JP2005180510A - Differential gear device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a differential gear device for a vehicle, including a torque-sensitive differential gear mechanism generating differential limiting force in response to torque and a speed sensitive differential limiting means generating differential limiting force in response to a differential rotating speed, solving the problems of increasing the size of the differential gear device for a vehicle and increasing in weight placing limitations on loading to the vehicle because the torque sensitive differential gear mechanism and the speed sensitive differential limiting means, which are all constructed independently, are simply arranged side by side in the axial direction. <P>SOLUTION: This differential gear device for a vehicle includes: a pressing member 20 receiving the thrust force applied to a planetary gear 15 of a torque sensitive differential gear device 10a, and further it includes a speed sensitive pressing force generating means 10b for pressing the pressing member 20 toward the planetary gear 15 with the pressing force depending on the front wheel side and rear wheel side differential rotating speed. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a vehicle equipped with a torque-sensitive differential limiting means that generates a differential limiting force in response to torque and a speed-sensitive differential limiting means that generates a differential limiting force in response to a differential rotational speed. The present invention relates to a differential gear device.

  In a four-wheel drive vehicle equipped with a center differential, a vehicle differential gear device equipped with a torque-sensitive differential limiting means and a speed-sensitive differential limiting means is incorporated in the center differential. Is known.

  This kind of vehicle differential gear device includes a pair of differential gears connected to respective power transmission shafts connected to the front wheel side and the rear wheel side, and a connection for connecting these differential gears so as to be differentially rotatable. Torque-sensitive differential limiting means comprising a gear and a differential case that rotatably accommodates and supports these coupling gears, and is interposed between the two power transmission shafts and is sensitive to the differential rotational speed between the two power transmission shafts. And a speed-sensitive differential limiting means comprising a viscous coupling.

Japanese Patent Laid-Open No. 6-33996 (paragraph number 0021 to paragraph number 0030, FIG. 1 on page 3)

  In the above-described conventional differential gear device for a vehicle, torque-sensitive differential limiting means and speed-sensitive differential limiting means having independent configurations are simply arranged in parallel in the axial direction. As the differential device becomes larger, the weight increases, and there is a problem that the mounting on the vehicle is restricted.

  In order to solve the above problems, the structural feature of the invention described in claim 1 is that a housing and a helical gear connected to one of the front wheel side or the rear wheel side and rotatably supported in the housing are provided. 1 gear, a second gear composed of a helical gear connected to the other of the front wheel side or the rear wheel side and rotatably supported in the housing, and the first and second gears rotatably supported in the housing. And a planetary gear comprising a helical gear meshing with a gear of the vehicle, and having a torque-sensitive differential limiting function for distributing engine power transmitted to the housing to the first and second gears via the planetary gear. The dynamic gear device includes a pressing member that receives a thrust force acting on the planetary gear, and the pressing member is connected to the first gear and the second gear. It is characterized in that a pressing force corresponding to the moving speed with a pressing force generating unit for pressing said planetary gear.

  The structural features of the invention according to claim 2 are: a housing, an internal gear comprising a helical gear connected to one of the front wheel side and the rear wheel side and rotatably supported in the housing; A sun gear composed of a helical gear connected to the other wheel side and rotatably supported in the housing; and an internal gear and a sun gear rotatably supported in a storage hole provided in a carrier connected to the housing. In a vehicle differential gear device having a torque-sensitive differential limiting function that distributes engine power transmitted to the housing to an internal gear and a sun gear via the planetary gear. The planetary gear is made by the differential rotation of the internal gear and the sun gear. A pressing member that receives a thrust force to be pressed, and a pressing force generation unit that presses the pressing member toward the planetary gear with a pressing force corresponding to a differential rotational speed of the internal gear and the sun gear. To do.

  The structural features of the invention according to claim 3 are: a housing; a pair of sun gears connected to the front wheel side and the rear wheel side, respectively, supported rotatably around a common axis in the housing; And a pair of planetary gears supported rotatably about an axis parallel to the common axis, each sun gear having a helical gear, and each planetary gear meshing with each sun gear individually. A gear-like second gear portion that meshes with each planetary gear, and the housing is formed with a receiving hole for rotatably receiving the planetary gear, and the engine power transmitted to the housing is transmitted to the planetary gear. In the vehicle differential gear device having a torque-sensitive differential limiting function that distributes to the pair of sun gears via the A pressing member that receives a thrust force acting on the planetary gear by differential rotation with the pair of gears, and generates a pressing force that presses the pressing member toward the planetary gear with a pressing force corresponding to the differential rotation speed with the pair of sun gears. Means are provided.

