CN114321318B - Multifunctional differential mechanism and automobile - Google Patents
Multifunctional differential mechanism and automobile Download PDFInfo
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- CN114321318B CN114321318B CN202011058344.XA CN202011058344A CN114321318B CN 114321318 B CN114321318 B CN 114321318B CN 202011058344 A CN202011058344 A CN 202011058344A CN 114321318 B CN114321318 B CN 114321318B
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- 239000000446 fuel Substances 0.000 abstract description 8
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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; an input shaft switching device selectively combining 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 mechanism 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 mechanism 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 normal differential running function of the automobile can be realized, and the idling and same-speed functions can be realized, so that the 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, the requirements of people on automobiles are not limited to vehicles, and people have higher pursuits on automobile comfort, 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, the differential mechanism in the prior art can only realize the differential function of an automobile, but cannot realize the locking function of wheels of the automobile, and cannot meet the requirement that the wheel end has stronger escaping capability under the working conditions of crossing pits or being trapped and the like of the automobile; 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 a transmission in the prior art cannot meet the conditions that an automobile is too pothole or trapped and the like, and the wheel end is not strong in escaping capability and the like, and provides a multifunctional differential and an electric automobile.
In view of the above problems, a multifunctional differential provided by embodiments of the present invention includes 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 an 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 the planetary gear row and the input shaft, the multifunctional differential mechanism 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 mechanism 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.
Optionally, the planetary gear row includes a first planetary gear row and a second planetary gear row meshed with the first planetary gear row; the first planetary gear row comprises a first sun gear and a plurality of first planetary gears; the second planetary gear row comprises 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 planetary gears and the second planetary gears are equal in number and are staggered; 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 an installation space for installing 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 comprises a first shaft pin and a second shaft pin which are 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; 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; opposite ends of the second pin are respectively arranged in the second pin hole and the fourth pin hole, and the second planet wheel is arranged on the second pin; the first half shaft of the automobile penetrates through the first shaft hole to be connected with the first sun gear, and the 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 device is a coupling ring; an inner tooth is arranged on the inner wall of the combining ring, one end, close to the planetary gear row, of the input shaft is provided with a combining tooth matched with the inner tooth, and the switching assembly further comprises a connecting gear which is coaxially connected with the planetary gear row and is matched with the inner tooth; the coupling ring couples the input shaft through engagement of the internal teeth with the coupling teeth, and the coupling ring couples the planetary gear row through engagement of the internal teeth with the connecting gear.
Optionally, the switching assembly further comprises a housing and a pretensioner; the shell is provided with a mounting hole for accommodating the combination teeth, the connecting gear, the combination ring and the pre-tightening piece; a convex ring is arranged on the inner wall of the mounting hole; one end of the pre-tightening piece is abutted against the convex ring, and the other end of the pre-tightening piece is abutted against the combining ring.
Optionally, external teeth are arranged on the outer wall of the combining ring, a sliding groove matched with the external teeth is arranged on the inner wall of the mounting hole, and the combining ring slides along the sliding groove in the mounting hole so as to control the internal teeth to be combined with or separated from the combining teeth and/or the connecting gear.
Optionally, the multi-function differential further comprises an actuation assembly; the execution assembly comprises a release bearing and at least two ejector pins;
the first planet carrier is provided with at least two first pinholes, the number of which is equal to that of the ejector pins, and the second planet carrier is provided with a sliding shaft and at least two second pinholes, the number of which is equal to that of the ejector pins; the release bearing is connected to the sliding shaft; one end of the thimble is connected to the release bearing, and the other end of the thimble sequentially passes through the second pinhole and the first pinhole and abuts against the switching device.
Optionally, the release bearing comprises a pressure plate and a piston mounted on the pressure plate; the end face of the pressure plate, which is far away from the piston, is provided with a needle groove for installing the thimble.
