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WO2018121291A1 - Différentiel, et véhicule - Google Patents

Différentiel, et véhicule Download PDF

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Publication number
WO2018121291A1
WO2018121291A1 PCT/CN2017/116565 CN2017116565W WO2018121291A1 WO 2018121291 A1 WO2018121291 A1 WO 2018121291A1 CN 2017116565 W CN2017116565 W CN 2017116565W WO 2018121291 A1 WO2018121291 A1 WO 2018121291A1
Authority
WO
WIPO (PCT)
Prior art keywords
differential
planet
gear
ring gear
driving
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.)
Ceased
Application number
PCT/CN2017/116565
Other languages
English (en)
Chinese (zh)
Inventor
凌和平
翟震
黄长安
罗永孟
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BYD Co Ltd
Original Assignee
BYD Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by BYD Co Ltd filed Critical BYD Co Ltd
Publication of WO2018121291A1 publication Critical patent/WO2018121291A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators

Definitions

  • the present invention relates to the field of vehicle technology, and in particular, to a differential and a vehicle having the same.
  • the new energy vehicle adopts a distributed driving mode, and the two motors respectively drive the wheels on both sides, and the rotational speed and torque of the left and right wheels can be independently adjusted by the controller, thus canceling the differential, but in a certain In some slippery road conditions, it is still necessary to lock the left and right axles to improve vehicle passing. If the conventional electric lock-type differential is applied to a distributed-powered new energy vehicle, the differential function of the differential is wasted, and the conventional electric lock-type differential has a complicated structure and many components. Take up more space.
  • the present invention aims to solve at least one of the technical problems in the related art to some extent. To this end, the present invention proposes a differential that can lock the two half shafts and improve the ability of the vehicle to escape.
  • the invention further proposes a vehicle.
  • a differential includes: a first planet carrier, a first planet gear, and a first ring gear, the first planet gear being disposed on the first planet carrier, the first planet gear and the first planet gear a first ring gear meshes; a second planet carrier, a second planet gear and a second ring gear, the second planet gear being disposed on the second planet carrier, the second planet gear and the second ring gear Engaging and engaging the second planet gear with the first planet gear; wherein the first ring gear and the second ring gear constitute two power output ends of the differential, the first planet carrier And the second planet carrier constitutes a power input end of the differential; the power engagement device includes a first engagement portion and a second engagement portion, the first engagement portion and the first ring gear One of the second ring gears is connected, the second engaging portion rotates in synchronization with the first planet carrier and the second planet carrier; the joint driving device includes: a driving pin and a driving portion The driving pin is disposed to be wrapable with the first planet carrier and the second planet carrier And the
  • the engaging portion driving device drives the second engaging portion to engage with the first engaging portion
  • the output rotational speeds of the first ring gear and the second ring gear are the same, so that the two half shafts can be synchronized. This can help improve the vehicle's ability to get out of trouble.
  • a vehicle according to the present invention includes the above differential.
  • FIG. 1 is an exploded view of a differential according to an embodiment of the present invention.
  • FIG. 2 is a front elevational view of a differential in accordance with an embodiment of the present invention.
  • FIG. 3 is a schematic diagram of a planar principle of a differential according to an embodiment of the present invention.
  • FIG. 4 is a partial perspective view of a differential according to an embodiment of the present invention, in which the first ring gear and the first planet carrier are removed;
  • Figure 5 is a partial front elevational view of the differential, mainly showing the first planet carrier, the first planet gears, and the second planet carrier and the second planet gear, etc., in accordance with an embodiment of the present invention
  • Figure 6 is a schematic view showing the meshing of the first planetary gear and the second planetary gear
  • Figure 7 is a schematic diagram of the engagement of the first planetary gear and the second planetary gear
  • Figure 8 is a perspective view of a first ring gear or a second ring gear according to still another embodiment of the present invention.
  • Figure 9 is a perspective view of a first ring gear or a second ring gear according to still another embodiment of the present invention.
  • Figure 10 is a schematic illustration of a power drive system in accordance with an embodiment of the present invention.
  • FIG. 11 is a schematic illustration of a vehicle in accordance with an embodiment of the present invention.
  • Figure 12 is a schematic illustration of a power drive system in accordance with the present invention.
  • Figure 13 is a schematic view of a differential, a power engaging device, and a joint driving device
  • Figure 14 is a schematic view showing the structure of the follower portion.
  • a differential 100 according to an embodiment of the present invention will be described in detail below with reference to FIGS. 1-11.
  • the differential 100 can be used for inter-wheel differential or inter-axle differential for the example of inter-wheel differential.
  • the differential 100 enables the left and right drive wheels to roll at different angular velocities when the vehicle is turning or traveling on uneven roads to ensure a pure rolling motion between the drive wheels on both sides and the ground.
  • a differential 100 may include a first planet carrier 11, a first planet gear 12 and a first ring gear 13, and a second planet carrier 21, a second planet gear 22, and a Two ring gears 23.