  According to a fourth aspect of the present invention, there is provided a structural feature of the first, second, or third aspect, wherein the pressing force generating means is formed between the housing and the pressing member. A concave portion enclosing a viscous fluid and the first or second output shaft connected to the first or second output shaft are caused to flow by the differential rotation of the housing and the first or second output shaft. And a blade that presses the pressing member toward the end face of the planetary gear with a pressing force corresponding to a differential rotational speed with respect to the output shaft.

  The structural feature of the invention according to claim 5 is that according to claim 4, wherein the cross-sectional shape of the blade is asymmetric in the circumferential direction.

  The invention according to claim 1 configured as described above includes the first gear, the second gear, and the planetary gear that are formed of helical gears, and distributes engine power to the first and second gears via the planetary gear. A torque-sensitive differential gear mechanism and a pressing member that receives a thrust force acting on the planetary gear of the differential gear mechanism are provided, and the pressing member is pressed according to the differential rotational speeds of the first and second gears. Since the pressing force generating means for pressing toward the planetary gear is provided, it is possible to obtain a vehicle differential gear device including a smaller and lighter torque-sensitive differential limiting means and a speed-sensitive differential limiting means. There is an advantageous effect in mounting on a vehicle.

  In the invention according to claim 2 configured as described above, a torque-sensitive differential is provided that includes an internal gear, a sun gear, and a planetary gear that are helical gears, and distributes engine power to the internal gear and the sun gear via the planetary gear. A gear mechanism and a pressing member that receives a thrust force acting on the planetary gear of the differential gear mechanism are provided. The pressing member presses the pressing member toward the planetary gear with a pressing force corresponding to the differential rotational speed of the internal gear and the sun gear. Since the pressure generating means is provided, it is possible to obtain a vehicle differential gear device having a smaller and lighter torque-sensitive differential limiting means and a speed-sensitive differential limiting means, which is advantageous for mounting on a vehicle. In addition, there is an effect of obtaining an uneven torque distribution characteristic that is optimal for the center differential.

  In the invention according to claim 3 configured as described above, a torque-sensitive differential gear mechanism that includes a pair of side gears composed of helical gears and a planetary gear, and distributes engine power to the pair of side gears via the planetary gear; A pressing member that receives a thrust force acting on the planetary gear of the differential gear mechanism is provided, and a pressing force generating means that presses the pressing member toward the planetary gear with a pressing force according to the differential rotational speed of the pair of side gears. Therefore, it is possible to obtain a vehicle differential gear device having a smaller and lighter torque-sensitive differential limiting means and a speed-sensitive differential limiting means, which is advantageous for mounting on a vehicle and has an equal torque distribution characteristic. Is effective.

  Further, in the invention according to claim 4 configured as described above, the pressing force generating means is configured to provide a difference between the concave portion formed between the housing and the pressing member and enclosing the viscous fluid, and the viscous fluid in the concave portion. A blade that presses the pressing member toward the end face of the planetary gear with a pressing force according to the differential rotation speed by flowing by dynamic rotation is provided, so that differential limiting force is generated in response to the differential rotation speed of the front and rear wheels There is an effect that the pressing force generating means can be configured in a smaller size.

  Furthermore, in the invention according to claim 5 configured as described above, since the cross-sectional shape of the blade is formed asymmetrically in the circumferential direction, the generated pressure is larger in the reverse differential rotation than in the forward differential rotation. The pressing force can be reduced by lowering the pressure, thereby preventing the interference with the ABS.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The vehicle differential gear device 10 in this embodiment includes a housing 11, an internal gear 12, a sun gear 13, a carrier 14, and a planetary gear 15 as main components.

  The housing 11 has a cylindrical portion 11a that is driven to rotate about the rotation axis L by an unillustrated engine. A bottom portion 11b is formed at one end portion (left end portion in FIG. 1) of the cylindrical portion 11a, and a through hole 11c is formed in the bottom portion 11b. The carrier 14 is spline-engaged with the other end portion (right end portion in FIG. 1) of the inner peripheral surface of the cylindrical portion 11a, and is positioned and fixed by a stopper 16 screwed into the opening end of the cylindrical portion 11a.

