JP2013096511A - Driving force transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device capable of miniaturizing a diameter of a first transmission gear.SOLUTION: This driving force transmission device includes a connecting hollow shaft 33 and an inclined transmission shaft 35 rotatably supported by a distribution case 9, mutually juxtaposed and capable of interlocking by first and second transmission gears 39 and 41, and a rear wheel side output shaft 37 rotatably supported by the distribution case 9 and capable of outputting by increasing a speed to the connecting hollow shaft 33 by interlocking with the inclined transmission shaft 35 by first and second crossing meshing gears 43 and 45. The second transmission gear 41 is formed of a tapered gear, and is slantingly meshed with the first transmission gear 39, a crossing angle of the rotational axes of the first and second crossing meshing gears 43 and 45 is set smaller than a right angle, the inclined transmission shaft 35 is juxtaposed at an inclination to the connecting hollow shaft 33, and an inter-axial distance between the first crossing meshing gear 43 and the connecting hollow shaft 33 is secured.

Description

  The present invention relates to a power transmission device used for a transfer device or the like.

  Conventionally, as a structure of a power transmission device, there is a transfer device for a four-wheel drive vehicle as described in Patent Document 1.

  This transfer device distributes and outputs the input to the front differential device to the rear wheel side, and is connected to the case with a second rotating member that is a hollow shaft connected to the case, a third rotating member that is a transmission intermediate shaft, and a rear wheel. A fourth rotating member which is a side output shaft is rotatably supported. The fourth rotating member is arranged orthogonal to the third rotating member, and the third rotating member is arranged parallel to the second rotating member.

  Between the second rotating member and the third rotating member, driving force is transmitted by the meshing of the first and second gears which are parallel meshing gears, and between the third rotating member and the fourth rotating member, Driving force is transmitted by meshing the third and fourth gears which are orthogonal meshing gears.

  Therefore, the driving force is distributed to the rear wheels by the transfer device, and four-wheel drive traveling can be performed.

  However, in the transfer device, since the first gear, which is the drive gear, is formed with a larger diameter than the second gear because of the need for speed increase, the outer periphery of the first gear is the shaft of the drive shaft. There was a problem that it protruded greatly toward the front engine side with respect to the heart, and it was difficult to obtain a clearance between the case and the engine.

  On the other hand, when the diameter of the first gear is reduced, the protrusion to the engine side is suppressed, and the clearance between the case and the engine can be easily obtained.

  However, when the first gear becomes smaller, the position of the third rotating member approaches the second rotating member, and the third gear of the third rotating member interferes with the second rotating member. The diameter of the first gear could not be simply reduced.

  On the other hand, the movement of the axial position of the third rotating member can be avoided by reducing the diameter of the first gear and increasing the diameter of the second gear of the third rotating member.

  However, when the diameter of the first gear is reduced and the diameter of the second gear is increased, the third speed is increased in order to ensure the overall speed increasing ratio between the second rotating member and the fourth rotating member. It is necessary to increase the diameter of the gear, and it interferes with the second rotating member as described above.

  For this reason, the diameter of the first gear cannot be simply reduced.

JP 2008-208947 A

  The problem to be solved is that even if it is necessary to suppress the protrusion of the case, the diameter of the drive gear cannot be simply reduced.

  In order to reduce the diameter of the drive gear and suppress the protrusion of the case, the present invention is rotatably supported by the case and is provided adjacent to each other and interlocked by the first and second transmission gears. The first and second transmission shafts and the first and second cross-meshing gears that are rotatably supported by the case are interlocked with the second transmission shaft to increase the speed of the first transmission shaft. A third transmission shaft that can be output, and the second transmission shaft is disposed side by side with an inclination with respect to the first transmission shaft, and the first cross-meshing gear and the first transmission shaft A distance between the transmission shaft and the transmission shaft is ensured.

  The power transmission device of the present invention has the above-described configuration, ensures a distance between the first cross-meshing gear and the first transmission shaft, and reduces the diameter of the first transmission gear of the first transmission shaft. can do.