  • both the first planet carrier 11 and the second planet carrier 21 can be configured as a circular plate-like structure, which can reduce the axial dimension of the differential 100 to some extent.
  • the first planet carrier 11 and the second planet carrier 21 may be of a split structure, and since the separate widgets are relatively easy to shape, separately machining the first planet carrier 11 and the second planet carrier 21 separately may simplify manufacturing. Process, improve processing accuracy.
  • the first planet gears 12 are disposed on the first planet carrier 11, for example, each of the first planet gears 12 is provided with a first planet gear axle 14
  • the two ends of the first planetary axle 14 are rotatably supported on the first planet carrier 11 and the second planet carrier 21, respectively, such that both ends of the first planetary axle 14 are rotatably supported by bearings
  • the first planet gear 12 can be fixed to the corresponding first planet gear shaft 14 at this time.
  • the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved by the first planetary axle 14 such that the first planet carrier 11 and the second planet carrier 21 maintain the same speed and the same direction (ie, the first The carrier 11 and the second carrier 21 are interlocked). Moreover, with this connection, the first planet carrier 11 and the second planet carrier 21 can support the first planetary axle 14 well, preventing the first planetary axle 14 from being disconnected from the single planet carrier, thereby causing the differential 100 to fail. .
  • the first planet gear 12 meshes with the first ring gear 13, specifically in the form of internal engagement, that is, the first planet gear 12 is located inside the first ring gear 13 and with the teeth on the first ring gear 13.
  • the first planetary gears 12 are preferably plural and are distributed equidistantly inside the first ring gear 13 in the circumferential direction.
  • the first planetary gears 12 may be three and any adjacent ones.
  • the angle between the two first planet wheels 12 is 120°.
  • the second planet gears 22 are disposed on the second planet carrier 21, for example, each of the second planet gears 22 is configured with a second.
  • the planetary axles 24, such as the two ends of the second planetary axle 24, are rotatably supported by bearings in respective axial bores of the first planet carrier 11 and the second planet carrier 21, at which time the second planet gear 22 can be fixed to the corresponding second planetary axle 24.
  • the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved by the second planetary gear shaft 24, so that the first planet carrier 11 and the second planet carrier 21 maintain the same speed and the same direction.
  • the first planet carrier 11 and the second planet carrier 21 can support the second planetary axle 24 well, preventing the second planetary axle 24 from being disconnected from the single planet carrier, thereby causing the differential 100 to fail. .
  • the first planet carrier 11 and the second planet carrier 21 may also be passed through the intermediate member.
  • Directly fixed connection that is, the same speed and co-directional movement of the first planet carrier 11 and the second planet carrier 21 in the above embodiment may be achieved by the first planetary axle 14 and the second planetary axle 24, and
  • the embodiment can realize the same speed and the same direction movement of the first planet carrier 11 and the second planet carrier 21 directly by providing the intermediate component, for example, the intermediate component can be located on the first planet carrier 11 and the second planet carrier. Between 21 and respectively welded and fixed to the first planet carrier 11 and the second planet carrier 21.
  • the second planetary gear 22 meshes with the second ring gear 23, specifically in the form of internal engagement, that is, the second planetary gear 22 is located inside the second ring gear 23 and with the teeth on the second ring gear 23.
  • the second planetary gears 22 are preferably plural and are distributed equidistantly inside the second ring gear 23 in the circumferential direction.
  • the second planetary gears 22 may be three and any adjacent ones.
  • the angle between the two second planet gears 22 is 120°.
  • FIG. 3 is a schematic diagram of the plane principle of the differential 100 according to an embodiment of the present invention, wherein the meshing relationship between the first planet gear 12 and the second planet gear 22 is schematically illustrated and The meshing relationship between the first planetary gear 12 and the first ring gear 13, the second planetary gear 22 and the second ring gear 23, as shown in Fig. 3, and at the same time shows the above three meshing relationships, the relative positions of the components The relationship is merely illustrative and does not represent or imply the actual spatial arrangement of the components.
  • both the first planet gear 12 and the second planet gear 22 are multiple, preferably, the plurality of first planet gears 12 and the plurality of second planet gears 22 are respectively engaged.
  • the first planetary gear 12 and the second planetary gear 22 are three, and the first first planetary gear 12 can be meshed with the corresponding first second planetary gear 22,
  • the second first planet gear 12 is engageable with the corresponding second second planet gear 22,
  • the third first planet gear 12 is engageable with the corresponding third second planet gear 22 such that there are multiple sets of meshing with each other
  • the plurality of first planetary gears 12 and the plurality of second planetary gears 22 are alternately arranged in the circumferential direction, and are arbitrarily adjacent The first planet gear 12 and the second planet gear 22 mesh. That is, in this embodiment, the plurality of first planetary gears 12 and the plurality of second planetary gears 22 are alternately arranged in the circumferential direction and form an annular shape, and each of the first planetary gears 12 has two adjacent ones thereof. The two planet gears 22 mesh, and similarly, each of the second planet gears 22 meshes with its two adjacent first planet gears 12.