  On the inner peripheral surface of the cylindrical portion 11a, an internal gear 12 having a helical gear 12a formed on the inner periphery is fitted so as to be rotatable about the rotation axis L. An annular connecting portion 12b is formed on the inner peripheral surface of one end on the bottom side of the internal gear 12, and the output member 17 is spline-engaged with the inner peripheral surface of the annular connecting portion 12b. A cylindrical portion 17a that penetrates the through hole 11c formed in the bottom portion 11b is formed at one end portion (left end portion in FIG. 1) of the output member 17. A spline 17b is formed on the inner peripheral surface of the output member 17, and a first output shaft connected to the front wheel side or the rear wheel side (not shown) is spline-engaged with the spline 17b. .

  A cylindrical sun gear 13 is disposed inside the internal gear 12 so as to be rotatable about the rotation axis L, and a helical gear 13 a is formed on the outer periphery of the sun gear 13. A spline 13b is formed on the inner peripheral surface of the sun gear 13, and a second output shaft connected to the rear wheel side or the front wheel side is spline engaged with the spline 13b (not shown).

  A cylindrical support portion 14a is formed concentrically with the rotation axis L on the carrier 14, and the support portion 14a is formed between the inner peripheral surface of the internal gear 12 and the outer peripheral surface of the sun gear 13 at the bottom portion 11b. It extends towards the side. In the support portion 14a, a circular accommodation hole 18 having an intermediate diameter between the inner diameter of the internal gear 12 and the outer diameter of the sun gear 13 from the distal end to the proximal end portion is equiangular on the circumference. A plurality (eight in the embodiment) are formed at intervals. The inner diameter of each accommodation hole 18 is set to be larger than the radial thickness of the support portion 14a, whereby the outer peripheral side and inner peripheral side of the reception hole 18 are opened from the outer peripheral surface and inner peripheral surface of the support portion 14a, respectively. Yes.

  Each accommodation hole 18 accommodates a planetary gear 15 so that the planetary gear 15 can rotate and move in the axial direction. One end surface (left end surface) of the planetary gear 15 is frictionally engaged with the inner wall of the annular coupling portion 12b via a thrust washer 19, The other end surface (right end surface) is disposed so as to frictionally engage with the bottom surface 18 a of the accommodation hole 18. The outer diameter of the planetary gear 15 is set to be slightly smaller than the inner diameter of the accommodation hole 18 so that it can rotate in the accommodation hole 18. A helical gear 15a is formed on the outer periphery of the planetary gear 15 over its entire length. The helical gear 15a meshes with the helical gear 12a of the internal gear 12 at the opening portion outside the accommodation hole 18, and at the opening portion inside the accommodation hole 18. The sun gear 13 meshes with the helical gear 13a.

  Therefore, when the housing 10 is driven to rotate, the rotation is transmitted to the internal gear 12 and the sun gear 13 via the carrier 14 and the planetary gear 15. In this case, when the planetary gear 15 does not rotate, the internal gear 12 and the sun gear 13 rotate integrally. However, when the planetary gear 15 rotates, the internal gear 12 and the sun gear 13 rotate differentially, resulting in a differential limiting force. Occur.

  The housing 11, the internal gear 12, the sun gear 13, the carrier 14, the planetary gear 15 and the like constitute a torque-sensitive differential gear mechanism 10a that generates a differential limiting force in response to torque. .

  A pressing member 20 is disposed between the bottom 11b of the housing 11 and the annular connecting portion 12b of the internal gear 12, and a thrust washer 21 is interposed between the pressing member 20 and the annular connecting portion 12b. Yes. The outer periphery of the pressing member 20 is spline engaged with the inner periphery of the housing 11 so as to be movable only in the axial direction, and the inner periphery thereof is closely fitted to the outer periphery of the cylindrical portion 16 a of the output member 17. A concave portion 20b having a relatively small depth is formed on the end surface of the pressing member 20 on the bottom portion 11b side, except for the outer peripheral edge 20a contacting the bottom portion 11b. A thin rotor 22 corresponding to the depth of the recess 20 b is rotatably accommodated in the recess 20 b, and the rotor 22 is splined to the outer periphery of the output member 17. As shown in FIG. 3, the rotor 22 is formed with three blades 23 extending in the radial direction at equal angular intervals on the circumference, and the outer periphery of the blade 23 abuts on the inner periphery of the outer peripheral edge 20a so as to be slidable. Has been. A highly viscous fluid such as silicone oil is sealed in the recess 20b.

