CN114321318A - Multifunctional differential and automobile - Google Patents
Multifunctional differential and automobile Download PDFInfo
- Publication number
- CN114321318A CN114321318A CN202011058344.XA CN202011058344A CN114321318A CN 114321318 A CN114321318 A CN 114321318A CN 202011058344 A CN202011058344 A CN 202011058344A CN 114321318 A CN114321318 A CN 114321318A
- Authority
- CN
- China
- Prior art keywords
- differential
- planetary gear
- shaft
- input shaft
- planet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000008878 coupling Effects 0.000 claims description 29
- 238000010168 coupling process Methods 0.000 claims description 29
- 238000005859 coupling reaction Methods 0.000 claims description 29
- 230000036316 preload Effects 0.000 claims description 16
- 239000000446 fuel Substances 0.000 abstract description 8
- 230000007246 mechanism Effects 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 15
- 230000005540 biological transmission Effects 0.000 description 14
- 230000009471 action Effects 0.000 description 9
- 230000001960 triggered effect Effects 0.000 description 6
- 239000010720 hydraulic oil Substances 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
Images
Landscapes
- Retarders (AREA)
Abstract
The invention belongs to the technical field of differentials, and particularly relates to a multifunctional differential and an automobile, wherein the multifunctional differential comprises a differential component and a switching component; the differential assembly comprises a planetary gear row connecting a first half shaft and a second half shaft of the automobile; the switching assembly comprises an input shaft and a switching device; the input shaft switching device is selectively combined with the planetary gear row and the input shaft; when the switching device is separated from the planetary gear row and the input shaft, the multifunctional differential is in an idle state; when the switching device is combined with the planetary gear row and the input shaft at the same time, the multifunctional differential is in the same speed state; the switching device is combined with the input shaft, and when the switching device is separated from the planetary gear row, the multifunctional differential is in a differential state. According to the multifunctional differential mechanism, the function of normal differential running of the automobile can be realized, and the functions of idling and same speed can be realized, so that the difficulty-escaping capability and the fuel economy of the automobile are improved.
Description
Technical Field
The invention belongs to the technical field of differentials, and particularly relates to a multifunctional differential and an automobile.
Background
With the continuous development of automobile technology, people's demands for automobiles are not only limited to vehicles, but also pursue higher comfort of automobiles, fuel economy and the like. The differential mechanism is usually composed of a planetary gear and a sun gear, and the meshing of the planetary gear and the sun gear can realize the differential function of the left wheel end and the right wheel end of the automobile, so that the normal running of the automobile can be realized. In the prior art, a differential mechanism in the prior art can only realize the differential function of an automobile, but cannot realize the locking function of automobile wheels, and cannot meet the requirement that the wheel end must have stronger escaping capability under the working conditions that the automobile is over a pothole or is trapped and the like; in addition, the structure of the transmission is complex, the weight is heavy, and the quantitative arrangement of the automobile is not facilitated.
Disclosure of Invention
The invention solves the technical problems that in the prior art, a transmission cannot meet the requirement that the wheel end escaping capability of an automobile is not strong under the working conditions of over-pothole or trapped and the like, and provides a multifunctional differential and an electric automobile.
In view of the above problems, an embodiment of the present invention provides a multi-function differential including a differential assembly and a switching assembly; the differential assembly comprises a planetary gear row connecting a first half shaft and a second half shaft of the automobile; the switching assembly comprises an input shaft and a switching device; the switching device selectively couples the planetary gear row and the input shaft;
when the switching device is separated from both the planetary gear row and the input shaft, the multi-function differential is in an idle state; when the switching device is combined with the planetary gear row and the input shaft at the same time, the multifunctional differential is in the same speed state; the switching device is coupled to the input shaft, and the multi-function differential is in a differential state when the switching device is separated from the planetary gear row.
Optionally, the planetary gear rows include a first planetary gear row and a second planetary gear row meshed with the first planetary gear row; the first planetary gear row includes a first sun gear and a plurality of first planet gears; the second planetary gear row includes a second sun gear and a plurality of second planet gears; the first sun gear is meshed with all the first planet gears; the second sun gear is meshed with all the second planet gears; the input shaft, the first sun gear and the second sun gear are coaxially arranged; the first planet gears and the second planet gears are equal in number and are arranged in a staggered mode; each first planet wheel is meshed with one second planet wheel adjacent to the first planet wheel; each second planet wheel is meshed with one adjacent first planet wheel;
the differential assembly further comprises a first planet carrier and a second planet carrier connected with the first planet carrier; the second planet carrier is also provided with a groove for accommodating the second planet gear row, and a mounting space for mounting the first planet gear row and the second planet gear row is formed between the first planet carrier and the second planet carrier.
Optionally, the differential assembly further includes a first shaft pin and a second shaft pin arranged in parallel with the central shaft of the first sun gear, the first planet carrier is provided with a first shaft hole, a first pin hole and a second pin hole, and the second planet carrier is provided with a second shaft hole, a third pin hole and a fourth pin hole; the two opposite ends of the first shaft pin are respectively arranged in the first pin hole and the third pin hole, and the first planet wheel is arranged on the first shaft pin; two opposite ends of the second shaft pin are respectively installed in the second pin hole and the fourth pin hole, and the second planet wheel is installed on the second shaft pin; and a first half shaft of the automobile penetrates through the first shaft hole to be connected with the first sun gear, and a second half shaft of the automobile penetrates through the second shaft hole to be connected with the second sun gear.
Optionally, a first oil hole is formed in the first shaft pin, and a second oil hole is formed in the second shaft pin.