  • the revolution axis O of the first planet gear 12 coincides with the revolution axis O of the second planet gear 22, and the revolution radius of the first planet gear 12 and the second planet gear 22 (ie, the planetary gear The distance of the central axis from the revolution axis O is the same.
  • the first planet gear 12 is in meshing engagement with the second planet gear 22.
  • the first planetary gear 12 it not only meshes with the first ring gear 13, but also meshes with the second planetary gear 22, and for the second planetary gear 22, it not only meshes with the second ring gear 23, At the same time, it also meshes with the first planet gear 12.
  • the first ring gear 13 and the second ring gear 23 may constitute two power output ends of the differential 100, and the first carrier 11 and the second carrier 21 correspond to the power of the differential 100.
  • the input end (for example, the first carrier 11 and the second carrier 21 can be rigidly connected together), so that the power output from the external power source can be input from the first carrier 11 and the second carrier 21, and the differential is passed.
  • the differential action of the device 100 can be respectively from the first ring gear 13 and the second ring gear 23 Output.
  • first planet carrier 11 and the second planet carrier 21 may be connected to a power source such as an engine, a motor, etc., and the first ring gear 13 and the second ring gear 23 may pass through a gear transmission structure and corresponding The half shafts are connected, and the half shafts are connected to the corresponding wheels, but are not limited thereto.
  • the differential 100 is applied to the inter-wheel differential, and the first ring gear 13 and the second ring gear 23 constitute a power output end of the differential 100, and the first carrier 11 and the second carrier 21 constitute a differential.
  • the power input end of 100 exemplifies the working principle of the differential 100, wherein the first ring gear 13 can be connected to the left half shaft through a gear transmission structure, and the left half shaft can be connected to the left side wheel, the second tooth.
  • the ring 23 can be connected to the right half shaft by a gear transmission structure, and the right half shaft can be connected to the right side wheel, and the power output of the power source such as the engine and/or the motor can be output to the first carrier through the deceleration of the final drive. 11 and the second planet carrier 21.
  • the differential 100 does not function as a differential, and the first carrier 11 and the second carrier 21 are at the same speed.
  • the first ring gear 13 and the second ring gear 23 rotate at the same speed and in the same direction, and the first planetary gear 12 and the second planetary gear 22 only revolve and do not rotate.
  • the left and right wheels are theoretically different in rotational speed, and the rotational speeds of the first ring gear 13 and the second ring gear 23 are also different, that is, there is a difference in rotational speed.
  • the first planetary gear 12 and the second planetary gear 22 also rotate while revolving, and the rotation of the first planetary gear 12 and the second planetary gear 22 causes one of the first ring gear 13 and the second ring gear 23 to increase speed, Another deceleration, the difference between the speed-increasing ring gear and the decelerating ring gear is the difference between the left and right wheels, thus achieving differential action.
  • the differential 100 utilizes the principle of planetary differential, has higher space utilization in structure and connection form, smaller axial dimension, and is more advantageous in production and assembly.
  • a structural form can not only avoid the dimensional defects in the axial direction and the radial direction of the bevel gear, but also can better utilize the hollow space inside the main reduction driven gear, thereby achieving better space utilization and greatly facilitating the difference.
  • the overall arrangement of the speedometer 100 assembly and the limitation on the weight, as well as higher reliability and better transmission efficiency, are beneficial to improve the reliability of the power transmission chain and the power output fluency during cornering. This is more practical than a symmetrical bevel gear differential.
  • the first planetary gear 12 and the second planetary gear 22 partially overlap in the axial direction (the horizontal direction in FIG. 7), that is, the first planetary gear 12 and the second planetary gear.
  • the wheels 22 only partially overlap, the other portions are staggered, the overlapping portions of the first planet gear 12 and the second planet gear 22 can engage each other, and the staggered portions can engage the respective ring gears.
  • the first planetary gear 12 may include a first tooth portion 151 and a second tooth portion 152 (with a broken line of K2 in FIG. 7), and the second planetary gear 22 may include the first The third tooth portion 153 and the fourth tooth portion 154 (with a broken line of K1 in FIG. 7 as a boundary line), the second tooth portion 152 and the third tooth portion 153 constitute an overlapping portion, that is, the second tooth portion 152 and the third tooth portion 153 are
  • the first tooth portion 151 and the fourth tooth portion 154 are axially offset and mesh with the corresponding ring gears, that is, the first tooth portion 151 is meshed with the first ring gear 13 , and the fourth portion is overlapped and engaged. Tooth portion 154 and second ring gear 23 Engage.
  • the axial dimension of the differential 100 is made more compact, and the volume of the differential 100 is more compact, which facilitates the installation and arrangement of the differential 100.
  • the power input end and the power output end of the differential 100 will be described in detail below in conjunction with specific embodiments.
  • the differential 100 further includes input shafts 31, 32 and output shafts 41, 42 that are coupled to the first planet carrier 11 and the second planet carrier 21, respectively, as in the example of FIG.
