not function as a differential, and the first carrier 11 and the second carrier 21 are at the same speed. In the same direction, the first ring gear 13 and the second ring gear 23 rotate at the same speed and in the same direction, and the first planetary gear 12 and the second planetary gear 22 only revolve and do not rotate. If the vehicle is driving on an uneven road surface or the vehicle is turning, the left and right wheels are theoretically different in rotational speed, and the rotational speeds of the first ring gear 13 and the second ring gear 23 are also different, that is, there is a difference in rotational speed. The first planetary gear 12 and the second planetary gear 22 also rotate while revolving, and the rotation of the first planetary gear 12 and the second planetary gear 22 causes one of the first ring gear 13 and the second ring gear 23 to increase speed, Another deceleration, the difference between the speed-increasing ring gear and the decelerating ring gear is the difference between the left and right wheels, thus achieving differential action.

In summary, the differential 100 according to an embodiment of the present invention utilizes the principle of planetary differential, has higher space utilization in structure and connection form, smaller axial dimension, and is more advantageous in production and assembly. Such a structural form can not only avoid the dimensional defects in the axial direction and the radial direction of the bevel gear, but also can better utilize the hollow space inside the main reduction driven gear, thereby achieving better space utilization and greatly facilitating the difference. The overall arrangement of the speedometer 100 assembly and the limitation on the weight, as well as higher reliability and better transmission efficiency, are beneficial to improve the reliability of the power transmission chain and the power output fluency during cornering. This is more practical than a symmetrical bevel gear differential.

The meshing relationship between the first planetary gear 12 and the second planetary gear 22 will be described in detail below in conjunction with a specific embodiment.

Referring to FIGS. 3 and 5 to 7, the first planetary gear 12 and the second planetary gear 22 partially overlap in the axial direction (the horizontal direction in FIG. 7), that is, the first planetary gear 12 and the second planetary gear. The wheels 22 only partially overlap, the other portions are staggered, the overlapping portions of the first planet gear 12 and the second planet gear 22 can engage each other, and the staggered portions can engage the respective ring gears.

Specifically, as shown in FIG. 6 and FIG. 7, the first planetary gear 12 may include a first tooth portion 151 and a second tooth portion 152 (with a broken line of K2 in FIG. 7), and the second planetary gear 22 may include the first The third tooth portion 153 and the fourth tooth portion 154 (with a broken line of K1 in FIG. 7 as a boundary line), the second tooth portion 152 and the third tooth portion 153 constitute an overlapping portion, that is, the second tooth portion 152 and the third tooth portion 153 are The first tooth portion 151 and the fourth tooth portion 154 are axially offset and mesh with the corresponding ring gears, that is, the first tooth portion 151 is meshed with the first ring gear 13 , and the fourth portion is overlapped and engaged. Tooth portion 154 and second ring gear 23 Engage.

Thereby, the axial dimension of the differential 100 is made more compact, and the volume of the differential 100 is more compact, which facilitates the installation and arrangement of the differential 100.

The power input end and the power output end of the differential 100 will be described in detail below in conjunction with specific embodiments.

As shown in FIG. 3, the differential 100 further includes

input shafts

31, 32 and

output shafts

41, 42 that are coupled to the first planet carrier 11 and the second planet carrier 21, respectively, as in the example of FIG. An input shaft 31 is connected to the left side of the first carrier 11, and another input shaft 32 is connected to the right side of the second carrier 21. The

output shafts

41, 42 are respectively connected to the first ring gear 13 and the second ring gear 23, as in the example of Fig. 3, the left side of the first ring gear 13 is connected to an output shaft 41, and the second ring gear 23 is connected to the right. Another output shaft 42 is connected to the side. The

input shafts

31, 32, the

output shafts

41, 42, the first ring gear 13 and the second ring gear 23 can be arranged coaxially.

Further, as shown in FIG. 3, the input shaft includes a first input shaft 31 and a second input shaft 32. The first input shaft 31 is connected to the first carrier 11, and the second input shaft 32 is connected to the second carrier 21. The output shaft may include a first output shaft 41 and a second output shaft 42, the first output shaft 41 being coupled to the first ring gear 13, and the second output shaft 42 being coupled to the second ring gear 23, the first input shaft 31 and the The two input shafts 32 and the first output shaft 41 and the second output shaft 42 may each be a hollow shaft structure. In a preferred embodiment, the first output shaft 41 is coaxially sleeved on the first input shaft 31, and second. The output shaft 42 is coaxially sleeved on the second input shaft 32, whereby the differential 100 is more compact and smaller in size.