Optionally, the switching means is a coupling ring; the inner wall of the combination ring is provided with inner teeth, one end of the input shaft, which is close to the planetary gear row, is provided with combination teeth matched with the inner teeth, and the switching assembly further comprises a connecting gear which is coaxially connected with the planetary gear row and is matched with the inner teeth; the coupling ring is coupled to the input shaft through engagement of the internal teeth with the coupling teeth, and the coupling ring is coupled to the planetary gear row through engagement of the internal teeth with the connecting gear.
Optionally, the switching assembly further comprises a housing and a preload member; the shell is provided with a mounting hole for accommodating the combination teeth, the connecting gear, the combination ring and the preload piece; a convex ring is arranged on the inner wall of the mounting hole; one end of the preload piece is abutted to the convex ring, and the other end of the preload piece is abutted to the combination ring.
Optionally, the outer wall of the combination ring is provided with external teeth, the inner wall of the mounting hole is provided with a sliding groove adapted to the external teeth, and the combination ring slides along the sliding groove in the mounting hole to control the internal teeth to combine with or separate from the combination teeth and/or the connecting gear.
Optionally, the multi-function differential further comprises an actuation assembly; the executing assembly comprises a separating bearing and at least two ejector pins;
the first planet carrier is provided with at least two first needle holes with the number equal to that of the thimbles, and the second planet carrier is provided with a sliding shaft and at least two second needle holes with the number equal to that of the thimbles; the release bearing is connected to the sliding shaft; one end of the ejector pin is connected to the release bearing, and the other end of the ejector pin sequentially penetrates through the second needle hole and the first needle hole and abuts against the switching device.
Optionally, the release bearing comprises a pressure plate and a piston mounted on the pressure plate; and a needle groove for mounting the thimble is formed in the end face, far away from the piston, of the pressure plate.
When the switching device is separated from the planetary gear row and the input shaft, the input shaft is driven to idle under the action of external driving force, namely, the external driving force only can drive the input shaft to rotate and cannot drive a first half shaft and a second half shaft of an automobile through the planetary gear row, for example, when the multifunctional speed changer is used for driving a four-wheel drive automobile in a front driving mode and the automobile runs in a single-front driving mode, the connection between a front wheel and a front power assembly can be independently cut off; or when the multifunctional transmission is used for rear drive of a four-wheel drive vehicle and the vehicle runs under a single rear drive working condition, the rear wheel can be independently connected with the rear driving force assembly; therefore, the multifunctional differential reduces the resistance and the drag torque of the automobile and improves the fuel economy of the automobile. Secondly, when the switching device is combined with the planetary gear row and the input shaft at the same time, the multifunctional differential is in the same speed state, and at the moment, the input shaft, the switching device and the planetary gear row have the same rotating speed; that is, when the automobile wheels are trapped, the multifunctional differential can be in the same speed state, at the moment, the rotating speeds of the input shaft, the switching device and the planetary gear row are the same, and the external driving force needs to output a large torque to drive the input shaft to rotate, so that the trapping removal capability of the automobile is improved. And thirdly, when the switching device is combined with the input shaft and is separated from the planetary gear row, the input shaft drives the planetary gear row to rotate through the switching device under the action of external driving force, so that the function of normal differential driving of the automobile is realized. According to the multifunctional differential mechanism, the function of normal differential running of the automobile can be realized, and the functions of idling and same speed can be realized, so that the difficulty removing capability and the fuel economy of the automobile are improved.
An embodiment of the invention further provides an automobile comprising the multifunctional differential.
Drawings
The invention is further illustrated with reference to the following figures and examples.
FIG. 1 is an exploded view of a multi-function differential according to an embodiment of the present invention;
FIG. 2 is a schematic view of an assembled structure of the multi-function differential according to an embodiment of the present invention;
FIG. 3 is a cross-sectional view of a multi-function differential provided in accordance with an embodiment of the present invention;
FIG. 4 is a schematic diagram illustrating the switching assembly and the first sun gear of the multi-function differential according to an embodiment of the present invention;
FIG. 5 is a schematic structural view of a housing of a controller of the multi-function differential according to an embodiment of the present invention;
FIG. 6 is a schematic view of an input shaft of the multi-function differential according to an embodiment of the present invention;
FIG. 7 is a front view of a switching device of the multi-function differential according to an embodiment of the present invention;
fig. 8 is a schematic structural view of a switching device, coupling teeth, and a connecting gear of the multi-function differential according to an embodiment of the present invention;
FIG. 9 is a schematic structural view of an actuator assembly of the multi-function differential according to an embodiment of the present invention;
FIG. 10 is a schematic view of the first sun gear and connecting gear of the multi-function differential according to one embodiment of the present invention;
fig. 11 is a schematic structural view of a first carrier of the multi-function differential according to an embodiment of the present invention;
FIG. 12 is a schematic structural diagram of a second planet carrier of the multi-function differential according to an embodiment of the present invention;
FIG. 13 is a schematic view of a pressure plate of the multi-function differential in accordance with an embodiment of the present invention;
FIG. 14 is a cross-sectional view of a throwout bearing of the multi-function differential provided in accordance with one embodiment of the present invention;
FIG. 15 is a schematic view of the switching device of the multi-function differential shown disengaged from both the planetary gear set and the input shaft in accordance with one embodiment of the present invention;
FIG. 16 is a schematic view of the switching device of the multi-function differential in combination with both the planetary gear set and the input shaft in accordance with one embodiment of the present invention;
fig. 17 is a schematic view of the switching device of the multi-function differential according to the embodiment of the present invention, which is coupled to the input shaft, and is separated from the planetary gear row.