  • An input shaft 31 is connected to the left side of the first carrier 11, and another input shaft 32 is connected to the right side of the second carrier 21.
  • the output shafts 41, 42 are respectively connected to the first ring gear 13 and the second ring gear 23, as in the example of Fig. 3, the left side of the first ring gear 13 is connected to an output shaft 41, and the second ring gear 23 is connected to the right.
  • Another output shaft 42 is connected to the side.
  • the input shafts 31, 32, the output shafts 41, 42, the first ring gear 13 and the second ring gear 23 can be arranged coaxially.
  • the input shaft includes a first input shaft 31 and a second input shaft 32.
  • the first input shaft 31 is connected to the first carrier 11, and the second input shaft 32 is connected to the second carrier 21.
  • the output shaft may include a first output shaft 41 and a second output shaft 42, the first output shaft 41 being coupled to the first ring gear 13, and the second output shaft 42 being coupled to the second ring gear 23, the first input shaft 31 and the
  • the two input shafts 32 and the first output shaft 41 and the second output shaft 42 may each be a hollow shaft structure.
  • the first output shaft 41 is coaxially sleeved on the first input shaft 31, and second.
  • the output shaft 42 is coaxially sleeved on the second input shaft 32, whereby the differential 100 is more compact and smaller in size.
  • the number of teeth of the first ring gear 13 is equal to the number of teeth of the second ring gear 23, and the number of teeth of the first planet gear 12 is equal to the number of teeth of the second planet gear 22.
  • the first planetary gear 12 and the second planetary gear 22 are both spur gears, and the differential 100 using the spur gear is more compact in structure than the conventional symmetrical bevel gear differential, in particular It has higher space utilization in structure and connection form, smaller axial dimension, and is more advantageous in production and assembly.
  • first ring gear 13 and the second ring gear 23 will be described in detail below in conjunction with specific embodiments.
  • the first ring gear 13 and the second ring gear 23 are symmetric structures, in other words, the first ring gear 13 and the second ring gear 23 are symmetrically arranged, which can increase the versatility of the ring gear and reduce cost.
  • each of the first ring gear 13 and the second ring gear 23 includes a main body flat plate portion 161 and an annular side wall portion provided at an outer peripheral edge of the main body flat plate portion 161.
  • the main body flat portion 161 and the annular side wall portion 162 may be integrally formed members.
  • a plurality of gear teeth are disposed on an inner wall surface of the annular side wall portion 162, and a cavity A1, A2 is defined between the main body flat plate portion 161 and the annular side wall portion 162 (see FIG.
  • the first ring gear 13 A cavity A1 is defined between the main body flat portion 161 and the annular side wall portion 162, and a cavity A2 is defined between the main body flat portion 161 of the second ring gear 23 and the annular side wall portion 162, and the inside of the first ring gear 13
  • the cavity A1 and the cavity A2 in the second ring gear 23 face each other to constitute an installation space A (see FIG. 3), wherein the first planet carrier 11 and the first planet gear 12 and the second planet carrier 21 and the second planet The wheel 22 is housed in the installation space A, so that the structure of the differential 100 is relatively more compact and occupied.
  • the volume is smaller and easier to arrange, while the first ring gear 13 and the second ring gear 23 function as an outer casing, which can protect the planet carrier and the planet gear housed therein, improving the life.
  • the installation space A defined by the first ring gear 13 and the second ring gear 23 is relatively closed, and the external debris is not easily entered into the installation space A to affect the moving parts, thereby ensuring stable operation of the differential 100.
  • the first ring gear 13 and the second ring gear 23 are provided with a gap D in the axial direction, that is, the first ring gear 13 and the second ring gear 23 are axially spaced apart from each other, not Closely fit.
  • the width of the meshing portion of the first planet gear 12 and the second planet gear 22 determines the size of the gap D, that is, the width of the meshing portion of the first planet gear 12 and the second planet gear 22. It is equal to the minimum value of the gap D, so by controlling the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22, the size of the gap D can be indirectly controlled, and the first one is guaranteed by those skilled in the art.
  • the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22 can be stabilized under the premise that the planetary gear 12 and the second planetary gear 22 can stably transmit power and the service life of the first planetary gear 12 and the second planetary gear 22
  • the arrangement is relatively narrow, so that the gap D can be effectively reduced, so that the axial dimension of the differential 100 is smaller, more compact, and easier to arrange.
  • the gap D of the above-mentioned FIG. 3 refers to the distance between the annular side wall portion 162 of the first ring gear 13 and the annular side wall portion 162 of the second ring gear 23.
  • the first ring gear 13 and the second ring gear 23 both include a body flat plate portion 161 and an annular side wall portion 162.
  • each of the first ring gear 13 and the second ring gear 23 further includes an annular flange portion 163, an annular flange The portion 163 extends from the end surface of the annular side wall portion 162 in a direction away from the main body flat portion 161.