  The cross section of the blade 23 is asymmetric in the circumferential direction. That is, as shown in detail in FIG. 4, the intermediate width portion 23a in the circumferential width is formed thick and both end portions 23b and 23c are formed thin. Further, with reference to the intermediate portion 23a, the thickness portion 23c on the clockwise side in the drawing is long, and the thickness portion 23b on the counterclockwise side in the drawing is short in size.

  As a result, when the housing 11 and the output member 17 are relatively rotated, the highly viscous fluid in the recess 20b is caused to flow by the blade 23, and the housing 11 and the output member 17 are relatively moved into the recess 20b by the viscous frictional action of the highly viscous fluid. Pressure corresponding to the rotation speed is generated. By this pressure, the pressing member 20 is pressed to the planetary gear 15 side, and the frictional resistance of both end surfaces of the planetary gear 15 is increased. The effect of increasing the frictional resistance is increased according to the differential rotation between the housing 11 and the output member 17.

  At this time, since the blades 23 of the rotor 22 are formed in an asymmetric shape in the circumferential direction, the generated pressure in the forward / reverse differential direction of the rotor 22 can be made different. That is, the generated pressure can be increased during forward rotation differential, and the generated pressure can be decreased during reverse rotation differential.

  A pressing force generating means 10b that generates a differential limiting force in response to the differential rotational speed of the front and rear wheels by the pressing member 20, the rotor 22 having the blade 23, and the highly viscous fluid enclosed in the recess 20b. Is configured.

  In the figure, reference numerals 26 and 27 denote thrust washers. The thrust washers 26 and 27 are interposed between both ends of the sun gear 13 and the output member 17 and the carrier 14.

  With the configuration described above, when the housing 11 is rotationally driven by the engine, the carrier 14 is rotated integrally with the housing 11, and the planetary gear 15 accommodated in the accommodation hole 18 of the carrier 14 is rotated about the rotation axis L. The Thus, engine power is distributed from the planetary gear 15 to the front wheel side and the rear wheel side via the internal gear 12, the output member 17, and the sun gear 13. At this time, a large driving torque is sent to the front wheel or rear wheel on the side of the internal gear 12 having a large tooth diameter, and a smaller driving torque is sent to the rear wheel or front wheel on the side of the sun gear 13 having a small tooth diameter. Unequal torque distribution characteristics that are optimal for differentials can be obtained.

  Then, for example, when driving on a rough road, a difference in driving resistance occurs between the front wheels and the rear wheels, and if a difference occurs between the internal gear 12 and the sun gear 13, each planetary gear 15 rotates. As a result, the outer periphery of each planetary gear 15 is pressed against the accommodation hole 18 by the meshing reaction force with the sun gear 13 to generate a frictional resistance. As a result, the internal gear 12 is pressed against the inner peripheral surface of the housing 11 by the meshing reaction force with each planetary gear 15 to generate frictional resistance.

  Further, since the internal gear 12, the sun gear 13, and the planetary gear 15 are constituted by the helical gears 12a, 13a, and 15a, a thrust force is generated in the planetary gear 15 by the meshing reaction force, and each of the gears depends on the traveling direction of the vehicle. The end surface of the planetary gear 15 is pressed against the bottom surface 18a of the storage hole 18 or is pressed against the end surface of the thrust washer 19, thereby generating a frictional resistance. Such frictional resistance provides a torque sensitive differential limiting function.

  Further, in the vehicle differential gear device 10 configured as described above, when differential rotation occurs between the internal gear 12 and the sun gear 13, the housing 11 and the output member 17 rotate relative to each other, and the pressing force generation means 25 Is rotated relative to the housing 11 in the recess 20b to flow the highly viscous fluid sealed in the recess 20b. As a result, a pressure corresponding to the relative rotational speed between the output member 17 and the housing 11 is generated in the recess 20b, and the pressure member 20 is pressed toward the planetary gear 15 by this pressure, and the thrust washer 21, the annular connecting portion 12b, and the thrust The planetary gear 15 is pressed in the thrust direction via the washer 19, and the frictional resistance between the both end surfaces of each planetary gear 15 and the bottom surface 18 a of the storage hole 18 and each end surface of the thrust washer 19 is increased.