The reference numerals in the specification are as follows:
1. a differential assembly; 11. a planet gear row 111, a first planet gear row; 1111. a first sun gear; 1112. a first planet gear; 112. a second planetary gear row; 1121. a second sun gear; 1122. a second planet wheel; 12. a first carrier; 121. a first shaft hole; 122. a first pin hole; 123. a second pin hole; 124. a first pinhole; 13. a second planet carrier; 131. a groove; 132. a second shaft hole; 133. a third pin hole; 134. a fourth pin hole; 135. a second pinhole; 136. a sliding shaft; 14. a first shaft pin; 15. a second shaft pin; 2. a switching component; 21. an input gear; 22. an input shaft; 221. a coupling tooth; 23. a switching device; 231. internal teeth; 232. an outer tooth; 24. a housing; 241. mounting holes; 242. a chute; 243. a convex ring; 25. a connecting gear; 26. pre-tightening piece; 27. a bearing; 3. an execution component; 31. a thimble; 32. separating the bearing; 321. a platen; 3211. a needle groove; 322. a piston; 4. a first half shaft; 5. a second half shaft.
Detailed Description
In order to make the technical problems, technical solutions and advantageous effects solved by the present invention more clearly apparent, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
It is to be understood that the terms "upper", "lower", "left", "right", "front", "rear", "middle", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are only for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the referenced components or elements must have a particular orientation, be constructed in a particular orientation, and be operated, and thus are not to be construed as limiting the present invention.
As shown in fig. 1 to 3, an embodiment of the present invention provides a multi-function differential, which includes a differential assembly 1 and a switching assembly 2; the differential assembly 1 comprises a planetary gear row 11 connecting a first half shaft 4 and a second half shaft 5 of the automobile; the switching assembly 2 comprises an input shaft 22 and a switching device 23; the switching device 23 selectively couples the planetary gear row 11 and the input shaft 22; it is to be understood that the planetary gear row 11 includes a first planetary gear row 111 and a second planetary gear row 112 meshed with the first planetary gear row 111; and the first planetary gear row 111 includes a first sun gear 1111 and a plurality of first planet gears 1112, and the second planetary gear row 112 includes a second sun gear 1121 and a plurality of second planet gears 1122; just be equipped with first internal spline on the first sun gear 1111, be equipped with on the first semi-axis 4 with the first external spline of first internal spline meshing, first semi-axis 4 is connected through intermeshing's first internal spline and first external spline first sun gear 1111, just first semi-axis 4 is kept away from the first wheel of car is connected to first sun gear 1111 one end.
The second sun gear 1121 is provided with a second internal spline, the second half shaft 5 is provided with a second external spline engaged with the second internal spline, the second half shaft 5 is connected with the second sun gear 11121 through the second internal spline and the second external spline which are engaged with each other, and one end of the first half shaft 5, which is far away from the second sun gear 1121, is connected with a second wheel of the automobile (the first wheel and the second wheel are two front wheels or two rear wheels of the automobile). So that the first half shaft 4 and the second half shaft 5 can perform a function of differential driving by the first planetary gear row 111 and the second planetary gear row 112.
Further, the input shaft 22 is connected to an output shaft of a transmission of an automobile, so that an external driving force (a motor driving force, an engine driving force, etc.) can drive the planetary gear set 11 to rotate through the input shaft 22.
When the switching device 23 is disengaged from both the planetary gear row 11 and the input shaft 22, the multifunction differential is in an idle state; when the switching device 23 is combined with the planetary gear row 11 and the input shaft 22 at the same time, the multi-function differential is in the same speed state; the switching device 23 is coupled to the input shaft 22, and the multifunction differential is in the differential state when the switching device 23 is separated from the planetary gear row 11. It is understood that when the multi-function differential is in the same speed state, the rotation speeds of the input shaft 22, the switching device 23 and the planetary gear set 11 are the same, and at this time, the multi-function differential cannot realize the differential function, and the rotation speeds of the two wheels on the front row or the rear row of the automobile are always the same.
Specifically, the specific operating states of the multifunction differential are as follows:
as shown in fig. 15, receiving an idle rotation command, controlling the switching device 23 to be separated from both the planetary gear train 11 and the input shaft 22, and the input shaft 22 drives the input shaft 22 to idle under the action of an external driving force; it is understood that the idle command may be a driving command manually triggered by a driver when the vehicle is running in a coasting condition; further, when it is determined that the vehicle is running under the coasting condition according to the vehicle running information (including the vehicle running speed and direction, acceleration, and the like), an idle command is automatically triggered, and at this time, the switching device 23 is controlled to be separated from both the planetary gear set 11 and the input shaft 22; therefore, the input shaft 22 is in an idle state (i.e. the rotation of the input shaft 22 does not drive the first planetary gear row 111 and the second planetary gear row 112 to rotate), i.e. the power of the transmission or the reduction gearbox of the automobile is disconnected from the wheel end of the automobile. Understandably, when the multifunctional transmission is used for driving a four-wheel drive vehicle in a front driving mode and the vehicle runs in a single front driving working condition, the connection between a front wheel and a front power assembly can be cut off independently; or when the multifunctional transmission is used for rear drive of a four-wheel drive vehicle and the vehicle runs under a single rear drive working condition, the rear wheel can be independently connected with the rear driving force assembly; therefore, the multifunctional differential can reduce the resistance and the drag torque of the automobile and improve the fuel economy of the automobile.