  • the inner diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, such that the ring The flange portion 163 corresponds to the outwardly projecting annular side wall portion 162 (i.e., the outer peripheral surface of the first ring gear 13 or the second ring gear 23) in the radial direction.
  • the outer diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, and the inner diameter of the annular flange portion 163 may be larger than the inner diameter of the annular side wall portion 162, that is, The thickness of the annular flange portion 163 is thinner than the thickness of the annular side wall portion 162.
  • the gap D between the two ring gears refers to the gap between the annular side wall portions 162 of the two ring gears.
  • the gap D between the two ring gears refers to the gap between the annular flange portions 163 of the two ring gears.
  • the first ring gear 13 and/or the second ring gear 23 may further include an annular flange portion 163, when such a ring gear structure is employed, due to the presence of the annular flange portion 163,
  • the gap D can be at least partially reduced compared to the ring gear without the annular flange portion 163, and preferably, the gap D can be reduced to zero, for example, the first ring gear 13 and the second ring gear 23 can At the same time, the ring gear structure shown in FIG. 8 is adopted.
  • the annular flange portion 163 of the first ring gear 13 and the end surface of the annular flange portion 163 of the second ring gear 23 can be substantially fitted together, so that the gap D is Zero, so the installation space A is more closed, and the external debris is more difficult to enter into the installation space A and affect the moving parts, ensuring The stable operation of the differential 100 is achieved. It should be understood, of course, that the description herein is merely illustrative and is not to be construed as a limitation of the scope of the present invention.
  • the arrangement of the annular flange portion 163 can further After reducing the gap D and even reducing the gap D to zero, the type of the ring gear can be flexibly selected for combination, for example, ensuring that at least one of the ring gears has the annular flange portion 163, so that the gap D can be further reduced. Even the gap D is reduced to zero, so that the installation space A is more encrypted.
  • first ring gear 13 and the second ring gear 23 have the same radial dimension, and each of the first ring gear 13 and the second ring gear 23 may be an integrally formed component.
  • the combined technical solution may be a superposition of two or more technical solutions, a superposition of two or more technical features or a superposition of two or more technical solutions and technical features, thereby enabling The technical solutions and/or technical features interact and support each other functionally, and the combined solution has a superior technical effect.
  • a person skilled in the art can partially overlap the first planet gear 12 and the second planet gear 22 with a scheme in which the first planet carrier 11 and the second planet carrier 21 are plate-like structures, which can effectively reduce the differential speed.
  • the axial dimension of the device 100 is such that the volume of the differential 100 is smaller.
  • a person skilled in the art can combine the solution that the first planetary gear 12 and the second planetary gear 22 partially overlap with the solution that the planetary gear and the carrier are housed in the installation space, so that the differential 100 can be effectively reduced.
  • the axial size also allows the planet wheels and planet carrier to be hidden in the installation space to avoid damage to the outside, which increases the service life and reduces maintenance costs.
  • a person skilled in the art may adjust the revolving axis of the first planet gear 12 to the revolving axis of the second planet gear 22 and the revolving radius of the first planet gear 12 to be the same as the revolving radius of the second planet gear 22 .
  • the combination makes the structure of the differential 100 more compact, smaller in size, and easier to arrange.
  • the differential 100 can effectively save space and reduce weight.
  • the planetary gear differential 100 is compared to a conventional bevel gear differential.
  • the weight can be reduced by about 30%, and the axial dimension is reduced by about 70%, which not only reduces the friction of the bearing, but also realizes the torque distribution of the left and right wheels, makes the load distribution of the differential 100 more reasonable, and the differential 100 is more rigid.
  • the transmission efficiency is also improved.
  • the conventional bevel gear transmission efficiency of 6-level accuracy and 7-level accuracy is about 0.97 to 0.98
  • the efficiency of the spur gear transmission of 6-level precision and 7-level precision is about 0.98 to 0.99
  • the operating noise of the differential 100 is also reduced, while the heat generation is reduced, greatly increasing the life of the differential 100.
  • the differential 100 according to the embodiment of the present invention has many advantages such as light weight, small size, low cost, high transmission efficiency, low noise, low heat generation, and high life.
  • the differential 100 according to the embodiment of the present invention can omit the sun gear, the elimination of the sun gear can have the following advantages:
  • the sun gear is cancelled, but the ring gear is used to realize the differential speed, because the number of teeth of the ring gear can be set more than the sun wheel, and the pitch circle is larger (the pitch circle refers to the gear meshing transmission at the node) A pair of tangential circles), so that the load and the withstand torque can be distributed more evenly, which is advantageous for the improvement of the life of the differential 100.
  • the pitch circle refers to the gear meshing transmission at the node
  • a pair of tangential circles A pair of tangential circles
  • the sun gear and the planet gear are externally meshed
  • the gear ring can store lubricating oil, thereby greatly improving the cooling and lubrication effect.
  • the sun gear is eliminated, the components are reduced, the quality and cost of the differential 100 are reduced, and the differential 100 is further reduced in size and weight.