It is a skeleton top view of a four-wheel drive vehicle. Example 1 It is a plane sectional view of a transfer device. Example 1 It is a side view of the transfer apparatus which shows the relationship with an engine. Example 1

  The object of making it possible to reduce the diameter of the drive gear is realized by arranging the second transmission shaft side by side with an inclination with respect to the first transmission shaft.

[Overall configuration of four-wheel drive vehicle]
FIG. 1 is a skeleton plan view of a four-wheel drive vehicle.

  As shown in FIG. 1, the transfer device 1 that is the power transmission device of the present embodiment is disposed on the outer periphery of the intermediate output shaft 3 on the front wheel side and is coupled to the rear wheel output side of the front differential device 5. As a case, the distribution case 9 of the transfer device 1 is attached to the bell housing 13 on the side of the transmission 11.

  The front differential device 5 is supported in the bell housing 13. The front differential device 5 receives a drive input from the transmission 11 to the ring gear 15. Driving input is performed from the engine 17 to the input shaft of the transmission 11.

A motor / generator 19 is coupled to the input shaft of the transmission 11 to assist the engine 17 during acceleration or the like, and to generate power during deceleration or the like. Intermediate output shafts 21 and 3 are respectively coupled to the side gears. The intermediate output shafts 21 and 3 are coupled to the left and right front wheel axles 23 and 25 to connect the front differential unit 5 and the front wheel axles 23 and 25. The front wheel axles 23 and 25 are interlocked to the left and right front wheels 29 and 31.

  Accordingly, the drive output of the front differential device 5 is transmitted to the left and right front wheels 29 and 31 via the front wheel axles 23 and 25 by the intermediate output shafts 21 and 3, respectively.

  The one intermediate output shaft 3 is disposed through the distribution case 9 of the transfer device 1. In the distribution case 9, a connecting hollow shaft 33 serving as a first transmission shaft, a tilt transmission shaft 35 serving as a solid second transmission shaft disposed at an inclination, and a rear wheel side serving as a third transmission shaft. An output shaft 37 is provided.

  The connecting hollow shaft 33 is provided with a first transmission gear 39 which is a drive gear, and the first transmission gear 39 meshes with a second transmission gear 41 attached to one end side of the inclined transmission shaft 35. Yes. A first cross meshing gear 43 is attached to the other end side of the tilt transmission shaft 35, and the first cross meshing gear 43 meshes with a second cross meshing gear 45 attached to the rear wheel side output shaft 37. ing.

  A propeller shaft 49 is coupled to the rear wheel side output shaft 37 via a universal joint 47. A drive pinion shaft 55 is coupled to the propeller shaft 49 via a universal joint 51 and an on-demand torque transmission coupling 53 for 4WD. The drive pinion gear 57 of the drive pinion shaft 55 meshes with the ring gear 61 of the rear differential device 59.

  The rear differential device 59 is supported by the carrier case 63. Left and right rear wheels 69 and 71 are linked to the rear differential device 59 via left and right rear wheel axles 65 and 67.

  Accordingly, when torque is input from the engine 17 or the engine 17 and the motor generator 19 to the ring gear 15 of the front differential device 5 via the transmission 11, on the other hand, the intermediate output shafts 21 and 3 and the front wheel axle 23 are provided. , 25, torque is transmitted to the left and right front wheels 29, 31. On the other hand, torque is transmitted to the inclined transmission shaft 35 via the connecting hollow shaft 33, the first transmission gear 39, and the second transmission gear 41. Done. Torque is transmitted from the tilt transmission shaft 35 to the rear wheel side output shaft 37 via the first and second cross meshing gears 43 and 45.

  From the rear wheel side output shaft 37, a rear differential is provided via a universal joint 47, a propeller shaft 49, a universal joint 51, a torque transmission coupling 53, a drive pinion shaft 55, and a drive pinion gear 57. Torque is transmitted to the ring gear 61 of the device 59. Torque is transmitted from the rear differential device 59 to the left and right rear wheels 69 and 71 via the left and right rear wheel axles 65 and 67.

By this torque transmission, the vehicle can travel in the on-demand four-wheel drive state by the front and rear wheels 29, 31, 69, 71.
[Transfer device]
FIG. 2 is a plan sectional view of the transfer device, and FIG. 3 is a side view of the transfer device showing the relationship with the engine.