As shown in fig. 16, receiving a constant speed command, controlling the switching device 23 to simultaneously couple with the planetary gear set 11 and the input shaft 22, so that the input shaft 22 and the planetary gear set 11 are in a constant speed state; it is understood that the same speed command may be a driving command manually triggered by a driver when the automobile is driven in a pothole or trapped working condition; further, when the vehicle is over a pothole or is trapped, the switching device 23 is controlled to be simultaneously engaged with the planetary gear row 11 and the input shaft 22; at this time, the input shaft 22, the first planetary gear row 111 and the second planetary gear row 112 are tightly connected together, and the first half shaft 4 connected with the first sun gear 1111, and/or the half shaft connected with the second sun gear 1121 is in the same speed state due to the vehicle being trapped, and the external driving force needs to output a large torque to rotate the input shaft 22, so that when the multi-function transmission is in the locked state, the ability of the vehicle to escape from the trap can be improved.
As shown in fig. 17, when a differential command is received, the switching device 23 is controlled to be coupled with the input shaft 22, and the switching device 23 is controlled to be separated from the planetary gear train 11, the input shaft 22 drives the planetary gear train 11 to rotate through the switching device 23 under the action of an external driving force. It is understood that the differential command may be a command automatically triggered to confirm that the vehicle is in a normal driving state according to vehicle driving information (including vehicle traveling speed and direction, acceleration and the like). Further, when the automobile is in a normal driving state, a differential command is automatically triggered, at this time, the rotation of the input shaft 22 sequentially drives the first planetary gear row 111 and the second planetary gear row 112 to rotate through the input shaft 22 and the switching device 23, and the rotation of the first planetary gear row 111 and the second planetary gear row 112 can drive the first half shaft 4 and the second half shaft 5 to realize differential rotation, so that the normal differential driving of the automobile is realized.
In the invention, when the switching device 23 is separated from the planetary gear row 11 and the input shaft 22, the input shaft 22 drives the input shaft 22 to idle under the action of external driving force, so that the external driving force can only drive the input shaft 22 to rotate, and the connection between the front wheel and the front driving power assembly can be cut off independently, or the connection between the rear wheel and the rear driving power assembly can be cut off independently; therefore, the multifunctional differential can reduce the resistance and the drag torque of the automobile and improve the fuel economy of the automobile. Secondly, when the switching device 23 is simultaneously combined with the planetary gear row 11 and the input shaft 22, the multi-function differential is in the same speed state, that is, the rotation speeds of the input shaft 22, the switching device 23 and the planetary gear row 11 are the same, and when the automobile wheels are in a trapped state, the external driving force needs to output a large torque to drive the input shaft 22 to rotate, so that the trapping capability of the automobile is improved. When the switching device 23 is combined with the input shaft 22 and the switching device 23 is separated from the planetary gear row 11, the input shaft 22 drives the planetary gear row to rotate through the switching device 23 under the action of external driving force; thereby realizing the function of normal differential running of the automobile. According to the multifunctional differential mechanism, the function of normal differential running of the automobile can be realized, and the functions of idling and same speed can be realized, so that the difficulty removing capability and the fuel economy of the automobile are improved.
In one embodiment, as shown in fig. 9, the planetary gear row 11 includes a first planetary gear row 111 and a second planetary gear row 112 meshed with the first planetary gear row 111; the first planetary gear row 111 includes a first sun gear 1111 and a plurality of first planet gears 1112; the second planetary gear row 112 includes a second sun gear 1121 and a plurality of second planet gears 1122; the first sun gear 1111 meshes with all the first planetary gears 1112; the second sun gear 1121 is in mesh with all of the second planet gears 1122; the input shaft 22, the first sun gear 1111 and the second sun gear 1121 are coaxially disposed; the first planet gears 1112 and the second planet gears 1122 are equal in number and are arranged in a staggered manner; each first planet wheel 1112 is in mesh with its adjacent one of the second planet wheels 1122; each second planet 1122 is in mesh with its adjacent one of the first planet 1112; it can be understood that the number of the first planet gears 1112 and the second planet gears 1122 is the same, and the number of the first planet gears 1112 and the second planet gears 1122 can be set according to actual requirements; preferably, the number of the first planetary gears 1112 and the number of the second planetary gears 1122 are 3.
As shown in fig. 12 and 13, the differential assembly 1 further includes a first carrier 12 and a second carrier 13 connecting the first carrier 12; the second planet carrier 13 is further provided with a groove 131 for accommodating the second planet gear row 112, and a mounting space for mounting the first planet gear row 111 and the second planet gear row 112 is formed between the first planet carrier 12 and the second planet carrier 13. It can be understood that the second planet carrier is further provided with a groove 131 for accommodating the second planet gear row 112, so that the multifunctional differential has a simple structure and is convenient to install, and the design of the groove 131 makes the multifunctional differential more compact and enhances the strength of the multifunctional differential; meanwhile, due to the design of the groove 131, the weight of the multifunctional differential is reduced, and the lightweight design of an automobile is facilitated.
In an embodiment, as shown in fig. 9, 10 and 11, the differential assembly 1 further includes a first shaft pin 14 and a second shaft pin 15 disposed in parallel with a central axis of the first sun gear 1111, the first planet carrier 12 is provided with a first shaft hole 121, a first pin hole 122 and a second pin hole 123, and the second planet carrier 13 is provided with a second shaft hole 132, a third pin hole 133 and a fourth pin hole 134; the opposite ends of the first axle pin 14 are respectively installed in the first pin hole 122 and the third pin hole 133, and the first planet wheel 1112 is installed on the first axle pin 14; opposite ends of the second shaft pin 15 are respectively installed in the second pin hole 123 and the fourth pin hole 134, and the second planet wheel 1122 is installed on the second shaft pin 15; a first axle shaft 4 of the vehicle is connected to the first sun gear 1111 through the first axle hole 121, and a second axle shaft 5 of the vehicle is connected to the second sun gear 1121 through the second axle hole 132. It is understood that the number of the first axle pins 14, the first pin holes 122, and the third pin holes 133 is equal to the number of the first planet wheels 1112, and the number of the second axle pins 15, the second pin holes 123, and the fourth pin holes 134 is equal to the number of the second planet wheels 1122. The multifunctional differential mechanism is simple in structure and convenient to install.