  • a power drive system 1000 which includes the differential 100 in the above embodiment, will be briefly described below.
  • the power drive system 1000 includes a differential 100, a transmission 200, and a power source 300.
  • the power outputted by the power source 300 is output to the differential 100 through the shifting action of the transmission 200, and then distributed by the differential 100.
  • the power drive system 1000 illustrated in FIG. 10 is merely an example and is not a limitation of the scope of the present invention.
  • other configurations of the differential such as engines, transmissions, and the like, in accordance with embodiments of the present invention are known in the art and are well known to those skilled in the art and therefore will not be described again.
  • the differential 100 may further include: a power engagement device 400 and a joint driving device 500.
  • the power drive system 1000 may further include other components, such as a first motor generator and a second motor generator. .
  • the power engagement device 400 may include a first engagement portion 410 and a second engagement portion 420 that is coupled to one of the first ring gear 13 and the second ring gear 23, the second engagement portion 420 and the first planet carrier 11 and the second planet carrier 21 rotate in synchronization.
  • the first engaging portion 410 and the second engaging portion 420 are selectively engageable, and since the first carrier 11 and the second carrier 21 constitute a power input end of the differential 100, the first ring gear 13 and the second ring gear 23
  • the first engaging portion 410 may rotate synchronously with one of the first ring gear 13 and the second ring gear 23.
  • the power can be directly transmitted into the first ring gear 13 or the second ring gear 23, so that the output power of the first ring gear 13 and the second ring gear 23 can be made the same.
  • the joint driving device 500 includes a driving needle 510 and a driving portion, the driving needle 510 is disposed to be rotatable with the first carrier 11 and the second carrier 21, and the driving needle 510 can be opposite to the first planet.
  • Frame 11 and The two planet carriers 21 are axially moved.
  • the two ends of the driving pin 510 are respectively engaged with the driving portion and the second engaging portion 420.
  • the driving portion is configured to drive the driving pin 510 to drive the second engaging portion 420 toward the first joint in the axial direction.
  • the direction of the portion 410 is moved such that the second engaging portion 420 engages the first engaging portion 410. That is, the driving portion may be used to drive the driving needle 510 to move axially, and the axially moving driving needle 510 may urge the second engaging portion 420 to move axially to engage the second engaging portion 420 and the first engaging portion 410.
  • the first motor generator is disposed to be coupled to the first ring gear 13 and the coupled power output is to one of a pair of wheels
  • the second motor generator is disposed to be coupled to the second ring gear 23 and coupled
  • the rear power is output to the other of the pair of wheels.
  • the pair of wheels can be a set of front wheels or a set of rear wheels.
  • the conventional electric lock-type differential incorporates an electric actuating locking mechanism based on a common open differential, so that the differential has a locking function and is locked by an electric control differential.
  • This is an electric lock differential that is usually applied to a centralized drive type fuel vehicle, that is, the power is distributed to the left and right half shafts respectively after passing through the final drive and the differential, and the left and right wheel speeds are adjusted by the differential. difference.
  • a centralized drive type fuel vehicle that is, the power is distributed to the left and right half shafts respectively after passing through the final drive and the differential, and the left and right wheel speeds are adjusted by the differential. difference.
  • Such an electric lock differential is bulky and an electric vehicle has no engine.
  • the drive shaft locking device 100 of the present invention is significantly different in structure and implementation from the conventional electric lock-up differential, whereby the joint driving device 500 drives the second engaging portion 420 to engage the first engagement.
  • the joint driving device 500 drives the second engaging portion 420 to engage the first engagement.
  • the output rotational speeds of the first ring gear 13 and the second ring gear 23 are the same, so that the synchronous locking of the two half shafts can be realized, which can be advantageous for improving the vehicle's ability to remove the trap.
  • the first planetary axle 14 and/or the second planetary axle 24 may constitute a drive needle 510. That is, the first planetary axle 14 can be used as the drive pin 510, or the second planetary axle 24 can be used as the drive pin 510, or the first planetary axle 14 and the second planetary axle 24 can be used simultaneously as the drive pin 510.
  • the drive pin 510 is spaced apart from the first planetary axle 14 and the second planetary axle 24.
  • the drive pin 510 is a separately arranged component such that modifications to the first planetary axle 14 and the second planetary axle 24 can be reduced, and the first planetary axle 14 and the second planetary axle 24 can be maintained at an appropriate length, and Conducive to the design and manufacture of the differential.
  • At least one of the first planetary axle 14, the second planetary axle 24 and the drive pin 510 is coupled to the second engagement portion 420 such that the second engagement portion 420 follows the first planet carrier 11
  • the second carrier 21 rotates in synchronization. That is, the component connected to the second joint portion 420 may be at least one of the above three components, and since the three components are all rotated in synchronization with the first planet carrier 11 and the second planet carrier 21, this may cause the second component
  • the engaging portion 420 is rotatable in synchronization with the first carrier 11 and the second carrier 21.