  The distribution case 9 of the transfer device 1 includes a first case portion 73 that rotatably supports the connecting hollow shaft 33 and the tilt transmission shaft 35, and a second case portion 75 that rotatably supports the rear wheel side output shaft 37. It is made up of. The first case portion 73 includes a case main body 77 and a case cover 79.

  The case main body 77 is provided with a mating surface 81, and a plurality of main body side fastening portions 83 are provided as fastening portions including the mating surface 81. The plurality of main body side fastening portions 83 are arranged so as to surround the connecting hollow shaft 33 and the inclined transmission shaft 35. A matching surface 85 and a cover side fastening portion 87 corresponding to the case cover 79 are also formed. The mating surface 85 of the case cover 79 is abutted against the mating surface 81 of the case main body 77 and the fastening portions 83 and 87 are fastened by bolts 89, and the case cover 79 is fixed to the case main body 77.

  The mating surfaces 81 and 85 are formed so as to be orthogonal to the respective axes on the connecting hollow shaft 33 side and the inclined transmission shaft 35 side, and are formed so as to incline in FIG. Yes. The mating surfaces 81b and 85b at the end of the inclined transmission shaft 35 are positioned so as to be offset outward in the axial direction with respect to the mating surfaces 81a and 85a at the end of the connecting hollow shaft 33.

  The first case portion 73 forms first and second accommodating portions 89 and 91, and upper and lower mounting bracket portions 93 for attaching to the bell housing 13 are provided outside the case main body 77. 95 is formed. A case side mounting fastening portion 97 is formed on the mounting bracket portions 93 and 95.

  The case side mounting fastening portion 97 of the mounting bracket portion 93 is disposed at the upper portion so as to straddle the axis of the tilt transmission shaft 35.

  For this reason, the distribution case 9 can be supported by the heavy inclined transmission shaft 35 portion to which the first cross-meshing gear 43 and the second transmission gear 41 having a large diameter are attached, and the inclined transmission shafts are arranged in an inclined manner. The sound vibration can be suppressed by the reliable support of 35.

  In addition, the case side mounting fastening portion 97 of the mounting bracket portion 95 is disposed on the lower side of the axis of the inclined transmission shaft 35.

  For this reason, it is possible to reinforce the support on the side of the inclined transmission shaft 35 which is heavy and inclined, by means of the mounting bracket portion 95, so that the sound vibration can be suppressed.

  The mounting bracket portions 93 and 95 are abutted against the mounting portion of the bell housing 13 on the transmission side, and the case side mounting fastening portion 97 is fastened to the fastening portion of the bell housing 13 on the stationary side with a bolt or the like. Then, the transfer device 19 is attached.

  The first accommodating portion 89 accommodates the connecting hollow shaft 33 and the first transmission gear 39. The second accommodating portion 91 accommodates the inclined transmission shaft 35, the second transmission gear 41, and the first and second cross meshing gears 43 and 45.

  In the first accommodating portion 89, a bearing support portion 99 and a seal support portion 101 are provided on the case body 77 on one side in the axial direction of the first transmission gear 39, and a bearing is provided on the other side in the axial direction of the first transmission gear 39. A support portion 103 and a seal support portion 105 are provided on the case cover 79.

  The coupling hollow shaft 33 is rotatably supported by the bearing support portions 99 and 103 by ball bearings 107 and 109. A gear housing portion 110 is formed in the distribution case 9 between the ball bearings 107 and 109 to house the first transmission gear 39. The cross section of the gear housing part 110 is formed such that the outer wall of the distribution case 9 forms a part of a cylinder, and a part of the plurality of main body side fastening parts 83 is formed on the cylindrical outer wall 9a of the gear housing part 110. Has been placed.

  Oil seals 111a, 111b, and 113 are attached as seals to the inner periphery of the seal support portion 101 and the seal support portion 105 of the first housing portion 89. The oil seals 111a, 111b, and 113 are connected to the connecting hollow shaft 33. It is in close contact with the outer periphery and can slide relative to each other. An O-ring 115 is supported on the outer periphery of one end portion of the first accommodating portion 89 as a seal.