In one embodiment, the first shaft pin 14 is provided with a first oil hole (not shown), and the second shaft pin 15 is provided with a second oil hole (not shown). It is understood that the first oil hole and the second oil hole respectively penetrate through the first shaft pin 14 and the second shaft pin 15, and the shapes of the first oil hole and the second oil hole can be set according to actual requirements; further, the first oil hole includes a first inner hole arranged along the axis of the first shaft pin 14, and a second inner hole arranged in the radial direction of the first shaft pin 14; one end of the first inner hole is communicated with the external environment, and the other end of the first inner hole is communicated with the second inner hole; one end of the second inner hole, which is far away from the first inner hole, is communicated with the external environment. And the arrangement mode of the second oil holes is the same as that of the first oil holes, and is not described again here. Specifically, when the first planetary gear row 111 and the second planetary gear row 112 rotate, the first oil holes will suck the lubricating oil from the housing 24 of the multi-function differential and throw it to the first planetary gear 1112 under the centrifugal force of the first planetary gear row 111; meanwhile, under the action of the centrifugal force of the second planetary gear row 112, the second oil holes will suck lubricating oil from the housing 24 of the multi-function differential and throw the lubricating oil onto the second planetary gears 1122; therefore, the design of the first oil hole and the second oil hole improves the lubricating effect and the cooling effect of the multifunctional differential, and the service life of the multifunctional transmission is prolonged.
In one embodiment, as shown in fig. 6 to 8 and 10, the switching device 231 is a coupling ring; an inner tooth 231 is arranged at one end of the input shaft 22 close to the planetary gear row 11, and the switching assembly 2 further comprises a connecting gear 25 coaxially connected with the planetary gear row 11 and matched with the inner tooth 231 (i.e. the connecting gear 25 is coaxially arranged with the first sun gear 1111); the coupling ring engages the input shaft 22 through the engagement of the internal teeth 231 with the coupling teeth 221, and the coupling ring engages the planetary gear row 11 through the engagement of the internal teeth 231 with the connecting gear 25 (i.e., the coupling ring engages the first sun gear 1111 through the engagement of the internal teeth 231 with the connecting gear 25). It is to be understood that the connecting gear 25 is fixedly connected to an end face of the first sun gear 1111 remote from the second sun gear 1121; further, the coupling teeth 221 may be engaged with the inner teeth 231 of the coupling ring as the coupling gear 25 has the same tooth shape.
Preferably, the first length of the internal teeth 231 is greater than a sum of a second length, which is a tooth length of the connecting gear 25, and a third length, which is a tooth length of the coupling teeth 221. So that the simultaneous engagement of the internal teeth 231 with the connecting gear 25 and the coupling gear 221 can be achieved. In the invention, the multifunctional differential can realize the functions of the same speed and idle running of the wheels of the automobile through the combination ring, thereby reducing the manufacturing cost of the multifunctional differential.
In one embodiment, as shown in fig. 4 and 5, the switch assembly 2 further comprises a housing 24 and a preload member 26; the housing 24 is provided with a mounting hole 241 for accommodating the engaging tooth 221, the connecting gear 25, the engaging ring and the preload member 26; a convex ring 243 is arranged on the inner wall of the mounting hole 241, the preload piece 26 is sleeved on the combination tooth 221, one end of the preload piece 26 is abutted against the convex ring 243, and the other end of the preload piece 26 is abutted against the combination ring. It is to be understood that the preload member 26 includes, but is not limited to, a coil spring; the pre-tightening design can ensure that the combination ring is separated from the planetary gear row and the input shaft 22 when returning, and the return function of the multifunctional differential is ensured.
In an embodiment, the switching assembly 2 further includes an input gear 21 mounted on the input shaft 22, and a bearing 27 sleeved on the input shaft 22, the input shaft 22 is provided with a shoulder (the shoulder is located on a side of the coupling teeth 221 away from the planetary gear row 11), one end of the bearing 27 abuts against the input gear 21, and the other end of the bearing 27 abuts against the shoulder; the input shaft 22 is rotatably mounted in the mounting hole 241 by the bearing 27. Preferably, a gear mounting portion in interference fit with the input gear 21 and a bearing 27 mounting portion for mounting the bearing 27 are arranged on the input shaft 22, and an outer diameter of the bearing 27 mounting portion is larger than an outer diameter of the gear mounting portion, so that the input gear 21 is ensured to be fixedly mounted on the input shaft 22, and the input shaft 22 passes through the mounting hole 241 of the housing 24, so that the input gear 21 can drive the input shaft 22 to rotate, while the housing 24 is kept stationary; in addition, when the input shaft 22 is mounted in the mounting hole 241 through the bearing 27, an end of the bearing 27 remote from the input gear 21 abuts against the shoulder, thereby simplifying the mounting of the multifunction transmission.