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 can only drive the input shaft to rotate, but can not drive the first half shaft and the second half shaft of the automobile through the planetary gear row, for example, when the multifunctional transmission is used for the front drive of a four-wheel drive automobile, and the automobile runs under a single front drive working condition, the connection between the front wheels and the front power assembly can be independently cut off; or the multifunctional transmission is used for rear drive of the four-wheel drive vehicle, and when the vehicle runs under a single rear drive working condition, the independent rear wheels can be connected with the rear driving force assembly; therefore, the resistance and the dragging torque of the automobile are reduced through the multifunctional differential mechanism, and the fuel economy of the automobile is improved. Secondly, when the switching device is combined with the planetary gear row and the input shaft at the same time, the multifunctional differential mechanism is in the same speed state, and at the moment, the rotating speeds of the input shaft, the switching device and the planetary gear row are the same; that is, when the wheels of the automobile are trapped, the multifunctional differential mechanism can be in the same-speed state, at the moment, the rotation 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 capacity of the automobile is improved. And when the switching device is combined with the input shaft and the switching device is separated from the planetary gear row, the input shaft drives the planetary gear row to rotate under the action of external driving force through the switching device, so that the normal differential running function of the automobile is realized. According to the multifunctional differential mechanism, the normal differential running function of the automobile can be realized, the idling and the same speed functions can be realized, and the escaping capability and the fuel economy of the automobile are improved.
The embodiment of the invention also provides an automobile comprising the multifunctional differential mechanism.
Drawings
The invention will be further described with reference to the drawings and examples.
FIG. 1 is a schematic diagram of an explosion structure of a multifunctional differential according to an embodiment of the present invention;
FIG. 2 is a schematic diagram illustrating an assembly structure of a multifunctional 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 one embodiment of the present invention;
FIG. 4 is a schematic diagram of a switching assembly and a first sun gear of a multi-functional differential according to an embodiment of the present invention;
FIG. 5 is a schematic view of a casing of a controller of a multifunctional differential according to an embodiment of the present invention;
FIG. 6 is a schematic structural diagram of an input shaft of a multifunctional differential according to an embodiment of the present invention;
FIG. 7 is a front view of a switching device of a multi-functional differential according to an embodiment of the present invention;
FIG. 8 is a schematic diagram of a switching device, a coupling tooth and a connecting gear of a multifunctional differential according to an embodiment of the present invention;
FIG. 9 is a schematic structural view of an actuator assembly of a multifunctional differential according to an embodiment of the present invention;
FIG. 10 is a schematic view of a first sun gear and a connecting gear of a multi-functional differential according to an embodiment of the present invention;
FIG. 11 is a schematic view illustrating a structure of a first planet carrier of a multi-purpose differential according to an embodiment of the present invention;
FIG. 12 is a schematic view of a second planet carrier of the multi-functional differential according to an embodiment of the present invention;
FIG. 13 is a schematic view of a platen of a multi-function differential according to an embodiment of the present invention;
FIG. 14 is a cross-sectional view of a release bearing of a multi-function differential provided in accordance with one embodiment of the present invention;
FIG. 15 is a schematic view of a switching device of a multi-functional differential according to an embodiment of the present invention, separated from a planetary gear row and an input shaft;
FIG. 16 is a schematic view of a switching device of a multi-function differential according to an embodiment of the present invention in combination with a planetary gear row and an input shaft;
fig. 17 is a schematic diagram of a switching device of a multifunctional differential according to an embodiment of the invention, which is combined with an input shaft and separated from a planetary gear row.
Reference numerals in the specification are as follows:
1. a differential assembly; 11. a planetary gear row 111, a first planetary gear row; 1111. a first sun gear; 1112. a first planet; 112. a second planetary gear row; 1121. a second sun gear; 1122. a second planet wheel; 12. a first planet carrier; 121. a first shaft hole; 122. a first pin hole; 123. a second pin hole; 124. a first pinhole; 13. a second 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 pin; 2. a switching assembly; 21. an input gear; 22. an input shaft; 221. a coupling tooth; 23. a switching device; 231. internal teeth; 232. external teeth; 24. a housing; 241. a mounting hole; 242. a chute; 243. a convex ring; 25. a connecting gear; 26. a pretension member; 27. a bearing; 3. an execution component; 31. a thimble; 32. separating the bearing; 321. a pressure plate; 3211. a needle groove; 322. a piston; 4. a first half shaft; 5. and a second half shaft.
Detailed Description
In order to make the technical problems, technical schemes and beneficial effects solved by the invention more clear, the 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 for purposes of illustration only and are not intended to limit the scope of the invention.