According to some embodiments of the present invention, the number of teeth of the first ring gear 13 is equal to the number of teeth of the second ring gear 23, and the number of teeth of the first planet gear 12 is equal to the number of teeth of the second planet gear 22.

According to some embodiments of the present invention, the first planetary gear 12 and the second planetary gear 22 are both spur gears, and the differential 100 using the spur gear is more compact in structure than the conventional symmetrical bevel gear differential, in particular It has higher space utilization in structure and connection form, smaller axial dimension, and is more advantageous in production and assembly.

The structure of the first ring gear 13 and the second ring gear 23 will be described in detail below in conjunction with specific embodiments.

In some embodiments of the present invention, the first ring gear 13 and the second ring gear 23 are symmetric structures, in other words, the first ring gear 13 and the second ring gear 23 are symmetrically arranged, which can increase the versatility of the ring gear and reduce cost.

Specifically, as shown in FIG. 1 and in conjunction with FIG. 3, each of the first ring gear 13 and the second ring gear 23 includes a main body flat plate portion 161 and an annular side wall portion provided at an outer peripheral edge of the main body flat plate portion 161. 162, the main body flat portion 161 and the annular side wall portion 162 may be integrally formed members. A plurality of gear teeth are disposed on an inner wall surface of the annular side wall portion 162, and a cavity A1, A2 is defined between the main body flat plate portion 161 and the annular side wall portion 162 (see FIG. 3), that is, the first ring gear 13 A cavity A1 is defined between the main body flat portion 161 and the annular side wall portion 162, and a cavity A2 is defined between the main body flat portion 161 of the second ring gear 23 and the annular side wall portion 162, and the inside of the first ring gear 13 The cavity A1 and the cavity A2 in the second ring gear 23 face each other to constitute an installation space A (see FIG. 3), wherein the first planet carrier 11 and the first planet gear 12 and the second planet carrier 21 and the second planet The wheel 22 is housed in the installation space A, so that the structure of the differential 100 is relatively more compact and occupied. The volume is smaller and easier to arrange, while the first ring gear 13 and the second ring gear 23 function as an outer casing, which can protect the planet carrier and the planet gear housed therein, improving the life. In addition, the installation space A defined by the first ring gear 13 and the second ring gear 23 is relatively closed, and the external debris is not easily entered into the installation space A to affect the moving parts, thereby ensuring stable operation of the differential 100.

As shown in FIG. 2, the first ring gear 13 and the second ring gear 23 are provided with a gap D in the axial direction, that is, the first ring gear 13 and the second ring gear 23 are axially spaced apart from each other, not Closely fit. For the person skilled in the art, the width of the meshing portion of the first planet gear 12 and the second planet gear 22 determines the size of the gap D, that is, the width of the meshing portion of the first planet gear 12 and the second planet gear 22. It is equal to the minimum value of the gap D, so by controlling the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22, the size of the gap D can be indirectly controlled, and the first one is guaranteed by those skilled in the art. The width of the meshing portion of the first planetary gear 12 and the second planetary gear 22 can be stabilized under the premise that the planetary gear 12 and the second planetary gear 22 can stably transmit power and the service life of the first planetary gear 12 and the second planetary gear 22 The arrangement is relatively narrow, so that the gap D can be effectively reduced, so that the axial dimension of the differential 100 is smaller, more compact, and easier to arrange.

It should be noted that the gap D of the above-mentioned FIG. 3 (in conjunction with FIGS. 1 to 2) refers to the distance between the annular side wall portion 162 of the first ring gear 13 and the annular side wall portion 162 of the second ring gear 23. For example, referring to the embodiment of FIGS. 1, 2, and 3, the first ring gear 13 and the second ring gear 23 both include a body flat plate portion 161 and an annular side wall portion 162.