In an embodiment, as shown in fig. 5, 7 and 8, the outer wall of the coupling ring is provided with external teeth 232, the inner wall of the mounting hole 241 is provided with a sliding groove 242 adapted to the external teeth 232, and the coupling ring slides along the sliding groove 242 in the mounting hole 241 to control the internal teeth 231 to be coupled with or separated from the coupling teeth 221 and/or the connecting gear 25. It will be appreciated that the external teeth 232 are in clearance fit with the sliding slots 242, thereby ensuring that the coupling ring slides axially along the sliding slots 242. In the present invention, the stability of the coupling ring sliding in the mounting hole 241 is ensured by the design of the sliding groove 242 and the external teeth 232.
In one embodiment, as shown in fig. 1, 13 and 14, the multi-function differential further includes an actuator assembly 3; the actuating assembly 3 comprises a release bearing 32 and at least two ejector pins 31; it can be understood that the number of the thimbles 31 can be set according to actual requirements, and preferably, the number of the thimbles 31 is 3; the rotation of the input shaft 22 can drive the first planet carrier 12 and the second planet carrier 13 to rotate through 3 ejector pins 31.
At least two first pin holes 124 equal in number to the ejector pins 31 are formed in the first planet carrier 12, and a sliding shaft 136 and at least two second pin holes 135 equal in number to the ejector pins 31 are formed in the second planet carrier 13; the release bearing 32 is connected to the slide shaft 136; one end of the thimble 31 is connected to the release bearing 32, and the other end of the thimble 31 sequentially passes through the second needle hole 135 and the first needle hole 124 and abuts against the switching device 23. It is understood that the number of the first needle holes 124, the second needle holes 135 and the ejector pins 31 are equal. Further, the fixed end of the release bearing 32 is fixedly connected to the sliding shaft 136, and the movable end of the release bearing 32 can slide along the sliding shaft 136, so as to push the thimble 31 to move.
As shown in fig. 15, when receiving an idle rotation command, the release bearing 32 is controlled not to push the ejector pin 31, and the switching device 23 is released from both the planetary gear train 11 and the input shaft 22 by the elastic force of the preload member 26, thereby implementing an idle rotation function of the input gear 21. When receiving an idle rotation command, controlling the release bearing 32 not to push the ejector pin 31, and under the action of the elastic force of the preload member 26, the switching device 23 is separated from both the planetary gear train 11 and the input shaft 22; so that the input gear 21 is in an idle state (i.e. the rotation of the input gear 21 does not drive the first planetary gear row 111 and the second planetary gear row 112 to rotate), i.e. the power of the transmission or the reduction gearbox of the automobile is disconnected from the wheel end of the automobile; therefore, the multifunctional differential can reduce the resistance and the drag torque of the automobile and improve the fuel economy of the automobile.
As shown in fig. 16, when the same speed command is received, the release bearing 32 is controlled to push the switching device 23 along the slide groove 242 through the ejector pin 31, so that the switching device 23 is controlled to be simultaneously coupled with the planetary gear train 11 and the input shaft 22, and the rotational speeds of the input gear 21, the switching device 23, the first sun gear 1111 and the second sun gear 1121 are equal. As can be understood, when the vehicle is over a pothole or is trapped, the release bearing 32 is controlled to push the thimble 31 to slide along the slide slot 242, and the switching device 23 is simultaneously coupled with the planetary gear train 11 and the input shaft 22; at this time, the input gear 21, the first planetary gear row 111 and the second planetary gear row 112 are tightly connected together, and the first half shaft 4 connected with the first sun gear 1111, and/or the half shaft connected with the second sun gear 1121 are in a trapped state due to the automobile being trapped, and an external driving force needs to output a large torque to rotate the input gear 21; at the moment, the rotation of the automobile wheels needs external driving force to output larger torque, so that when the multifunctional transmission is in the same speed state, the difficulty removing capability of the automobile can be improved.
As shown in fig. 17, when a differential command is received, the release bearing 32 is controlled to push the thimble 31 to slide along the slide slot 242, so as to control the switching device 23 to be coupled with the input shaft 22, and simultaneously control the switching device 23 to be separated from the planetary gear train 11, and the input gear 21 drives the planetary gear train 11 to rotate through the switching device 23 under the action of an external driving force. It can be understood that when the vehicle is in a normal driving state, the differential command is automatically triggered, the release bearing 32 is controlled to continuously push the thimble 31 to slide along the slide slot 242, and the switching device 23 is simultaneously connected with the planetary gear set 11 and not connected with the input shaft 22; at this time, the rotation of the input gear 21 drives the first planetary gear row 111 and the second planetary gear row 112 to rotate sequentially through the input shaft 22 and the switching device 23, and the rotation of the first planetary gear row 111 and the second planetary gear row 112 can drive the first half shaft 4 and the second half shaft 5 to realize differential rotation, so that the normal differential running of the automobile is realized.
In the invention, the design of the executing component 3 can realize the selective combination of the switching device 23 and the first sun gear 1111 and the input shaft 22, so that the multifunctional transmission does not need to be provided with an electric push rod, the weight of the multifunctional transmission is reduced, and the lightweight design of an automobile is facilitated.
In one embodiment, as shown in fig. 13 and 14, the release bearing 32 includes a pressure plate 321 and a piston 322 mounted on the pressure plate 321; the end surface of the pressure plate 321 far away from the piston 322 is provided with a needle groove 3211 for mounting the thimble 31. It can be understood that the pressure plate 321 is sleeved on the outer wall of the first planet carrier 12, and the second half shaft 5 sequentially passes through the pressure plate 321 and the second planet carrier 13 to connect with the second sun gear 1121. Specifically, when high-pressure hydraulic oil is injected into the piston 322, the pressure plate 321 is pushed by the high-pressure hydraulic oil to drive the thimble 31 to move forward; when the hydraulic oil is pumped out from the piston 322, the pressure plate 321 drives the thimble 31 to retreat. Due to the design of the piston 322 and the pressure plate 321, the impact force between the pressure plate 321 and the ejector pin 31 is reduced, and the NVH performance of the automobile is improved.