It is to be understood that the directions or positional relationships indicated by the terms "upper", "lower", "left", "right", "front", "rear", "middle", etc., are based on the directions or positional relationships shown in the drawings, are merely for convenience of description and simplification of the description, and do not indicate or imply that the components or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus are not to be construed as limitations of the present invention.
As shown in fig. 1 to 3, a multifunctional differential provided in an embodiment of the present invention 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 vehicle; 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; as can be appreciated, the planetary gear row 11 includes a first planetary gear row 111 and a second planetary gear row 112 that meshes with the first planetary gear row 111; while the first planetary gear row 111 includes a first sun gear 1111 and a plurality of first planetary gears 1112, the second planetary gear row 112 includes a second sun gear 1121 and a plurality of second planetary gears 1122; and be equipped with first internal spline on the first sun gear 1111, be equipped with on the first semi-axis 4 with first external spline of first internal spline meshing, first semi-axis 4 is through first internal spline and the first external spline of intermeshed first sun gear 1111, just first semi-axis 4 is kept away from first sun gear 1111 one end connects the first wheel of car.
The second sun gear 1121 is provided with a second internal spline, the second half shaft 5 is provided with a second external spline meshed 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 meshed 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 an 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 realize a differential running function 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 an automobile transmission, so that an external driving force (motor driving force, engine driving force, etc.) can drive the planetary gear set 11 to rotate through the input shaft 22.
When the switching device 23 is separated from the planetary gear row 11 and the input shaft 22, the multifunctional 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 multifunctional differential is in the same speed state; the switching device 23 is coupled to the input shaft 22, and the multi-function differential is in a differential state when the switching device 23 is separated from the planetary gear row 11. It will be appreciated that, when the multifunctional differential is in the same speed state, the rotational speeds of the input shaft 22, the switching device 23 and the planetary gear set 11 are the same, and at this time, the multifunctional differential cannot realize the differential function, and the rotational speeds of the front or rear wheels of the automobile are always equal.
Specifically, the specific working state of the multifunctional differential is as follows:
as shown in fig. 15, receiving an idle running command, controlling the switching device 23 to be separated from the planetary gear row 11 and the input shaft 22, wherein the input shaft 22 drives the input shaft 22 to idle running under the action of external driving force; it is to be appreciated that the idle command may be a driver manually triggered travel command during a coasting condition of the vehicle; further, when it is confirmed that the vehicle is running under the sliding condition according to the vehicle running information (including the vehicle running speed, direction, acceleration, etc.), the idle running command is automatically triggered, and at this time, the switching device 23 is controlled to be separated from both the planetary gear row 11 and the input shaft 22; so that the input shaft 22 is in an idle state (i.e., the rotation of the input shaft 22 does not rotate the first planetary gear set 111 and the second planetary gear set 112), i.e., the power of the transmission or reduction gearbox of the automobile is disconnected from the wheel end of the automobile. Understandably, when the multifunctional transmission is used for the front drive of a four-wheel drive vehicle and the vehicle runs under a single-front drive condition, the connection between the front wheels and the front power assembly can be cut off independently; or the multifunctional transmission is used for rear drive of the four-wheel drive vehicle, and when the vehicle runs under a single rear drive working condition, the independent rear wheels can be connected with the rear driving force assembly; therefore, the multifunctional differential mechanism can reduce the resistance and the dragging torque of the automobile and improve the fuel economy of the automobile.
As shown in fig. 16, receiving the same-speed command, the switching device 23 is controlled to be simultaneously combined with the planetary gear row 11 and the input shaft 22, so that the input shaft 22 and the planetary gear row 11 are in the same-speed state; it can be understood that the same-speed instruction can be a running instruction manually triggered by a driver when the automobile runs in a hollow or trapped working condition; further, when the automobile gets over a depression or gets trapped, the switching device 23 is controlled to be combined with the planetary gear row 11 and the input shaft 22 at the same time; at this time, the input shaft 22, the first planetary gear set 111 and the second planetary gear set 112 are tightly connected together, and the first half shaft 4 connected to the first sun gear 1111 and/or the half shaft connected to the second sun gear 1121 are/is in the same speed state due to the fact that the vehicles are trapped, the external driving force needs to output a large torque to drive the input shaft 22 to rotate, so that when the multifunctional transmission is in the locked state, the escaping capability of the vehicles can be improved.