  • an annular sleeve 600 may be disposed between the first engaging portion 410 and one of the first ring gear 13 and the second ring gear 23,
  • the sleeve 600 surrounds the second joint portion 420.
  • the sleeve 600 can function as a connection, and the first joint portion 410 and the first ring gear 13 and the second ring gear 23 can be secured.
  • One of the synchronous rotations, and the sleeve 600 can also function to protect the second engaging portion 420 at least to some extent.
  • the power drive system 1000 may further include: an elastic device 700 elastically disposed between the first joint portion 410 and the second joint portion 420 to make the second joint portion
  • the 420 has a tendency to move away from the first joint 410.
  • the elastic device 700 may provide the second engaging portion 420 with an elastic force to urge the second engaging portion 420 to move away from the first engaging portion 410.
  • the resilient device 700 can be received within the sleeve 600.
  • the elastic device 700 can be disposed within the sleeve 600, and the sleeve 600 can function to protect the elastic device 700, thereby reducing the risk of failure of the elastic device 700.
  • one of the first ring gear 13 and the second ring gear 23 has an integrally formed annular extension that constitutes the sleeve 600. This makes it possible to make one of the first ring gear 13 and the second ring gear 23 simple in structure and easy to manufacture.
  • the driving portion may include a follower portion 520 , the follower portion 520 can rotate with the driving pin 510 , and the follower portion 520 can be braked, and the driving portion 520 is provided with a driving surface 530 .
  • the follower 520 is braked, the sliding of the driving pin 510 on the driving surface 530 is changed to change the position of the driving pin 510 and the driving surface 530, thereby driving the driving surface 530 to drive the driving pin 510 to move in the axial direction, so that the first The second joint portion 420 engages the first joint portion 410.
  • the follower portion 520 and the driving pin 510 may be in a synchronous rotation relationship before the follower portion 520 is not braked, but after the follower portion 520 is braked, the rotation speed of the follower portion 520 is decreased.
  • a difference in rotational speed will occur between the follower 520 and the drive pin 510, such that the drive pin 510 can slide over the drive surface 530 of the follower 520, and the drive pin 510 after sliding can be relative to the first planet carrier 11 and the second planet
  • the frame 21 is axially moved, so that the driving pin 510 can bring the second engaging portion 420 closer to the first engaging portion 410 until the second engaging portion 420 is engaged with the first engaging portion 410.
  • the driving portion may further include: a braking portion that is provided for braking the follower portion 520. That is, the braking portion can function as the brake follower 520, and the braking portion can brake the follower portion 520 when the first engaging portion 410 and the second engaging portion 420 are required to be engaged.
  • a braking portion that is provided for braking the follower portion 520. That is, the braking portion can function as the brake follower 520, and the braking portion can brake the follower portion 520 when the first engaging portion 410 and the second engaging portion 420 are required to be engaged.
  • the braking portion may be arranged to brake the follower 520 with electromagnetic force.
  • the electromagnetic force control is precise and reliable, so that the operational reliability of the drive shaft locking device can be improved, and the service life of the drive shaft locking device can be extended.
  • the driving portion may be an electromagnetic brake
  • the follower portion 520 constitutes a brake member of the electromagnetic brake
  • the braking portion constitutes a brake bracket of the electromagnetic brake.
  • the driving surface 530 may be a bevel or a curved surface.
  • the drive surface 530 as a bevel or curved surface, it is possible to facilitate the sliding of the drive needle 510 on the drive surface 530 and to cause the drive needle 510 to move in the axial direction.
  • the driving surface 530 may include: a first segment 530a and a second segment 530b.
  • the first segment 530a and the second segment 530b are connected, and the connection between the first segment 530a and the second segment 530b is the lowest point, and the first segment 530a And the second paragraph 530b The other end away from the connection is the highest point.
  • the first engaging portion 410 and the second engaging portion 420 are in a separated state, and when one end of the driving pin 510 is at the highest point or adjacent to the highest point, the first engaging portion 410 and The second joint portion 420 is in an engaged state.
  • each of the first segment 530a and the second segment 530b may be arcuate.
  • the first segment 530a and the second segment 530b of the arc shape may facilitate sliding of one end of the driving pin 510 on the driving surface 530, and the movement resistance of the driving pin 510 may be reduced.
  • each of the first segment 530a and the second segment 530b has a corresponding center angle.
  • the first segment 530a and the second segment 530b are substantially identical, such that the drive pin 510 can be more slidable on the drive surface 530.
  • the drive surface 530 can be multi-segmented and the multi-segment drive faces 530 are circumferentially spaced apart.
  • the number of driving pins 510 can correspond to the number of driving faces 530, which can increase the number of driving pins 510, so that the plurality of driving pins 510 and the second engaging portion 420 can be made to be reliable, and the second engaging portion can be made The 420 axial movement is reliable, which makes the drive shaft locking device work more reliably.
  • the plurality of driving surfaces 530 can be connected by a connection plane, and the connection plane is flush with the highest point. This can improve the structural reliability of the driving surface 530 of the follower portion 520 at least to some extent, and can improve the structural reliability of the driving shaft locking device.
  • the follower portion 520 may include: a follower body 520a and an annular follower flange 520b disposed on the follower body 520a, the follower portion A drive surface 530 is provided on an end surface of the flange 520b facing the drive pin 510.
  • the follower body 520a can effectively enhance the structural reliability of the follower portion 520, and the driving surface 530 can be disposed on the end surface of the follower portion flange 520b, so that the design difficulty of the driving surface 530 can be reduced, and the driving surface 530 can be improved. Structural reliability.
  • the driving surface 530 may be provided with a driving surface limiting groove 530c, and one end of the driving pin 510 is located in the driving surface limiting groove 530c. Therefore, by providing the driving surface limiting groove 530c, one end of the driving pin 510 can be engaged in the driving surface limiting groove 530c, so that at least a certain end of the driving pin 510 can be prevented from being detached from the driving surface 530, which can be improved. The reliability and stability of the drive needle 510 moving within the drive surface 530.
  • the driver controls the electromagnetic brake to be energized, and the brake frame brakes the brake member, so that the rotation speed of the brake member is suppressed, and a rotation speed difference is generated between the drive needle 510 and the brake member, and the drive needle 510 is
  • the driving surface 530 of the brake member slides, the driving needle 510 can slide from the lowest point of the driving surface 530 to the highest point or the position adjacent to the highest point, and the driving needle 510 is axially moved to one side of the second engaging portion 420 to drive
  • the needle 510 can also drive the second engaging portion 420 to gradually approach the first engaging portion 410 until the first engaging portion 410 and the second engaging portion 420 are engaged, at this time, the left and right half shafts Synchronous rotation, the left wheel Z1 and the right wheel Z2 are at the same speed, so that the vehicle's ability to escape can be improved.
  • the driver can press the electromagnetic brake again, the electromagnetic brake is de-energized, and the elastic device pushes the second engaging portion 420 to move axially away from the first engaging portion 410.
  • the driving pin 510 follows the first The two engaging portions 420 are axially moved, and the end of the driving pin 510 that cooperates with the driving surface 530 can be gradually slid from the highest point or the position adjacent to the highest point to the lowest point.
  • the second engaging portion 420 and the first engaging portion 410 are completely Separate, the vehicle can continue to travel according to the normal straight-line driving of the vehicle and the normal turning mode of the vehicle.
  • a vehicle 10000 according to an embodiment of the present invention which includes the power drive system 1000 of the above embodiment, which can be used for a front drive and of course for a rear drive, will be briefly described below.
  • the present invention is not particularly limited thereto.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un différentiel (100), et un véhicule (10000). Le différentiel (100) comprend : deux mécanismes d'engrenage planétaire, des couronnes dentées (13, 23) étant utilisées comme extrémité de sortie de puissance, une partie d'entrée et deux porte-satellites (11, 21) étant disposés de manière coaxiale, et la partie d'entrée étant reliée aux deux porte-satellites (11, 21) ; un dispositif de prise de puissance (400) comprenant des première et seconde parties de prise (410, 420), la première partie de prise (410) étant reliée à l'une des deux couronnes dentées (13, 23), la seconde partie de prise (420) tournant en synchronisme avec les deux porte-satellites (11, 21), et les deux porte-satellites (11, 21) formant une extrémité d'entrée de puissance du différentiel (100) ; et un dispositif d'entraînement de partie de prise (500) comprenant une broche d'entraînement (510) et une partie d'entraînement, la partie d'entraînement étant configurée pour entraîner la broche d'entraînement (510) pour entraîner la seconde partie de prise (420) en mouvement le long d'une direction d'essieu vers la première partie de prise (410), de telle sorte que la seconde partie de prise (420) est mise en prise avec la première partie de prise (410). De cette manière, le différentiel selon la présente invention peut verrouiller deux demi-essieux afin d'améliorer l'aptitude d'un véhicule à supporter un terrain accidenté.
PCT/CN2017/116565 2016-12-27 2017-12-15 Différentiel, et véhicule Ceased WO2018121291A1 (fr)

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CN201611229293.6A CN108240451B (zh) 2016-12-27 2016-12-27 差速器以及车辆
CN201611229293.6 2016-12-27

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CN110052650B (zh) * 2019-05-21 2024-11-05 苏州工业职业技术学院 一种高定位精度的开孔器
CN112392934B (zh) * 2019-07-31 2025-11-07 舍弗勒技术股份两合公司 差速器总成
CN112178152B (zh) * 2020-10-16 2023-02-21 魏家斌 斜齿轮差速器
CN116447297A (zh) * 2023-04-20 2023-07-18 臻驱科技（上海）有限公司 一种动力耦合装置、动力传动结构及车辆

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CN117432767B (zh) * 2023-12-21 2024-03-29 中国第一汽车股份有限公司 减速器及车辆

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