  By increasing the frictional resistance, in addition to the torque-sensitive differential limiting function, the differential limiting force can be increased according to the differential between the front and rear wheels.

  In this case, during reverse rotation, the generated pressure is lower than that during forward rotation and the pressing force can be reduced. Therefore, interference with ABS (anti-lock brake system) can be prevented.

  FIG. 5 shows another embodiment of the present invention. The vehicle differential gear device 30 according to this embodiment is applied to a parallel shaft type differential gear device having a configuration described in Japanese Patent Laid-Open No. 6-33996.

  In FIG. 5, a pair of side gears 32 and 33 made of helical gears are disposed inside the housing 31 so as to be rotatable around a common axis L. Although not shown, the first output shaft connected to the front wheel side or the rear wheel side is spline-engaged with one (left side in the figure) and the other (right side in the figure). Although not shown, the second output shaft connected to the rear wheel side or the front wheel side is spline-engaged with the side gear 33.

  The housing 31 is provided with a first storage hole 34 and a second storage hole (not shown) adjacent to the first storage hole 34 in the circumferential direction in the axial direction. A first planetary gear (pinion gear) 35 is housed in the first housing hole 34 so as to be rotatable and slidable. A second planetary gear (not shown, but described as 35a for convenience) is housed in the second housing hole. Is housed in a rotatable and slidable manner.

  The first planetary gear 35 includes gear portions 36 and 37 made of helical gears at both ends and a shaft portion 38 connecting them, and the shaft portion 38 has a small diameter in order to avoid interference with the right side gear 33. The left end gear portion 36 meshes with the left side gear 32, and the right end gear portion 37 meshes with a gear portion formed of a helical gear formed at the right end of the second planetary gear 35a. Further, a gear portion formed of a helical gear formed at the left end of the second planetary gear 35 a meshes with the right side gear 33. A thrust washer 39 is attached to the housing 31 to prevent the first and second planetary gears 35 and 35a from falling off. Thus, a torque-sensitive differential gear mechanism 30a that generates a differential limiting force in response to torque is configured.

  A pressing member 41 is disposed between the bottom 31a of the housing 31 and the first and second planetary gears 35 and 35a. The pressing member 41 and the planetary gears 35 and 35a are respectively provided in the thrust direction via thrust washers 42. It is joined. The outer periphery of the pressing member 41 is spline-engaged with the inner periphery of the housing 31 so as to be movable only in the axial direction, and the inner periphery is engaged with the outer periphery of the left side gear 32. A concave portion 41b having a relatively small depth is formed on the end surface of the pressing member 41 on the side of the bottom portion 31a except for the outer peripheral edge 41a that contacts the bottom portion 31a. A thin rotor 43 corresponding to the depth of the recess 41b is rotatably accommodated in the recess 41b, and the rotor 43 is spline-engaged with the outer periphery of the side gear 32. The rotor 43 is provided with a blade having the same shape as described in the previous embodiment. Further, a highly viscous fluid such as silicon oil is sealed in the recess 41b, and these structures constitute a pressing force generating means 30b that generates a differential limiting force in response to the differential rotational speed of the front and rear wheels. .

  With the configuration described above, when the housing 31 is driven by engine power, the driving force is distributed from the planetary gears 35 and 35a to the side gears 32 and 33 and transmitted to the front wheel side and the rear wheel side. When a driving resistance difference occurs between the front and rear wheels, the engine power is differentially distributed to the front and rear wheels by the rotation of the planetary gears 35 and 35a.

  Also in this embodiment, since the side gears 32 and 33 and the planetary gears 35 and 35a are constituted by helical gears, the planetary gears are generated by the thrust force generated by the engagement between the side gears 32 and 33 and the planetary gears 35 and 35a. 35 and 35a are frictionally engaged with the pressing member 41 or frictionally engaged with the thrust washer 39 according to the traveling direction of the vehicle, and a differential limiting force is generated by the frictional resistance.

  When differential rotation occurs between the pair of side gears 32 and 33, the pressing member 41 is pressed toward the planetary gears 35 and 35a with a pressure corresponding to the differential rotation speed, and both end surfaces of the planetary gears 35 and 35a. In order to increase the frictional resistance acting on the vehicle, in addition to the torque-sensitive differential limiting function, the differential limiting force can be increased in accordance with the differential between the front and rear wheels, as in the above-described embodiment. become.