As shown in fig. 17, the differential command is received, the switching device 23 is controlled to be combined with the input shaft 22, and meanwhile, the switching device 23 is controlled to be separated from the planetary gear row 11, and the input shaft 22 drives the planetary gear row 11 to rotate through the switching device 23 under the action of external driving force. It is understood that the differential command may be a command for automatically triggering when the vehicle is in a normal running state according to the running information of the vehicle (including the running speed, the running direction, the running acceleration, and the like). Further, when the automobile is in a normal running state, the differential speed command is automatically triggered, at this time, the rotation of the input shaft 22 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 speed rotation, so that normal differential speed running of the automobile is realized.
In the present 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 the 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 force assembly can be cut off independently, or the connection between the rear wheel and the rear driving force assembly can be cut off independently; therefore, the multifunctional differential mechanism can reduce the resistance and the dragging 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 set 11 and the input shaft 22, the multifunctional differential is in the same speed state, that is, the rotational speeds of the input shaft 22, the switching device 23 and the planetary gear set 11 are the same, and when the vehicle wheels are trapped, the external driving force needs to output a large torque to drive the input shaft 22 to rotate, so that the trapping capacity of the vehicle is improved. When the switching device 23 is combined with the input shaft 22, the switching device 23 is separated from the planetary gear row 11, and the input shaft 22 drives the planetary gear row to rotate under the action of external driving force through the switching device 23; thus, the normal differential running function of the automobile can be realized. According to the multifunctional differential mechanism, the normal differential running function of the automobile can be realized, the idling and the same speed functions can be realized, and the escaping 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 planetary 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 of the first planet 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 planetary gears 1112 and the second planetary gears 1122 are equal in number and are staggered; each first planet 1112 meshes with its adjacent one of the second planet 1122; each second planet 1122 is in mesh with its adjacent one of the first planet 1112; it can be appreciated that the number of the first planetary gears 1112 and the second planetary gears 1122 is the same, and the number of the first planetary gears 1112 and the second planetary gears 1122 can be set according to actual requirements; preferably, the number of the first planetary gears 1112 and the second planetary gears 1122 is 3.
As shown in fig. 12 and 13, the differential assembly 1 further includes a first carrier 12 and a second carrier 13 connected to 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. As can be appreciated, the second planet carrier is further provided with a groove 131 for accommodating the second planetary gear row 112, so that the multifunctional differential is simple in structure and convenient to install, and due to the design of the groove 131, the multifunctional differential is more compact in structure and strength; 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 one 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 parallel to the 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; opposite ends of the first shaft pin 14 are respectively installed in the first pin hole 122 and the third pin hole 133, and the first planet 1112 is installed on the first shaft pin 14; opposite ends of the second pin 15 are respectively installed in the second pin hole 123 and the fourth pin hole 134, and the second planetary gears 1122 are installed on the second pin 15; the first half shaft 4 of the automobile passes through the first shaft hole 121 to be connected with the first sun gear 1111, and the second half shaft 5 of the automobile passes through the second shaft hole 132 to be connected with the second sun gear 1121. It will be appreciated that the number of the first pin holes 14, the first pin holes 122, and the third pin holes 133 is equal to the number of the first planetary gears 1112, and the number of the second pin holes 15, the second pin holes 123, and the fourth pin holes 134 is equal to the number of the second planetary gears 1122. In the invention, the multifunctional differential mechanism has simple structure and convenient installation.
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 can be appreciated that the first oil hole and the second oil hole penetrate through the first shaft pin 14 and the second shaft pin 15, respectively, 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 disposed along the axis of the first shaft pin 14, and a second inner hole disposed radially along 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 far away from the first inner hole is communicated with the external environment. The arrangement mode of the second oil holes is the same as that of the first oil holes, and will not be described in detail here. Specifically, when the first planetary gear row 111 and the second planetary gear row 112 rotate, the first oil hole sucks the lubricating oil from the housing 24 of the multi-purpose differential and throws the lubricating oil onto the first planetary gear 1112 under the centrifugal force of the first planetary gear row 111; meanwhile, under the centrifugal force of the second planetary gear row 112, the second oil hole sucks the lubricating oil from the housing 24 of the multifunctional differential and throws the lubricating oil onto the second planetary gears 1122; therefore, the design of the first oil hole and the second oil hole improves the lubrication effect and the cooling effect of the multifunctional differential and prolongs the service life of the multifunctional transmission.