In still other embodiments of the present invention, as in the embodiment of Figures 8 and 9, each of the first ring gear 13 and the second ring gear 23 further includes an annular flange portion 163, an annular flange The portion 163 extends from the end surface of the annular side wall portion 162 in a direction away from the main body flat portion 161. In the embodiment of Fig. 8, the inner diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, such that the ring The flange portion 163 corresponds to the outwardly projecting annular side wall portion 162 (i.e., the outer peripheral surface of the first ring gear 13 or the second ring gear 23) in the radial direction. In the embodiment of FIG. 9, the outer diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, and the inner diameter of the annular flange portion 163 may be larger than the inner diameter of the annular side wall portion 162, that is, The thickness of the annular flange portion 163 is thinner than the thickness of the annular side wall portion 162.

However, it should be noted that in the ring gear structure of the embodiment of Figs. 1, 2 and 3, the gap D between the two ring gears refers to the gap between the annular side wall portions 162 of the two ring gears. In the ring gear structure of the embodiment of Figs. 8 and 9, the gap D between the two ring gears refers to the gap between the annular flange portions 163 of the two ring gears.

According to some embodiments of the present invention, since the first ring gear 13 and/or the second ring gear 23 may further include an annular flange portion 163, when such a ring gear structure is employed, due to the presence of the annular flange portion 163, The gap D can be at least partially reduced compared to the ring gear without the annular flange portion 163, and preferably, the gap D can be reduced to zero, for example, the first ring gear 13 and the second ring gear 23 can At the same time, the ring gear structure shown in FIG. 8 is adopted. At this time, the annular flange portion 163 of the first ring gear 13 and the end surface of the annular flange portion 163 of the second ring gear 23 can be substantially fitted together, so that the gap D is Zero, so the installation space A is more closed, and the external debris is more difficult to enter into the installation space A and affect the moving parts, ensuring The stable operation of the differential 100 is achieved. It should be understood, of course, that the description herein is merely illustrative and is not to be construed as a limitation of the scope of the present invention. After reading the above, it is understood that the arrangement of the annular flange portion 163 can further After reducing the gap D and even reducing the gap D to zero, the type of the ring gear can be flexibly selected for combination, for example, ensuring that at least one of the ring gears has the annular flange portion 163, so that the gap D can be further reduced. Even the gap D is reduced to zero, so that the installation space A is more encrypted.

Further, as an alternative embodiment, the first ring gear 13 and the second ring gear 23 have the same radial dimension, and each of the first ring gear 13 and the second ring gear 23 may be an integrally formed component.

In addition, for the technical solutions and/or technical features described in the foregoing embodiments, those skilled in the art can perform the technical solutions and/or technical features in the foregoing embodiments with each other without conflicting or contradicting each other. The combined technical solution may be a superposition of two or more technical solutions, a superposition of two or more technical features or a superposition of two or more technical solutions and technical features, thereby enabling The technical solutions and/or technical features interact and support each other functionally, and the combined solution has a superior technical effect.

For example, a person skilled in the art can partially overlap the first planet gear 12 and the second planet gear 22 with a scheme in which the first planet carrier 11 and the second planet carrier 21 are plate-like structures, which can effectively reduce the differential speed. The axial dimension of the device 100 is such that the volume of the differential 100 is smaller.

For another example, a person skilled in the art can combine the solution that the first planetary gear 12 and the second planetary gear 22 partially overlap with the solution that the planetary gear and the carrier are housed in the installation space, so that the differential 100 can be effectively reduced. The axial size also allows the planet wheels and planet carrier to be hidden in the installation space to avoid damage to the outside, which increases the service life and reduces maintenance costs.

For another example, a person skilled in the art may adjust the revolving axis of the first planet gear 12 to the revolving axis of the second planet gear 22 and the revolving radius of the first planet gear 12 to be the same as the revolving radius of the second planet gear 22 . The combination makes the structure of the differential 100 more compact, smaller in size, and easier to arrange.

Of course, it should be understood that the above-described exemplary descriptions are merely illustrative, and for a combination of technical solutions and/or technical features, those skilled in the art can freely combine without conflict, and the combined solutions have more The superior technical effect, the present invention has only been briefly described in the above several examples, and is not exhaustive here.

In addition, it is to be understood that the above-described combined technical solutions are also within the scope of the present invention.