  In the above-described embodiment, the pressing force generating means for generating the differential limiting force in response to the differential rotational speed of the front and rear wheels is a recess formed between the housing and the pressing member and enclosing the viscous fluid. Since the viscous fluid in the recess is made to flow by differential rotation and the pressing member is pressed toward the end face of the planetary gear with the pressing force according to the differential rotation speed, the pressing force generating means is arranged in the axial direction. However, the present invention is not limited to such a configuration, and generates a pressing force corresponding to a differential rotational speed, such as a vane pump or a plunger pump. What can be applied is also applicable.

It is sectional drawing which shows embodiment of this invention. It is sectional drawing along the AA line of FIG. It is sectional drawing along the BB line of FIG. FIG. 4 is a cross-sectional view taken along the line CC in FIG. 3. It is sectional drawing which shows other embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10, 30 ... Differential gear apparatus for vehicles, 10a, 30a ... Differential gear mechanism, 10b, 30b ... Pressing force generation means, 11, 31 ... Housing, 12 ... Internal gear, 13 ... Sun gear, 14 ... Carrier, 15 ... Planetary gear, 12a, 13a, 15a ... Helical gear, 17 ... Output member, 18 ... Storage hole, 20, 41 ... Pressing member, 20b, 41b ... Recess, 22, 43 ... Rotor, 23, 44 ... Blade, 32, 33 ... Side gear, 34 ... storage hole, 35 ... planetary gear.

Claims (5)

The housing is connected to one of the front wheel side or the rear wheel side and is connected to the other one of the front wheel side or the rear wheel side and is rotatable in the housing. A second gear composed of a helical gear supported on the housing, and a planetary gear composed of a helical gear supported rotatably in the housing and meshing with the first and second gears, and transmits engine power transmitted to the housing. In the vehicle differential gear device having a torque-sensitive differential limiting function that distributes to the first and second gears via the planetary gear, the vehicle includes a pressing member that receives a thrust force acting on the planetary gear. Is pressed against the planetary gear with a pressing force corresponding to the differential rotational speed of the first and second gears. Differential gearing for vehicle, characterized in that it comprises a force generating means. A housing, an internal gear comprising a helical gear connected to one of the front wheel side or the rear wheel side and rotatably supported in the housing, and connected to the other of the front wheel side or the rear wheel side and rotatable in the housing A sun gear composed of a supported helical gear and a planetary gear composed of a helical gear that is rotatably supported in a receiving hole provided in a carrier connected to the housing and meshes with the internal gear and the sun gear. In a vehicle differential gear device having a torque-sensitive differential limiting function that distributes transmitted engine power to an internal gear and a sun gear via the planetary gear, the planetary gear is driven by differential rotation of the internal gear and the sun gear. With a pressing member that receives the thrust force acting on The pressing member the internal gear and the differential gearing for vehicle, characterized in that it comprises a pressing force generating unit for pressing said planetary gear with a pressing force corresponding to the rotational speed difference between the sun gear. A housing, a pair of sun gears connected to the front wheel side and the rear wheel side, respectively, supported in the housing so as to be rotatable around a common axis, and rotatable around an axis parallel to the common axis in the housing Each of the sun gears has a helical gear, and each of the planetary gears has a helical first gear portion that meshes with each of the sun gears, and a helical second gear that meshes with each of the planetary gears. A torque-sensitive difference for distributing engine power transmitted to the housing to the pair of sun gears via the planetary gear. In a vehicle differential gear device having a motion limiting function, a planetary gear is provided by differential rotation with the pair of sun gears. A pressing member for receiving a thrust force acting on the bearing member, and a pressing force generating means for pressing the pressing member toward the planetary gear with a pressing force corresponding to a differential rotational speed with the pair of sun gears. A differential gear device for a vehicle. The pressing force generation means is connected to the recess formed between the housing and the pressing member and enclosing viscous fluid, and the first or second output shaft, and the housing and the first or second output. A blade for causing the viscous fluid to flow by differential rotation with a shaft and pressing the pressing member toward an end surface of the planetary gear with a pressing force corresponding to the differential rotation speed with the first or second output shaft; The differential gear device for a vehicle according to claim 1, claim 2, or claim 3. The vehicle differential gear device according to claim 4, wherein a cross-sectional shape of the blade is formed asymmetrically in a circumferential direction.

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