In an embodiment, as shown in fig. 6 to 8 and 10, the switching device 231 is a coupling ring, and inner teeth 231 are disposed on an inner wall of the coupling ring; the input shaft 22 is provided with a coupling gear 221 adjacent to one end of the planetary gear row 11 and adapted to the internal teeth 231, and the switching assembly 2 further includes a connecting gear 25 coaxially connected to the planetary gear row 11 and adapted to the internal teeth 231 (i.e. the connecting gear 25 is coaxially arranged with the first sun gear 1111); the coupling ring couples the input shaft 22 by the engagement of the internal teeth 231 with the coupling teeth 221, and the coupling ring couples the planetary gear row 11 by the engagement of the internal teeth 231 with the connecting gear 25 (i.e., the coupling ring couples the first sun gear 1111 by the engagement of the internal teeth 231 with the connecting gear 25). As can be appreciated, the connecting gear 25 is fixedly connected to the end face of the first sun gear 1111 remote from the second sun gear 1121; further, the coupling teeth 221, like the tooth form of the connecting gear 25, can be engaged with the inner teeth 231 of the coupling ring.
Preferably, the first length of the internal teeth 231 is greater than the sum of a second length, which is the tooth length of the connecting gear 25, and a third length, which is the tooth length of the coupling teeth 221. So that the internal teeth 231 simultaneously mesh with the connecting gear 25 and the coupling gear 221 simultaneously can be realized. According to the multifunctional differential mechanism, the functions of same speed and idle running of the wheels of the automobile can be realized through the combining ring, so that the manufacturing cost of the multifunctional differential mechanism is reduced.
In one embodiment, as shown in fig. 4 and 5, the switching assembly 2 further includes a housing 24 and a pretensioner 26; the housing 24 is provided with a mounting hole 241 for accommodating the coupling tooth 221, the connecting gear 25, the coupling ring and the pretensioner 26; the inner wall of the mounting hole 241 is provided with a convex ring 243, the pre-tightening piece 26 is sleeved on the combining teeth 221, one end of the pre-tightening piece 26 abuts against the convex ring 243, and the other end of the pre-tightening piece 26 abuts against the combining ring. It will be appreciated that the pretensioner 26 includes, but is not limited to, a coil spring; the pre-tightening design can ensure that the coupling ring is separated from the planetary gear row and the input shaft 22 when being returned, thereby ensuring the return function of the multifunctional differential mechanism.
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, where a shaft shoulder is disposed on the input shaft 22 (the shaft shoulder is located on a side of the coupling tooth 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 shaft shoulder; the input shaft 22 is rotatably mounted in the mounting hole 241 by the bearing 27. Preferably, the input shaft 22 is provided with a gear mounting portion in interference fit with the input gear 21, and a bearing 27 mounting portion for mounting the bearing 27, wherein the outer diameter of the bearing 27 mounting portion is larger than that of the gear mounting portion, so that the input gear 21 is fixedly mounted on the input shaft 22, the input shaft 22 passes through a mounting hole 241 of the housing 24, and the input gear 21 can drive the input shaft 22 to rotate, while the housing 24 is kept still; 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 multi-function 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 sliding grooves 242 matching with the external teeth 232, and the coupling ring slides along the sliding grooves 242 in the mounting hole 241 to control the coupling or decoupling of the internal teeth 221 with the coupling teeth 221 and/or the connecting gear 25. It will be appreciated that there is a clearance fit between the external teeth 232 and the runner 242, thereby ensuring that the coupling ring slides axially along the runner 242. In the present invention, the design of the sliding groove 242 and the external teeth 232 ensures the stability of the coupling ring when sliding in the mounting hole 241.
In an embodiment, as shown in fig. 1, 13 and 14, the multifunctional differential further comprises an actuating assembly 3; the execution assembly 3 comprises a release bearing 32 and at least two ejector pins 31; it can be appreciated that the number of the ejector pins 31 can be set according to actual requirements, and preferably, the number of the ejector pins 31 is 3; the rotation of the input shaft 22 may drive the first planet carrier 12 and the second planet carrier 13 to rotate through 3 ejector pins 31.