  A spline portion 117 is formed on the outer periphery of one end of the connecting hollow shaft 33, and the spline portion 117 is spline-engaged with a differential case of the front differential device 5. A concave portion 33a in the radial direction is formed on one side of the intermediate portion of the connecting hollow shaft 33, and a first transmission gear 39 is integrally formed on the other side of the intermediate portion. The first transmission gear 39 is, for example, an involute tooth type parallel meshing gear. An oil seal 119 is provided on the inner circumference on the other end side of the connecting hollow shaft 33, and is in close contact with the outer circumference of the intermediate output shaft 3.

  The second accommodating portion 91 has a closed wall 121 on the case body 77 on one end side of the inclined transmission shaft 35, and a closed wall portion 123 on the case cover 79 on the other end side of the inclined transmission shaft 35. . These closed wall portions 121 and 123 are inclined with respect to the axis of the connecting hollow shaft 33. The closed wall portion 121 is coupled to the outer peripheral portion of the seal support portion 101 on the first housing portion 89 side. The closing wall portion 123 is coupled to the outer peripheral portion of the bearing support portion 103 on the first housing portion 89 side.

  A bearing support portion 125 is formed on the closed wall portion 121 in the vicinity of the seal support portion 101, and a bearing support portion 127 protruding inward is formed on the closed wall portion 123.

  Both end sides of the inclined transmission shaft 35 are rotatably supported by the bearing support portions 125 and 127 via taper roller bearings 129 and 131, respectively.

  Therefore, the inclined transmission shaft 35 is disposed side by side with an inclination with respect to the connecting hollow shaft 33.

  A second transmission gear 41 is formed integrally with the inclined transmission shaft 35, and a first cross-meshing gear 43 is spline engaged.

  The second transmission gear 41 is formed of an involute tooth-type taper gear, and meshes with the first transmission gear 39 at an angle. The second transmission gear 41 is formed with a smaller diameter than the first transmission gear 39, and forms a speed increasing gear mechanism from the connecting hollow shaft 33 to the inclined transmission shaft 35.

  The first cross meshing gear 43 is formed of a hypoid gear together with the second cross meshing gear 45, and the crossing angle of the shaft centers of the first and second cross meshing gears 43, 45 is the inclination of the tilt transmission shaft 35. Is smaller than a right angle. The first cross meshing gear 43 is formed with a larger diameter than the second cross meshing gear 45, and constitutes a speed increasing gear mechanism from the tilt transmission shaft 35 to the rear wheel side output shaft 37.

  The inclined transmission shaft 35 is supported by the tapered roller bearing 129 through the boss portion 43 a of the first cross meshing gear 43. In this supported state, the outer periphery of the first cross meshing gear 45 is opposed to the concave portion 33 a of the connecting hollow shaft 33 in the radial direction.

  The second case portion 75 supports the rear wheel side output shaft 37, and one end is fitted and assembled to the opening 133 of the first case portion 73, and is fastened and fixed by a bolt 134. An O-ring 135 is attached to the outer periphery of one end of the second case portion 75 and is in close contact with the inner periphery of the opening 133.

  The second case portion 75 is provided with bearing support portions 137 and 139, and a seal support portion 141 is provided at the outer end portion. The rear wheel side output shaft 37 is rotatably supported by the bearing support portions 137 and 139 via tapered roller bearings 143 and 145. The tapered roller bearing 145 is fastened via a flange member 149 by a nut 147 screwed to the rear wheel side output shaft 37, and a preload is applied to the tapered roller bearings 143 and 145. The flange member 149 is splined to the rear wheel output shaft 37.

  An oil seal 151 is attached to the seal support portion 141, and the oil seal 151 is in close contact with the outer periphery of the flange member 149 and can be slid relative thereto. A dust cover 153 is attached to the flange member 149, and an edge of the dust cover 153 is loosely fitted in a recess 155 formed in the outer edge of the second case portion 75.

[Function and effect]
The transfer device 1 according to the embodiment of the present invention includes a coupling hollow shaft 33 and an inclined transmission shaft 35 that are rotatably supported by the distribution case 9 and that can be interlocked with each other by the first and second transmission gears 39 and 41. A rear-wheel-side output shaft that is rotatably supported by the distribution case 9 and that is linked to the tilt transmission shaft 35 by the first and second cross-meshing gears 43 and 45 to increase the speed of the connection hollow shaft 33 so that output is possible. 37, the second transmission gear 41 is formed by a taper gear, and the first transmission gear 39 is incliningly engaged with each other. It is smaller than a right angle.

  Then, the tilt transmission shaft 35 is disposed side by side with an inclination with respect to the connecting hollow shaft 33, and an inter-axis distance between the first cross-meshing gear 43 and the connecting hollow shaft 33 is ensured.

  For this reason, the distance between the first cross-meshing gear 43 and the connecting hollow shaft 33 can be secured, and the diameter of the first transmission gear 39 of the connecting hollow shaft 33 can be reduced.

  When the diameter of the first transmission gear 39 is reduced, the projecting dimension of the fastening portions 83 and 87 toward the engine 17 can be reduced, and the clearance between the engine 17 and the engine 17 can be easily made as shown in FIG. Can be secured.

  Since the recess 39a is formed in the connecting hollow shaft 39, in combination with the inclined arrangement of the inclined transmission shaft 35, the diameter of the first transmission gear 39 is made smaller and the diameter of the first cross meshing gear 43 is made smaller. The projecting dimension of the fastening portions 83 and 87 to the engine 17 side can be reduced while securing a speed increasing ratio between the connecting hollow shaft 33 and the rear wheel side output shaft 37.

  Since the diameter of the first cross meshing gear 43 can be increased, the strength of the gear 43 can be improved.

  In the description of the first embodiment, the second transmission gear 41 is described as a tapered gear.

  When the second transmission shaft is arranged side by side with an inclination with respect to the first transmission shaft, the first and second transmission gears interlocking with each other are in meshable tooth shape It is necessary to provide each.

  Although Example 1 shows an example of those tooth mold shapes, other examples are also noted.

  As another example, both the first and second transmission gears may be tapered gears. In this case, only the second transmission gear does not form a tooth shape corresponding to the inclination of the second transmission shaft, and the meshing tooth surface is adapted by the tapered shape of the first and second transmission gears. be able to.

  In addition, in order to satisfactorily mesh the first and second transmission gears, the tooth lines of each transmission gear are formed by appropriately selecting from spurs, helicals, etc., and setting the shift amount of the tooth type, The tooth surface can be subjected to tooth contact correction such as crowning.

  In the present invention, “tapered gear” is used as a technical term, but it may also be called “conical gear”.

  Further, in the present invention, the first and second transmission shafts are provided side by side with an inclination with respect to the first transmission shaft, the second transmission shaft is provided, and the first and second transmission shafts are interlocked between the first and second transmission shafts. A pair of screw gears can also be used for the transmission gear.

1 Transfer device (power transmission device)
9 Distribution case (case)
9a Outer wall 33 Connecting hollow shaft (first transmission shaft)
35 Inclined transmission shaft (second transmission shaft)
37 Rear wheel output shaft (third transmission shaft)
39 1st transmission gear 41 2nd transmission gear 83 Case side fastening part (fastening part)
87 Cover side fastening part (fastening part)
110 Gear housing

Claims (4)

First and second transmission shafts that are rotatably supported by the case and are linked to each other and interlocked by the first and second transmission gears;
A third transmission shaft that is rotatably supported by the case and interlocked with the second transmission shaft by the first and second cross-meshing gears to increase the speed with respect to the first transmission shaft and enable output. And
The second transmission shaft is disposed side by side with an inclination with respect to the first transmission shaft,
Securing an inter-axis distance between the first cross-meshing gear and the first transmission shaft;
A power transmission device characterized by that. The power transmission device according to claim 1,
The second transmission gear is a tapered gear.
A power transmission device characterized by that. The power transmission device according to claim 1 or 2,
A recess is formed in the first transmission shaft on the outer periphery of the first cross meshing gear,
A power transmission device characterized by that. The power transmission device according to any one of claims 1 to 3,
Forming a gear accommodating portion for accommodating the first transmission gear in the case;
The gear housing is formed so that the outer wall of the case forms part of a cylinder,
A fastening portion is formed on the outer wall of the case in the gear housing portion.
A power transmission device characterized by that.

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