In general, the differential 100 according to an embodiment of the present invention can effectively save space and reduce weight. Specifically, the planetary gear differential 100 is compared to a conventional bevel gear differential. The weight can be reduced by about 30%, and the axial dimension is reduced by about 70%, which not only reduces the friction of the bearing, but also realizes the torque distribution of the left and right wheels, makes the load distribution of the differential 100 more reasonable, and the differential 100 is more rigid. Well, in addition to the use of cylindrical gears, the transmission efficiency is also improved. For example, the conventional bevel gear transmission efficiency of 6-level accuracy and 7-level accuracy is about 0.97 to 0.98, and the efficiency of the spur gear transmission of 6-level precision and 7-level precision is about 0.98 to 0.99, in addition to cylindrical gears, The operating noise of the differential 100 is also reduced, while the heat generation is reduced, greatly increasing the life of the differential 100. In short, the differential 100 according to the embodiment of the present invention has many advantages such as light weight, small size, low cost, high transmission efficiency, low noise, low heat generation, and high life.

Meanwhile, since the differential 100 according to the embodiment of the present invention can omit the sun gear, the elimination of the sun gear can have the following advantages:

From the mechanical analysis, the sun gear is cancelled, but the ring gear is used to realize the differential speed, because the number of teeth of the ring gear can be set more than the sun wheel, and the pitch circle is larger (the pitch circle refers to the gear meshing transmission at the node) A pair of tangential circles), so that the load and the withstand torque can be distributed more evenly, which is advantageous for the improvement of the life of the differential 100. At the same time, there is no sun gear, and the lubrication and cooling of the differential 100 can be better realized. That is, since the sun gear is eliminated, a cavity can be formed in the planetary gear, and the meshing of the ring gear and the planetary gear is internal engagement. (The sun gear and the planet gear are externally meshed), and the gear ring can store lubricating oil, thereby greatly improving the cooling and lubrication effect. In addition, since the sun gear is eliminated, the components are reduced, the quality and cost of the differential 100 are reduced, and the differential 100 is further reduced in size and weight.

A power drive system 1000 according to an embodiment of the present invention, which includes the differential 100 in the above embodiment, will be briefly described below. As shown in FIG. 10, the power drive system 1000 includes a differential 100, a transmission 200, and a power source 300. The power outputted by the power source 300 is output to the differential 100 through the shifting action of the transmission 200, and then distributed by the differential 100. Give the drive wheels on both sides. It is to be understood that the power drive system 1000 illustrated in FIG. 10 is merely an example and is not a limitation of the scope of the present invention. Moreover, it should be understood that other configurations of the differential, such as engines, transmissions, and the like, in accordance with embodiments of the present invention are known in the art and are well known to those skilled in the art and therefore will not be described again.

Next, a power drive system 1000 according to an embodiment of the present invention will be described in detail by taking the power drive system 1000 shown in FIG. 12 as an example.

As shown in FIG. 12, the differential 100 may further include: a power engagement device 400 and a joint driving device 500. Of course, the power drive system 1000 may further include other components, such as a first motor generator and a second motor generator. .

The power engagement device 400 may include a first engagement portion 410 and a second engagement portion 420 that is coupled to one of the first ring gear 13 and the second ring gear 23, the second engagement portion 420 and the first planet carrier 11 and the second planet carrier 21 rotate in synchronization. The first engaging portion 410 and the second engaging portion 420 are selectively engageable, and since the first carrier 11 and the second carrier 21 constitute a power input end of the differential 100, the first ring gear 13 and the second ring gear 23 For the power output end of the differential 100, the first engaging portion 410 may rotate synchronously with one of the first ring gear 13 and the second ring gear 23. When the first engaging portion 410 and the second engaging portion 420 are engaged, the power can be directly transmitted into the first ring gear 13 or the second ring gear 23, so that the output power of the first ring gear 13 and the second ring gear 23 can be made the same.

As shown in FIG. 12, the joint driving device 500 includes a driving needle 510 and a driving portion, the driving needle 510 is disposed to be rotatable with the first carrier 11 and the second carrier 21, and the driving needle 510 can be opposite to the first planet. Frame 11 and The two planet carriers 21 are axially moved. The two ends of the driving pin 510 are respectively engaged with the driving portion and the second engaging portion 420. The driving portion is configured to drive the driving pin 510 to drive the second engaging portion 420 toward the first joint in the axial direction. The direction of the portion 410 is moved such that the second engaging portion 420 engages the first engaging portion 410. That is, the driving portion may be used to drive the driving needle 510 to move axially, and the axially moving driving needle 510 may urge the second engaging portion 420 to move axially to engage the second engaging portion 420 and the first engaging portion 410.

The first motor generator is disposed to be coupled to the first ring gear 13 and the coupled power output is to one of a pair of wheels, and the second motor generator is disposed to be coupled to the second ring gear 23 and coupled The rear power is output to the other of the pair of wheels. The pair of wheels can be a set of front wheels or a set of rear wheels.

The conventional electric lock-type differential incorporates an electric actuating locking mechanism based on a common open differential, so that the differential has a locking function and is locked by an electric control differential. This is an electric lock differential that is usually applied to a centralized drive type fuel vehicle, that is, the power is distributed to the left and right half shafts respectively after passing through the final drive and the differential, and the left and right wheel speeds are adjusted by the differential. difference. However, it cannot be directly applied to electric vehicles. Such an electric lock differential is bulky and an electric vehicle has no engine.

Thus, the drive shaft locking device 100 of the present invention is significantly different in structure and implementation from the conventional electric lock-up differential, whereby the joint driving device 500 drives the second engaging portion 420 to engage the first engagement. After the joint portion 410 is engaged, the output rotational speeds of the first ring gear 13 and the second ring gear 23 are the same, so that the synchronous locking of the two half shafts can be realized, which can be advantageous for improving the vehicle's ability to remove the trap.

According to a preferred embodiment of the invention, the first planetary axle 14 and/or the second planetary axle 24 may constitute a drive needle 510. That is, the first planetary axle 14 can be used as the drive pin 510, or the second planetary axle 24 can be used as the drive pin 510, or the first planetary axle 14 and the second planetary axle 24 can be used simultaneously as the drive pin 510.

According to another preferred embodiment of the invention, the drive pin 510 is spaced apart from the first planetary axle 14 and the second planetary axle 24. In other words, the drive pin 510 is a separately arranged component such that modifications to the first planetary axle 14 and the second planetary axle 24 can be reduced, and the first planetary axle 14 and the second planetary axle 24 can be maintained at an appropriate length, and Conducive to the design and manufacture of the differential.

According to still another preferred embodiment of the present invention, at least one of the first planetary axle 14, the second planetary axle 24 and the drive pin 510 is coupled to the second engagement portion 420 such that the second engagement portion 420 follows the first planet carrier 11 The second carrier 21 rotates in synchronization. That is, the component connected to the second joint portion 420 may be at least one of the above three components, and since the three components are all rotated in synchronization with the first planet carrier 11 and the second planet carrier 21, this may cause the second component The engaging portion 420 is rotatable in synchronization with the first carrier 11 and the second carrier 21.

According to an optional embodiment of the present invention, as shown in FIGS. 12 and 13, an annular sleeve 600 may be disposed between the first engaging portion 410 and one of the first ring gear 13 and the second ring gear 23, The sleeve 600 surrounds the second joint portion 420. Thereby, the sleeve 600 can function as a connection, and the first joint portion 410 and the first ring gear 13 and the second ring gear 23 can be secured. One of the synchronous rotations, and the sleeve 600 can also function to protect the second engaging portion 420 at least to some extent.

Further, as shown in FIG. 12 and FIG. 13, the power drive system 1000 may further include: an elastic device 700 elastically disposed between the first joint portion 410 and the second joint portion 420 to make the second joint portion The 420 has a tendency to move away from the first joint 410. When the second engaging portion 420 needs to be disconnected from the first engaging portion 410, the elastic device 700 may provide the second engaging portion 420 with an elastic force to urge the second engaging portion 420 to move away from the first engaging portion 410.

Preferably, the resilient device 700 can be received within the sleeve 600. Thus, the elastic device 700 can be disposed within the sleeve 600, and the sleeve 600 can function to protect the elastic device 700, thereby reducing the risk of failure of the elastic device 700.

As shown in FIG. 12, one of the first ring gear 13 and the second ring gear 23 has an integrally formed annular extension that constitutes the sleeve 600. This makes it possible to make one of the first ring gear 13 and the second ring gear 23 simple in structure and easy to manufacture.

As shown in FIG. 13 , the driving portion may include a follower portion 520 , the follower portion 520 can rotate with the driving pin 510 , and the follower portion 520 can be braked, and the driving portion 520 is provided with a driving surface 530 . When the follower 520 is braked, the sliding of the driving pin 510 on the driving surface 530 is changed to change the position of the driving pin 510 and the driving surface 530, thereby driving the driving surface 530 to drive the driving pin 510 to move in the axial direction, so that the first The second joint portion 420 engages the first joint portion 410. It can be understood that the follower portion 520 and the driving pin 510 may be in a synchronous rotation relationship before the follower portion 520 is not braked, but after the follower portion 520 is braked, the rotation speed of the follower portion 520 is decreased. A difference in rotational speed will occur between the follower 520 and the drive pin 510, such that the drive pin 510 can slide over the drive surface 530 of the follower 520, and the drive pin 510 after sliding can be relative to the first planet carrier 11 and the second planet The frame 21 is axially moved, so that the driving pin 510 can bring the second engaging portion 420 closer to the first engaging portion 410 until the second engaging portion 420 is engaged with the first engaging portion 410.

Further, the driving portion may further include: a braking portion that is provided for braking the follower portion 520. That is, the braking portion can function as the brake follower 520, and the braking portion can brake the follower portion 520 when the first engaging portion 410 and the second engaging portion 420 are required to be engaged.

Preferably, the braking portion may be arranged to brake the follower 520 with electromagnetic force. The electromagnetic force control is precise and reliable, so that the operational reliability of the drive shaft locking device can be improved, and the service life of the drive shaft locking device can be extended. For example, the driving portion may be an electromagnetic brake, the follower portion 520 constitutes a brake member of the electromagnetic brake, and the braking portion constitutes a brake bracket of the electromagnetic brake.

According to a specific embodiment of the present invention, as shown in FIG. 14, the driving surface 530 may be a bevel or a curved surface. By providing the drive surface 530 as a bevel or curved surface, it is possible to facilitate the sliding of the drive needle 510 on the drive surface 530 and to cause the drive needle 510 to move in the axial direction.

Further, the driving surface 530 may include: a first segment 530a and a second segment 530b. The first segment 530a and the second segment 530b are connected, and the connection between the first segment 530a and the second segment 530b is the lowest point, and the first segment 530a And the second paragraph 530b The other end away from the connection is the highest point. Thus, when one end of the driving pin 510 is at the lowest point, the first engaging portion 410 and the second engaging portion 420 are in a separated state, and when one end of the driving pin 510 is at the highest point or adjacent to the highest point, the first engaging portion 410 and The second joint portion 420 is in an engaged state. Thus, by properly arranging the driving surface 530, it is possible to facilitate the sliding of the driving pin 510 between the lowest point and the highest point, which can facilitate the engagement of the first engaging portion 410 and the second engaging portion 420, and can facilitate the lifting of the driving shaft lock. The operational reliability of the device.

Preferably, each of the first segment 530a and the second segment 530b may be arcuate. The first segment 530a and the second segment 530b of the arc shape may facilitate sliding of one end of the driving pin 510 on the driving surface 530, and the movement resistance of the driving pin 510 may be reduced.

Optionally, each of the first segment 530a and the second segment 530b has a corresponding center angle. Thus, the first segment 530a and the second segment 530b are substantially identical, such that the drive pin 510 can be more slidable on the drive surface 530.

Alternatively, the drive surface 530 can be multi-segmented and the multi-segment drive faces 530 are circumferentially spaced apart. Thus, the number of driving pins 510 can correspond to the number of driving faces 530, which can increase the number of driving pins 510, so that the plurality of driving pins 510 and the second engaging portion 420 can be made to be reliable, and the second engaging portion can be made The 420 axial movement is reliable, which makes the drive shaft locking device work more reliably.

The plurality of driving surfaces 530 can be connected by a connection plane, and the connection plane is flush with the highest point. This can improve the structural reliability of the driving surface 530 of the follower portion 520 at least to some extent, and can improve the structural reliability of the driving shaft locking device.

According to an optional embodiment of the present invention, as shown in FIG. 14, the follower portion 520 may include: a follower body 520a and an annular follower flange 520b disposed on the follower body 520a, the follower portion A drive surface 530 is provided on an end surface of the flange 520b facing the drive pin 510. Thus, the follower body 520a can effectively enhance the structural reliability of the follower portion 520, and the driving surface 530 can be disposed on the end surface of the follower portion flange 520b, so that the design difficulty of the driving surface 530 can be reduced, and the driving surface 530 can be improved. Structural reliability.

Further, as shown in FIG. 14, the driving surface 530 may be provided with a driving surface limiting groove 530c, and one end of the driving pin 510 is located in the driving surface limiting groove 530c. Therefore, by providing the driving surface limiting groove 530c, one end of the driving pin 510 can be engaged in the driving surface limiting groove 530c, so that at least a certain end of the driving pin 510 can be prevented from being detached from the driving surface 530, which can be improved. The reliability and stability of the drive needle 510 moving within the drive surface 530.

The operation of the differential according to an embodiment of the present invention will be described in detail below.

When the vehicle is trapped and slipped, the driver controls the electromagnetic brake to be energized, and the brake frame brakes the brake member, so that the rotation speed of the brake member is suppressed, and a rotation speed difference is generated between the drive needle 510 and the brake member, and the drive needle 510 is The driving surface 530 of the brake member slides, the driving needle 510 can slide from the lowest point of the driving surface 530 to the highest point or the position adjacent to the highest point, and the driving needle 510 is axially moved to one side of the second engaging portion 420 to drive The needle 510 can also drive the second engaging portion 420 to gradually approach the first engaging portion 410 until the first engaging portion 410 and the second engaging portion 420 are engaged, at this time, the left and right half shafts Synchronous rotation, the left wheel Z1 and the right wheel Z2 are at the same speed, so that the vehicle's ability to escape can be improved.

After the vehicle is out of sleep, the driver can press the electromagnetic brake again, the electromagnetic brake is de-energized, and the elastic device pushes the second engaging portion 420 to move axially away from the first engaging portion 410. In the process, the driving pin 510 follows the first The two engaging portions 420 are axially moved, and the end of the driving pin 510 that cooperates with the driving surface 530 can be gradually slid from the highest point or the position adjacent to the highest point to the lowest point. At this time, the second engaging portion 420 and the first engaging portion 410 are completely Separate, the vehicle can continue to travel according to the normal straight-line driving of the vehicle and the normal turning mode of the vehicle.

Referring to FIG. 11, a vehicle 10000 according to an embodiment of the present invention, which includes the power drive system 1000 of the above embodiment, which can be used for a front drive and of course for a rear drive, will be briefly described below. The present invention is not particularly limited thereto.

In the description of the present specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example" or "some examples" and the like means a specific feature described in connection with the embodiment or example, A structure, material or feature is included in at least one embodiment or example of the invention. In the present specification, the schematic representation of the above terms is not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. Further, various embodiments or examples described in the specification may be combined and combined by those skilled in the art.

Although the embodiments of the present invention have been shown and described, it is understood that the above-described embodiments are illustrative and are not to be construed as limiting the scope of the invention. The embodiments are subject to variations, modifications, substitutions and variations.

Claims

A differential for a vehicle, comprising:

a first planet carrier, a first planet gear, and a first ring gear, the first planet gear being disposed on the first planet carrier, the first planet gear meshing with the first ring gear;

a second planet carrier, a second planet gear and a second ring gear, the second planet gear being disposed on the second planet carrier, the second planet gear meshing with the second ring gear and the second The planet gear is also meshed with the first planet gear;

Wherein the first ring gear and the second ring gear constitute two power output ends of the differential, and the first planet carrier and the second planet carrier constitute a power input end of the differential;

a power engagement device including a first engagement portion and a second engagement portion, the first engagement portion being coupled to one of the first ring gear and the second ring gear, the second engagement portion being The first planet carrier and the second planet carrier rotate synchronously;

a joint driving device, the joint driving device comprising: a driving needle and a driving portion, the driving needle being disposed to be rotatable about the central axis with the first planet carrier and the second planet carrier, and a planet carrier and the second planet carrier are axially moved, and two ends of the driving pin are respectively engaged with the driving portion and the second engaging portion, and the driving portion is configured to drive the driving pin to drive The second engaging portion moves in a direction toward the first engaging portion in the axial direction, thereby causing the second engaging portion to engage the first engaging portion.
A differential for a vehicle according to claim 1, wherein each of said first planet gears is provided with a first planetary axle, and both ends of said first planetary axle are respectively said a first planet carrier coupled to the second planet carrier, each of the second planet gears being configured with a second planet gear axle, the two ends of the second planet gear axle being respectively associated with the first planet carrier and The second planet carrier is connected.
A differential for a vehicle according to claim 2, wherein said first planetary axle and/or said second planetary axle constitute said drive needle.
A differential for a vehicle according to claim 2, wherein said drive pin is spaced apart from said first planetary axle and said second planetary axle.
The differential for a vehicle according to claim 2, wherein at least one of the first planetary axle, the second planetary axle, and the drive pin is coupled to the second engagement portion, So that the second joint rotates synchronously with the first planet carrier and the second planet carrier.
The differential for a vehicle according to any one of claims 1 to 5, wherein the first engaging portion and the one of the first ring gear and the second ring gear An annular sleeve is disposed between the sleeves surrounding the second joint.
The differential for a vehicle according to any one of claims 1 to 6, further comprising: elastic means elastically disposed at the first joint portion and the second portion Between the joints to make the second The joint has a tendency to move away from the first joint.
A differential for a vehicle according to claim 7, wherein said elastic means is housed in said sleeve.
A differential for a vehicle according to claim 6, wherein said one of said first ring gear and said second ring gear has an integrally formed annular extension, said annular extension The sleeve is constructed.
The differential for a vehicle according to any one of claims 1 to 9, wherein the first planetary gear and the second planetary gear have different thicknesses in the axial direction.
A differential for a vehicle according to claim 10, wherein the teeth of the thinner planet wheels are fully meshed with the teeth of the thicker planet wheels, and the teeth of the thicker planet wheels are at the axis The teeth extending upwards beyond one side of the thinner planet wheel or the teeth of the thicker planet wheel extend axially outwards beyond the teeth of the thinner planet wheel.
A differential for a vehicle according to claim 10, wherein the radius of revolution of the thicker planet gear is smaller than the radius of revolution of the thinner planet wheel.
The differential for a vehicle according to claim 10, wherein the ring gear corresponding to the thicker planetary gear is a small ring gear, and the ring gear corresponding to the thinner planetary gear is a large ring gear, the large The outer diameter of the ring gear is larger than the outer diameter of the small ring gear.
The differential for a vehicle according to claim 10, wherein a thickness of the first planetary gear is greater than a thickness of the second planetary gear, and the first ring gear is a small ring gear, The second ring gear is a large ring gear, and the revolution radius of the first planet gear is smaller than the revolution radius of the second planet gear.
The differential for a vehicle according to any one of claims 1 to 14, wherein the driving portion comprises:

a follower portion, the follower portion is rotatable with the drive pin, and the follower portion is braked, the follower portion is provided with a drive surface, and the follower portion is braked when passed The sliding of the driving needle on the driving surface causes the driving surface to drive the driving needle to move in the axial direction such that the second engaging portion engages the first engaging portion.
The differential for a vehicle according to claim 15, wherein the driving portion further comprises:

a braking portion, the braking portion being configured to brake the follower portion.
A differential for a vehicle according to claim 16, wherein the braking portion is configured to brake the follower portion with an electromagnetic force.
A differential for a vehicle according to claim 17, wherein said driving portion is an electromagnetic brake, said follower portion constitutes a brake member of said electromagnetic brake, and said braking portion constitutes said Brake stand for electromagnetic brakes.
A differential for a vehicle according to any one of claims 15 to 18, wherein the driving surface is a bevel or a curved surface.
The differential for a vehicle according to any one of claims 15 to 18, wherein the driving surface comprises: a first segment and a second segment, the first segment and the second segment Connected, the first segment and the second segment The junction is the lowest point, and the other end of the first segment and the second segment away from the connection is the highest point.
A differential for a vehicle according to claim 20, wherein said follower portion includes: a follower portion body and an annular follower flange provided on said follower portion body, The drive surface is provided on an end surface of the follower flange facing the drive pin.
The differential for a vehicle according to claim 21, wherein the driving surface is provided with a driving surface limiting groove, and one end of the driving pin is located in the driving surface limiting groove.
A vehicle characterized by comprising a differential for a vehicle according to any one of claims 1-22.