The first planet carrier 12 is provided with at least two first pinholes 124 equal to the number of the ejector pins 31, and the second planet carrier 13 is provided with a sliding shaft 136 and at least two second pinholes 135 equal to the number of the ejector pins 31; the release bearing 32 is connected to the sliding 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 pinhole 135 and the first pinhole 124 and abuts against the switching device 23. It will be appreciated that the number of the first pinholes 124, the second pinholes 135, and the 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, the idle running command is received, the release bearing 32 is controlled not to push the ejector pin 31, and the switching device 23 is separated from the planetary gear row 11 and the input shaft 22 under the elastic force of the pretensioner 26, so that the idle running function of the input gear 21 is realized. When receiving an idling command, the control release bearing 32 does not push the thimble 31, and the switching device 23 is separated from the planetary gear row 11 and the input shaft 22 under the elastic force of the pretensioner 26; so that the input gear 21 is in idle (i.e. the rotation of the input gear 21 does not drive the rotation of the first planetary gear row 111 and the second planetary gear row 112), 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 mechanism can reduce the resistance and the dragging torque of the automobile and improve the fuel economy of the automobile.
As shown in fig. 16, receiving the same-speed command, the release bearing 32 is controlled to push the switching device 23 along the chute 242 through the ejector pin 31, so as to control the switching device 23 to be simultaneously combined with the planetary gear row 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 appreciated, when the vehicle passes through the depression or gets trapped, the release bearing 32 is controlled to push the thimble 31 to slide along the chute 242, and the switching device 23 is combined with the planetary gear row 11 and the input shaft 22 at the same time; 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 axle shaft 4 connected to the first sun gear 1111 and/or the axle shaft connected to the second sun gear 1121 are in a trapped state due to the trapped automobile, and the external driving force needs to output a large torque to rotate the input gear 21; at the moment, the rotation of the wheels of the automobile requires the external driving force to output larger torque, so that when the multifunctional transmission is in the same speed state, the escaping capability of the automobile can be improved.
As shown in fig. 17, the differential speed command is received, the release bearing 32 is controlled to push the thimble 31 to slide along the chute 242, so as to control the switching device 23 to be combined with the input shaft 22, and simultaneously control the switching device 23 to be separated from the planetary gear row 11, and the input gear 21 drives the planetary gear row 11 to rotate under the action of external driving force through the switching device 23. It can be appreciated that, when the automobile is in a normal running state, the differential speed command is automatically triggered, the release bearing 32 is controlled to continuously push the thimble 31 to slide along the chute 242, and the switching device 23 is simultaneously combined with the planetary gear row 11 but not combined 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 normal differential running of the automobile is realized.
In the present invention, the design of the executing component 3 may realize the driving of the switching device 23 to selectively combine with 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, which reduces the weight of the multifunctional transmission and is beneficial to the lightweight design of the automobile.
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, which is far away from the piston 322, is provided with a needle groove 3211 for installing the thimble 31. It is to be appreciated 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 be connected with the second sun gear 1121. Specifically, when high-pressure hydraulic oil is injected into the piston 322, the pressure plate 321 drives the ejector pin 31 to move forward under the pushing of the high-pressure hydraulic oil; when hydraulic oil is drawn out from the piston 322, the pressure plate 321 drives the ejector pins 31 to retract. The design of the piston 322 and the pressure plate 321 reduces the impact force between the pressure plate 321 and the thimble 31, and improves the NVH performance of the automobile.
The invention further provides an automobile comprising the multifunctional differential.
The foregoing description of the preferred embodiment of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.