The invention further provides an automobile comprising the multifunctional differential.
The present invention is not limited to the above preferred embodiments, and any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. A multi-function differential is characterized by comprising a differential component and a switching component; the differential assembly comprises a planetary gear row connecting a first half shaft and a second half shaft of the automobile; the switching assembly comprises an input shaft and a switching device; the switching device selectively couples the planetary gear row and the input shaft;
when the switching device is separated from both the planetary gear row and the input shaft, the multi-function differential is in an idle state; when the switching device is combined with the planetary gear row and the input shaft at the same time, the multifunctional differential is in the same speed state; the switching device is coupled to the input shaft, and the multi-function differential is in a differential state when the switching device is separated from the planetary gear row.
2. The multi-function differential of claim 1, wherein the planetary gear rows include a first planetary gear row and a second planetary gear row meshed with the first planetary gear row; the first planetary gear row includes a first sun gear and a plurality of first planet gears; the second planetary gear row includes a second sun gear and a plurality of second planet gears; the first sun gear is meshed with all the first planet gears; the second sun gear is meshed with all the second planet gears; the input shaft, the first sun gear and the second sun gear are coaxially arranged; the first planet gears and the second planet gears are equal in number and are arranged in a staggered mode; each first planet wheel is meshed with one second planet wheel adjacent to the first planet wheel; each second planet wheel is meshed with one adjacent first planet wheel;
the differential assembly further comprises a first planet carrier and a second planet carrier connected with the first planet carrier; the second planet carrier is also provided with a groove for accommodating the second planet gear row, and a mounting space for mounting the first planet gear row and the second planet gear row is formed between the first planet carrier and the second planet carrier.
3. The multi-function differential of claim 2, wherein the differential assembly further comprises a first axle pin and a second axle pin disposed parallel to a central axis of the first sun gear, the first carrier having a first axle hole, a first pin hole, and a second pin hole, the second carrier having a second axle hole, a third pin hole, and a fourth pin hole; the two opposite ends of the first shaft pin are respectively arranged in the first pin hole and the third pin hole, and the first planet wheel is arranged on the first shaft pin; two opposite ends of the second shaft pin are respectively installed in the second pin hole and the fourth pin hole, and the second planet wheel is installed on the second shaft pin; and a first half shaft of the automobile penetrates through the first shaft hole to be connected with the first sun gear, and a second half shaft of the automobile penetrates through the second shaft hole to be connected with the second sun gear.
4. The multi-function differential according to claim 3, wherein a first oil hole is provided in the first shaft pin, and a second oil hole is provided in the second shaft pin.
5. The multi-function differential of claim 2, wherein the switching means is a coupling ring; the inner wall of the combination ring is provided with inner teeth, one end of the input shaft, which is close to the planetary gear row, is provided with combination teeth matched with the inner teeth, and the switching assembly further comprises a connecting gear which is coaxially connected with the planetary gear row and is matched with the inner teeth; the coupling ring is coupled to the input shaft through engagement of the internal teeth with the coupling teeth, and the coupling ring is coupled to the planetary gear row through engagement of the internal teeth with the connecting gear.
6. The multi-function differential of claim 5, wherein the switching assembly further comprises a housing and a preload member; the shell is provided with a mounting hole for accommodating the combination teeth, the connecting gear, the combination ring and the preload piece; a convex ring is arranged on the inner wall of the mounting hole; one end of the preload piece is abutted to the convex ring, and the other end of the preload piece is abutted to the combination ring.
7. The multi-function differential according to claim 6, wherein the outer wall of the coupling ring is provided with external teeth, the inner wall of the mounting hole is provided with a sliding groove adapted to the external teeth, and the coupling ring slides along the sliding groove in the mounting hole to control the internal teeth to be coupled with or separated from the coupling teeth and/or the connecting gear.
8. The multi-function differential of claim 2, further comprising an actuator assembly; the executing assembly comprises a separating bearing and at least two ejector pins;
the first planet carrier is provided with at least two first needle holes with the number equal to that of the thimbles, and the second planet carrier is provided with a sliding shaft and at least two second needle holes with the number equal to that of the thimbles; the release bearing is connected to the sliding shaft; one end of the ejector pin is connected to the release bearing, and the other end of the ejector pin sequentially penetrates through the second needle hole and the first needle hole and abuts against the switching device.
9. The multi-function differential of claim 8, wherein the release bearing includes a pressure plate and a piston mounted on the pressure plate; and a needle groove for mounting the thimble is formed in the end face, far away from the piston, of the pressure plate.