Claims (9)
1. The multifunctional differential mechanism 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 an 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;
the planetary gear row includes a first planetary gear row and a second planetary gear row meshed with the first planetary gear row; the first planetary gear row comprises a first sun gear and a plurality of first planetary gears; the second planetary gear row comprises 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 differential assembly further comprises a first planet carrier and a second planet carrier connected with the first planet carrier, and an installation space for installing the first planet gear row and the second planet gear row is formed between the first planet carrier and the second planet carrier;
the switching device is a combining ring; an inner tooth is arranged on the inner wall of the combining ring, one end, close to the planetary gear row, of the input shaft is provided with a combining tooth matched with the inner tooth, and the switching assembly further comprises a connecting gear which is coaxially connected with the planetary gear row and is matched with the inner tooth; the coupling ring couples the input shaft through engagement of the internal teeth with the coupling teeth, and the coupling ring couples the planetary gear row through engagement of the internal teeth with the connecting gear;
when the switching device is separated from the planetary gear row and the input shaft, the internal teeth are not meshed with the combining teeth and the connecting gear, and the multifunctional differential is in an idle state; when the switching device is combined with the first sun gear of the planetary gear row and the input shaft at the same time, the internal teeth are meshed with the combining teeth and the connecting gear, and the multifunctional differential is in the same speed state; when the switching device is combined with the input shaft and separated from the planetary gear row, the internal teeth are meshed with the combined teeth and are not meshed with the connecting gear, the input shaft is connected with the first planet carrier through the switching device, and the multifunctional differential is in a differential state.
2. The multi-function differential of claim 1, wherein the input shaft, the first sun gear, and the second sun gear are coaxially disposed; the first planetary gears and the second planetary gears are equal in number and are staggered; 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 second planet carrier is also provided with a groove for accommodating the second planet gear row.
3. The multifunctional differential according to claim 2, wherein the differential assembly further comprises 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; 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; opposite ends of the second pin are respectively arranged in the second pin hole and the fourth pin hole, and the second planet wheel is arranged on the second pin; the first half shaft of the automobile penetrates through the first shaft hole to be connected with the first sun gear, and the second half shaft of the automobile penetrates through the second shaft hole to be connected with the second sun gear.
4. A multi-function differential as defined in claim 3, wherein said first axle pin is provided with a first oil hole and said second axle pin is provided with a second oil hole.
5. The multi-function differential of claim 1, wherein the switching assembly further comprises a housing and a pretensioner; the shell is provided with a mounting hole for accommodating the combination teeth, the connecting gear, the combination ring and the pre-tightening piece; a convex ring is arranged on the inner wall of the mounting hole; one end of the pre-tightening piece is abutted against the convex ring, and the other end of the pre-tightening piece is abutted against the combining ring.
6. The multifunctional differential according to claim 5, wherein external teeth are arranged on the outer wall of the combining ring, sliding grooves matched with the external teeth are arranged on the inner wall of the mounting hole, and the combining ring slides along the sliding grooves in the mounting hole so as to control the internal teeth to be combined with or separated from the combining teeth and/or the connecting gear.
7. The multi-function differential of claim 1, further comprising an implement assembly; the execution assembly comprises a release bearing and at least two ejector pins;
the first planet carrier is provided with at least two first pinholes, the number of which is equal to that of the ejector pins, and the second planet carrier is provided with a sliding shaft and at least two second pinholes, the number of which is equal to that of the ejector pins; the release bearing is connected to the sliding shaft; one end of the thimble is connected to the release bearing, and the other end of the thimble sequentially passes through the second pinhole and the first pinhole and abuts against the switching device.
8. The multi-function differential of claim 7, wherein the release bearing comprises a pressure plate and a piston mounted on the pressure plate; the end face of the pressure plate, which is far away from the piston, is provided with a needle groove for installing the thimble.
9. An automobile comprising the multi-functional differential as defined in any one of claims 1 to 8.
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| CN202011058344.XA CN114321318B (en) | 2020-09-30 | 2020-09-30 | Multifunctional differential mechanism and automobile |
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| CN202011058344.XA CN114321318B (en) | 2020-09-30 | 2020-09-30 | Multifunctional differential mechanism and automobile |
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| CN114321318B true CN114321318B (en) | 2024-03-19 |
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| CN111051106A (en) * | 2017-08-25 | 2020-04-21 | 奥迪股份公司 | Transmission device for a motor vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030171184A1 (en) * | 2002-03-11 | 2003-09-11 | Russell Wige | Dual-input differential planetary gear transmission |
| GB0913929D0 (en) * | 2009-08-10 | 2009-09-16 | Ontario Drive & Gear Ltd | Vehicle drive transmission and steering system |
| US10584773B2 (en) * | 2018-06-06 | 2020-03-10 | John Siwko | Automatic torque transmission |
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| 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 |
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|---|---|
| CN114321318A (en) | 2022-04-12 |
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