10. An automobile, characterized by comprising the multi-function differential according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011058344.XA CN114321318B (en) | 2020-09-30 | 2020-09-30 | Multifunctional differential mechanism and automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011058344.XA CN114321318B (en) | 2020-09-30 | 2020-09-30 | Multifunctional differential mechanism and automobile |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114321318A true CN114321318A (en) | 2022-04-12 |
| CN114321318B CN114321318B (en) | 2024-03-19 |
Family
ID=81011022
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011058344.XA Active CN114321318B (en) | 2020-09-30 | 2020-09-30 | Multifunctional differential mechanism and automobile |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114321318B (en) |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4215593A (en) * | 1976-10-25 | 1980-08-05 | Nissan Motor Company, Limited | Transfer case for automotive vehicles |
| JPH0558181A (en) * | 1991-09-02 | 1993-03-09 | Toyota Motor Corp | Planetary gear type differential gear |
| US5690575A (en) * | 1995-07-06 | 1997-11-25 | Steyr-Daimler-Puch Ag | Differential transmission with integrated range gear |
| US6258002B1 (en) * | 1997-07-01 | 2001-07-10 | Steyr-Daimler-Puch Fahrzeugtechnik Ag & Co Kg | Two-stage transfer gear-box |
| US20030171184A1 (en) * | 2002-03-11 | 2003-09-11 | Russell Wige | Dual-input differential planetary gear transmission |
| DE102009013293A1 (en) * | 2009-03-14 | 2010-09-16 | Schaeffler Technologies Gmbh & Co. Kg | Differential gear for e.g. vehicle, to distribute drive moment in transverse direction between wheels of vehicle transverse axle, has brakes contacting with gear elements, where reduction of speed is transmitted to planetary gear |
| US20110217887A1 (en) * | 2009-08-10 | 2011-09-08 | Ontario Drive & Gear Limited | Vehicle drive transmission and steering system |
| CN106555845A (en) * | 2015-09-25 | 2017-04-05 | 比亚迪股份有限公司 | Differential mechanism, power drive system and vehicle |
| CN206845829U (en) * | 2017-04-21 | 2018-01-05 | 杭州前进齿轮箱集团股份有限公司 | A kind of automotive transfer case planetary structure differential mechanism |
| US20190376582A1 (en) * | 2018-06-06 | 2019-12-12 | John Siwko | Automatic Torque Transmission |
| CN111051106A (en) * | 2017-08-25 | 2020-04-21 | 奥迪股份公司 | Transmission device for a motor vehicle |
-
2020
- 2020-09-30 CN CN202011058344.XA patent/CN114321318B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4215593A (en) * | 1976-10-25 | 1980-08-05 | Nissan Motor Company, Limited | Transfer case for automotive vehicles |
| JPH0558181A (en) * | 1991-09-02 | 1993-03-09 | Toyota Motor Corp | Planetary gear type differential gear |
| US5690575A (en) * | 1995-07-06 | 1997-11-25 | Steyr-Daimler-Puch Ag | Differential transmission with integrated range gear |
| US6258002B1 (en) * | 1997-07-01 | 2001-07-10 | Steyr-Daimler-Puch Fahrzeugtechnik Ag & Co Kg | Two-stage transfer gear-box |
| US20030171184A1 (en) * | 2002-03-11 | 2003-09-11 | Russell Wige | Dual-input differential planetary gear transmission |
| DE102009013293A1 (en) * | 2009-03-14 | 2010-09-16 | Schaeffler Technologies Gmbh & Co. Kg | Differential gear for e.g. vehicle, to distribute drive moment in transverse direction between wheels of vehicle transverse axle, has brakes contacting with gear elements, where reduction of speed is transmitted to planetary gear |
| US20110217887A1 (en) * | 2009-08-10 | 2011-09-08 | Ontario Drive & Gear Limited | Vehicle drive transmission and steering system |
| CN106555845A (en) * | 2015-09-25 | 2017-04-05 | 比亚迪股份有限公司 | Differential mechanism, power drive system and vehicle |
| CN206845829U (en) * | 2017-04-21 | 2018-01-05 | 杭州前进齿轮箱集团股份有限公司 | A kind of automotive transfer case planetary structure differential mechanism |
| CN111051106A (en) * | 2017-08-25 | 2020-04-21 | 奥迪股份公司 | Transmission device for a motor vehicle |
| US20190376582A1 (en) * | 2018-06-06 | 2019-12-12 | John Siwko | Automatic Torque Transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114321318B (en) | 2024-03-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP2855182B1 (en) | Two-speed transmission and electric vehicle | |
| US11738629B2 (en) | Vehicle two-power-source dual driving assembly | |
| CN100351552C (en) | Structure of lubricating differential apparatus | |
| US7798027B2 (en) | Power takeoff and gearbox | |
| EP4075005A1 (en) | Motive power transmission route switching device and two-speed transmission | |
| CN111677824A (en) | In-wheel two-gear automatic speed change mechanism of compound planetary gear train and gear shifting control method thereof | |
| CN111577854A (en) | Multi-speed motor gearbox with low gear ratio | |
| CN213235855U (en) | Automatic separating mechanism for new energy automobile reduction gearbox | |
| CN113474972B (en) | Electric axle with differential sun gear disconnect clutch | |
| CN114321318B (en) | Multifunctional differential mechanism and automobile | |
| CN212273022U (en) | Power output unit with power disconnection function and automobile | |
| CN210830342U (en) | Hybrid power gearbox | |
| CN117157477A (en) | Differential device | |
| CN111251871B (en) | Hybrid power driving system and vehicle | |
| CN111720537A (en) | Two-gear speed reducer for integrated electronic parking | |
| CN108612816B (en) | Two-speed gear assembly | |
| CN221033704U (en) | Electromagnetic jaw clutch device of electric automobile, transmission connecting device and electric automobile | |
| CN109795307B (en) | Hybrid power coupling system and hybrid electric vehicle | |
| CN215673541U (en) | Intermediate support assembly of automobile transmission | |
| CN211259510U (en) | Planet row type three-gear gearbox | |
| WO2024100732A1 (en) | Drive power transmission device for vehicle | |
| CN218644735U (en) | Power output disconnecting device, electrically-driven speed reducer and speed changer | |
| US11982340B2 (en) | Two-speed transmission | |
| CN219911665U (en) | Locking differential for actuator motor | |
| CN215891020U (en) | Electric automobile speed reducer with intermediate shaft clutch mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |