JP2011047422A - Power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission device capable of stabilizing the support with respect to a differential case and a fixed case in the axial direction by suppressing a size increase. <P>SOLUTION: The power transmission device 1 consists of a casing 3, input gear 5, fixed case 7, differential case 9, a pinion 11, a pair of side gears 13, 15, a differential mechanism 17 made up of the differential case 9, a pinion 11 and a pair of side gears 13, 15, an interrupting part 19 provided between the fixed case 7 and differential case 9 to connect and disconnect the fixed case 7 and differential case 9, and a pair of bearings 21, 23 rotatably supporting the differential case 9 with respect to the fixed case 7. The power transmission case keeps the interrupting part 19 between the fixed case 7 and differential case 9 in a radial direction and between a pair of bearings 21, 23 in an axial direction, and the bearing 21 on one side in the radial direction between the fixed case 7 and differential case 9 in a radial direction and adjacent to the differential case 9 in the axial direction, and positions and supports the fixed case 7 and differential case 9 in an axial direction. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a power transmission device applied to a vehicle.

Conventionally, as a power transmission device having an interrupting mechanism for interrupting a driving force from a driving source such as an engine, an engine as a driving source is arranged on the front wheel side, and a driving force from the driving source is arranged on the front wheel side. Transmitting the driving force from the drive source to the rear differential located on the rear wheel side by transmitting to the front differential and transfer, and connecting / disconnecting the clutch mechanism as the intermittent mechanism located on the rear wheel side via the propeller shaft It has been known. (For example, see Patent Document 1)
In this power transmission device, a clutch mechanism for transmitting a driving force from a driving source is disposed adjacent to the axial direction of the rear differential, and the clutch mechanism and the rear differential are accommodated in a differential carrier. By adopting a structure in which the clutch mechanism and the rear differential are accommodated in the differential carrier in this way, the clutch mechanism and the rear differential that have been handled separately can be handled as one component, and the setting of the clutch mechanism and the rear differential can be easily changed. It can be carried out.

JP 2002-370557 A

  However, in the power transmission device as described above, when the differential case of the rear differential is supported by the differential carrier on both sides in the axial direction, the clutch mechanism and the differential case are disposed adjacent to each other in the axial direction, so the clutch mechanism is disposed. The differential case could not be positioned axially on the side.

  For this reason, it is necessary to arrange the bearing with the clutch mechanism sandwiched in the axial direction, but this increases the length of the device, and as a fixed case to which the ring gear that transmits the driving force to the differential case or the clutch mechanism is fixed. The support of the outer case in the axial direction may become unstable.

  Accordingly, an object of the present invention is to provide a power transmission device capable of stabilizing the support of the differential case and the fixed case in the axial direction while suppressing an increase in length.

  The invention described in claim 1 includes a casing, an input gear that is accommodated in the casing and inputs a driving force, a fixed case in which the input gear is fixed so as to be integrally rotatable, and an inner portion of the fixed case that is accommodated in the casing. A differential case provided on the circumferential side so as to be rotatable relative to the fixed case, a pinion supported by the differential case and capable of rotating, and revolved by rotation of the differential case, and a pair of side gears that mesh with the pinion and can rotate relative to each other. A differential mechanism comprising the differential case, the pinion, and the pair of side gears, an intermittent portion that is provided between the fixed case and the differential case and interrupts power transmission between the fixed case and the differential case; A power transmission device comprising a first pair of bearings for rotatably supporting a differential case with respect to the fixed case The intermittent portion is provided between the radial direction of the fixed case and the differential case and between the axial directions of the pair of bearings, and is a bearing on one axial side of the first pair of bearings. Is arranged between the fixed case and the differential case in the radial direction and adjacent to the differential case in the axial direction, and positions and supports the fixed case and the differential case in the axial direction.

Invention of Claim 2 is the power transmission device of Claim 1, Comprising:
The bearing on one side in the axial direction has an outer race that contacts the fixed case and an inner race that contacts the differential case, and at least one of the outer race and the inner race is fixed in an axial position by a fixing member. It is characterized by being.

  A third aspect of the present invention is the power transmission device according to the second aspect, wherein the other of the outer race and the inner race has its axial position fixed by press-fitting.

  A fourth aspect of the present invention is the power transmission device according to any one of the first to third aspects, wherein a part of the fixed case that contacts the outer race of the bearing on the one axial side and the input gear are provided. Is characterized by being formed of one continuous member.

  The invention according to claim 5 is the power transmission device according to any one of claims 1 to 4, wherein the fixed case includes a first side member in which the input gear is formed, and the intermittent portion. And a bearing on one side in the axial direction is fixed to the inner periphery of the first side member.

  The invention according to claim 6 is the power transmission device according to claim 5, wherein the fixed case has a second side member connected to the cylindrical member, and the differential case is the first pair. It is supported on the inner periphery of the second side member via a bearing on the other side in the axial direction.

  A seventh aspect of the present invention is the power transmission device according to any one of the first to sixth aspects, wherein the bearing on the other axial side of the first pair of bearings is configured such that the differential case is in the radial direction. It is characterized by being supported only by.

  The invention according to claim 8 is the power transmission device according to any one of claims 1 to 7, comprising a second pair of bearings that rotatably support the fixed case with respect to the casing. In addition, at least one of the first pair of bearings is arranged to overlap with any one of the second pair of bearings in the radial direction.

  The invention according to claim 9 is the power transmission device according to claim 6, wherein the casing houses an actuator that operates the intermittent portion, and the actuator includes an electromagnet and a pilot operated by the electromagnet. A clutch, an armature that operates the pilot clutch by energizing the electromagnet, a rotor that transmits a magnetic flux of the electromagnet to form a magnetic path, and a cam mechanism that connects the intermittent portion by connecting the pilot clutch. And the rotor forms the second side member.

  In the power transmission device according to the first aspect, since the intermittent portion is provided between the radial direction of the fixed case and the differential case and between the axial directions of the first pair of bearings, the intermittent portion and the differential case are arranged in the axial direction. The bearings can be arranged close to each other in the axial direction of the differential case without being adjacently arranged and lengthened. In addition, the axial direction of the apparatus can be reduced in size by providing the intermittent portion between the fixed case and the differential case in the radial direction.

  In addition, since the bearing on the one axial side of the first pair of bearings is disposed between the radial direction of the fixed case and the differential case and adjacent to the differential case in the axial direction, the fixed case and the differential case are positioned and supported in the axial direction. The axial positions of the fixed case and the differential case are securely held, and power transmission between the fixed case and the differential case can be stabilized.

  Therefore, by providing the interrupted portion between the fixed case and the differential case in the radial direction, the bearing for positioning and supporting the fixed case and the differential case in the axial direction can be disposed adjacent to the axial direction of the differential case, thereby suppressing an increase in length. Thus, the support of the differential case and the fixed case in the axial direction can be stabilized.

  In the power transmission device according to the second aspect, since at least one of the outer race and the inner race of the bearing on the one side in the axial direction is fixed in the axial direction by the fixing member, the outer race that supports the fixed case and the differential case in the axial direction, The axial position of the inner race is fixed, and the axial position of the fixed case or the differential case can be reliably positioned and stabilized.

  In the power transmission device according to claim 3, since the axial position of the other of the outer race and the inner race is fixed by press-fitting, the axial position of the outer race or the inner race is stably fixed without using a fixing member. be able to.

  In the power transmission device according to the fourth aspect of the present invention, the fixed case and the input gear are separated from each other because the input gear and a part of the fixed case that contacts the outer race of the bearing on the one axial side are continuous. Since there is no connecting part and there is no assembly error between the two members, the bearing on the one side in the axial direction is mainly supported and the driving force input from the input gear can be transmitted to the fixed case without loss. it can.

  In the power transmission device according to the fifth aspect, since the bearing on one axial side is fixed to the inner periphery of the first side member, the maximization of the fixed case can be suppressed, and the differential case is supported by the pair of bearings. Since the span is shortened, the support stability can be improved.

  In the power transmission device according to the sixth aspect, since the bearing on the other axial side of the first pair of bearings is supported on the inner periphery of the second side member, the differential case is stably supported by the small diameter portion. Can do.

  In the power transmission device according to claim 7, since the bearing on the other axial side of the first pair of bearings supports the differential case only in the radial direction, vibration due to relative rotation or power transmission between the differential case and the fixed case, Or even if it is a case where a relative shift | offset | difference arises in an axial direction by the thermal expansion difference of each member, the change is absorbed and stable support is enabled. As this other side bearing, a bearing that supports only the radial direction, such as a needle bearing or a sliding bush, can be applied, and the structure of the bearing on the other side in the axial direction can be simplified.

  In the power transmission device according to the eighth aspect, at least one of the first pair of bearings is disposed so as to overlap in a radial direction with respect to any one of the second pair of bearings. It is possible to suppress the lengthening of the device and stabilize the support.

  In the power transmission device according to the ninth aspect, since the rotor forms the second side member, it is not necessary to provide a special support member for the differential case, and the structure can be prevented from becoming complicated. Therefore, the support structure is simplified, and the support can be stabilized by suppressing the lengthening of the apparatus.

(A) It is the schematic which shows the motive power system of a vehicle when a vehicle is a two-wheel drive state. (B) It is the schematic which shows the motive power system of a vehicle when a vehicle is a four-wheel drive state. (A), (b) It is the schematic which shows the power system of a vehicle when the 2-4 switching mechanism is mounted in the power system of the vehicle of FIG. FIG. 2 is a schematic diagram illustrating a power system different from the power system of the vehicle in FIG. 1, and (a) a power system of the vehicle when the vehicle is in a two-wheel drive state. (B) It is the schematic which shows the motive power system of a vehicle when a vehicle is a four-wheel drive state. It is sectional drawing of the power transmission device which concerns on 1st Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on 2nd Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on 3rd Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on 4th Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on the other example of 4th Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on 5th Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on the other example of 5th Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on 6th Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on the other examples of 6th Embodiment of this invention. It is sectional drawing of the power transmission device which concerns on 7th Embodiment of this invention.

  First, an example of a vehicle power system to which a power transmission device according to an embodiment of the present invention is applied will be described with reference to FIGS. In addition, although it is set as the power system which applied the power transmission device 1 which concerns on 1st Embodiment here, the power transmission device which concerns on other embodiment may be applied similarly to the power transmission device 1 of 1st Embodiment. it can.

  Further, here, the shaft member shown in black represents that the driving force from the driving source is transmitted, and the shaft member shown in the oblique line is rotated by the driving force from the driving source and the left and right wheels. It is assumed that the shaft member indicated by white is stopped.

  As shown in FIG. 1, the power system of a vehicle includes a drive source 1101 such as an engine and an electric motor, a transmission 1103 as a speed change mechanism, and a front differential as a differential mechanism that allows differential of the left and right wheels on the front wheel side. 1105, front axles 1107, 1109, front wheels 1111, 1113, transfer 1115, propeller shaft 1117, and main clutch 19 as an intermittent portion that intermittently controls the driving force transmitted from the front wheel side to the rear wheel side. And a differential mechanism 17 that allows differential between the left and right wheels on the rear wheel side, rear axles 1119 and 1121, rear wheels 1123 and 1125, and the like.

  The driving force of the driving source 1101 is distributed from the transmission 1103 through the front differential 1105 to the front wheels 1107 and 1109 to the front wheels 1111 and 1113 and is transmitted to the transfer 1115 connected to the front differential 1105. The driving force transmitted to the transfer 1115 is converted in direction by the conversion gear set 1127 and transmitted to the main clutch 19 as an intermittent portion via the propeller shaft 1117.

  The driving force transmitted to the main clutch 19 is transmitted to the differential mechanism 17 when the main clutch 19 is connected, and is distributed from the rear axles 1119 and 1121 to the rear wheels 1123 and 1125 to drive the front and rear wheels. It becomes a state. When the connection of the main clutch 19 is released, the vehicle is in a two-wheel drive state of front wheel drive.

  Thus, when the vehicle is in a two-wheel drive state, the propeller shaft 1117 is driven by the driving force from the drive source 1101, and the rear axles 1119 and 1121 are driven by the driven wheels from the road surface of the rear wheels 1123 and 1125. However, since the main clutch 19 is not connected, the driving force from the driving source 1101 is not transmitted to the differential mechanism 17. A vehicle power system that prevents the propeller shaft 1117 from being rotated and improves fuel efficiency has a structure as shown in FIG.

  As shown in FIG. 2, the transfer 1115 is provided with a 2-4 switching mechanism 1129 that interrupts the driving force transmitted between the differential case on the input side of the front differential 1105 and the shaft portion of the transfer 1115. . The 2-4 switching mechanism 1129 is connected to a controller (not shown) that controls driving of the vehicle. The controller is also connected to the main clutch 19 and controls the operation of the main clutch 19. Note that the 2-4 switching mechanism 1129 has a synchronizer ring function, and can perform intermittent operation while relaxing the switching impact even when relative rotation occurs between the rotating members.

  In the power system of this vehicle, when the vehicle is in a four-wheel drive state, the driving force of the drive source 1101 is connected to the 2-4 switching mechanism 1129 and is transmitted from the front differential 1105 to the transfer 1115, and the propeller It is transmitted to the main clutch 19 via the shaft 1117. When the vehicle is in a two-wheel drive state, the driving force of the drive source 1101 is in a disconnected state by the 2-4 switching mechanism 1129 and is not transmitted from the front differential 1105 to the transfer 1115, and thus the propeller shaft 1117 and the propeller shaft 1117. The pinion and the ring gear as a drive gear set that is arranged between the differential mechanism 17 and transmits power is stopped without rotating.

  In the power system of a vehicle having such a 2-4 switching mechanism 1129, when the vehicle is in a two-wheel drive state, the connection of the 2-4 switching mechanism 1129 is released, whereby the propeller shaft 1117 is stopped. The rotational drive loss of the stop member, the meshing resistance of the drive gear set, and the oil agitation resistance can be prevented, and the fuel efficiency of the vehicle can be improved.

  The vehicle power system described above has a structure in which a drive source is arranged on the front wheel side and the front wheel side is driven in the two-wheel drive state. However, the power transmission device of the present invention is driven on the front wheel side as shown in FIG. The present invention can also be applied to a structure in which a source is disposed and the rear wheel side is driven in a two-wheel drive state.

  As shown in FIG. 3, the power system of the vehicle includes a drive source 1201 such as an engine and an electric motor, a transmission 1203 as a speed change mechanism, a transfer 1205, a rear wheel side propeller shaft 1207, and left and right wheels on the rear wheel side. A rear differential 1209, a rear axle 1211, 1213, rear wheels 1215, 1217, and a transmission mechanism 1219, which is provided in the transfer 1205 and transmits the driving force from the driving source 1201 to the front wheels. A front wheel side propeller shaft 1221, a main clutch 19 as an intermittent portion for intermittently controlling the driving force transmitted from the transfer 1205 side to the front wheel side, and a differential mechanism that allows the front wheel side to differentiate between the left and right wheels 17, front axles 1223 and 1225, front wheels 1227 and 1229, and the like.

  The driving force of the driving source 1201 is transmitted from the transmission 1203 to the rear differential 1209 via the rear wheel side propeller shaft 1207, distributed from the rear axles 1211 and 1213 to the rear wheels 1215 and 1217, and to the transmission mechanism 1219 in the transfer 1205. Communicated. The driving force transmitted to the transmission mechanism 1219 is transmitted to the main clutch 19 via the front wheel side propeller shaft 1221.

  The driving force transmitted to the main clutch 19 is transmitted to the differential mechanism 17 when the main clutch 19 is connected, and is distributed to the front wheels 1227 and 1229 from the front axles 1223 and 1225 to be a four-wheel drive state in which the front and rear wheels are driven. become. Further, when the connection of the main clutch 19 is released, the vehicle enters a two-wheel drive state of rear wheel drive.

  Further, the transfer 1205 is provided with a 2-4 switching mechanism 1231 having a synchronization function similar to the switching mechanism 1129 in FIG. 2 in order to intermittently drive the driving force transmitted from the transmission mechanism 1219 to the front wheel side propeller shaft 1221. ing. For this reason, when the vehicle is in the two-wheel drive state of the rear wheel drive, the driving force of the drive source 1201 is transmitted to the front wheel side propeller shaft 1221 from the transmission mechanism 1219 because the 2-4 switching mechanism 1231 is in the disconnected state. Instead, the front wheel side propeller shaft 1221 is stopped. Therefore, when the vehicle is in the two-wheel drive state of the rear wheel drive, the front wheel side propeller shaft 1221 is stopped and the fuel consumption of the vehicle can be improved.

  Hereinafter, a power transmission device applied to such a vehicle power system will be described.

  The power transmission device according to the embodiment of the present invention will be described with reference to FIGS.

(First embodiment)
The first embodiment will be described with reference to FIG.

  The power transmission device 1 according to the present embodiment includes a casing 3, an input gear 5 that is housed in the casing 3 and inputs a driving force, a fixed case 7 that is fixed so that the input gear 5 can rotate integrally, and a casing. 3, a differential case 9 that is provided on the inner peripheral side of the fixed case 7 so as to be rotatable relative to the fixed case 7, a pinion 11 that is supported by the differential case 9 and that can rotate and revolves by the rotation of the differential case 9, A pair of side gears 13 and 15 that mesh with the pinion 11 and can rotate relative to each other, a differential mechanism 17 that includes the differential case 9, the pinion 11 and the pair of side gears 13 and 15, and a fixed case 7 and a differential case 9 are provided. The main clutch 19 as an intermittent portion for intermittently connecting the fixed case 7 and the differential case 9, and the differential case 9 is rotated with respect to the fixed case 7. And a bearing 21, 23 of the first pair of bearings supporting the ability.

  The main clutch 19 is provided between the fixed case 7 and the differential case 9 in the radial direction and between the pair of bearings 21 and 23, and the bearing 21 as a bearing on one side in the axial direction is connected to the fixed case 7. And the differential case 9 are disposed adjacent to each other in the radial direction and in the axial direction to position and support the fixed case 7 and the differential case 9 in the axial direction. More specifically, the bearing 21 is arranged adjacent to each other by being arranged on the side opposite to the side gear 13 with the side wall on one side of the differential case 9 sandwiched in the axial direction.

  The bearing 21 includes an outer race 25 that abuts against the fixed case 7 and an inner race 27 that abuts against the differential case 9. The outer race 25 and the inner race 27 are fixed at axial positions by fixing members 29 and 31. Yes.

  Furthermore, a part of the fixed case 7 (side member 33 described later) and the input gear 5 with which the outer race 25 of the bearing 21 abuts on the inner periphery are formed as one continuous member.

  The fixed case 7 includes a first side member 33 on which the input gear 5 is formed, and a cylindrical member 35 to which the main clutch 19 is connected. The side member 33 and the cylindrical member 35 include a fixed portion 37. The fixed portion 37 is formed on the back side in the axial direction of the gear portion of the input gear 5.

  Further, the bearing 21 is fixed to the inner periphery of the first side member 33.

  The fixed case 7 has a rotor 53 as a second side member connected to the cylindrical member 35, and the differential case 9 is arranged on the inner periphery of the rotor 53 via a bearing 23 as a bearing on the other side in the axial direction. It is supported.

  Further, the bearing 23 is disposed on the inner periphery of a second side member (a rotor 53 described later) which is a part of the fixed case 7 connected to the cylindrical member 35 and supports the differential case 9 only in the radial direction.

  Further, the bearings 49 and 51 are provided as a second pair of bearings that rotatably support the fixed case 7 with respect to the casing 3, and the bearings 23 have a diameter so as to have the same axial range with respect to the bearings 51. It is arranged to overlap (overlap) in the direction.

  As shown in FIG. 4, the casing 3 as a stationary member disposed in the vehicle has an input gear 5, a fixed case 7, a power transmission gear 41, a power transmission shaft 43, and a differential case 9. The moving mechanism 17, the main clutch 19, the actuator 45, the first pair of bearings 21, 23, the second pair of bearings 49, 51, and the like are accommodated.

  The input gear 5 is formed by forming a first side member 33 as one member continuous with the fixed case 7 in the circumferential direction of the outer periphery of the fixed case 7. The input gear 5 meshes with the power transmission gear 41 at the meshing portion 39 to form a bevel gear type gear set, and a driving force is transmitted from the power transmission gear 41 side to the input gear 5 side. In the present embodiment, the power transmission gear 41 and the input gear 5 are a hypoid gear set having a constant height.

  The power transmission gear 41 is formed as one member continuous with the power transmission shaft 43 on one axial end side of the power transmission shaft 43. The power transmission gear 41 meshes with the input gear 5 at the meshing portion 39, and inputs driving force from the power transmission shaft 43 side to the input gear 5.

  The power transmission shaft 43 is rotatably supported by the casing 3 via a unit bearing 47 in which balls parallel in the axial direction are arranged, and the propeller shaft 1117 is connected to a flange member 48 that is connected to the power transmission shaft 43 so as to be integrally rotatable. (See FIGS. 1 and 2) and a front wheel side propeller shaft 1221 (see FIG. 3) are connected so as to be integrally rotatable, and the driving force from the drive sources 1101 and 1201 (see FIGS. 1 to 3) is transmitted. The driving force transmitted to the power transmission shaft 43 is transmitted to the fixed case 7 via the power transmission gear 41 and the input gear 5.

  The fixed case 7 is rotatably supported by the casing 3 via bearings 49 and 51 on the outer periphery of a small-diameter shaft portion formed on each shaft end side of the first side member 33 and the second side member 53. The case 7 includes a side member 33, a cylindrical member 35, and a rotor 53. The input gear 5 is formed as one continuous member at a portion of the bearing 49 that contacts the outer race 25 of the bearing 49 that rotatably supports the fixed case 7 of the side member 33. A cylindrical member 35 is fixed to the side member 33 so as to be integrally rotatable.

  The cylindrical member 35 is formed in a cylindrical shape, and a spline-shaped connecting portion 55 is formed on the inner periphery. The cylindrical member 35 is fixed so that one end side in the axial direction can rotate integrally with the side member 33 by a fixing portion 37 by welding or the like. The fixed portion 37 is formed on the back side in the axial direction of the gear portion of the input gear 5. For example, when it is desired to increase the diameter of the main clutch 19, the fixed portion 37 is positioned on the radially outer side, but the gear portion and the meshing portion 39 of the input gear 5 are positioned on the radially outer side of the fixed portion 37. And the fixing | fixed part 37 cannot be located in a radial direction outer side. On the other hand, by arranging the fixed portion 37 and the back side of the gear portion of the input gear 5 to face each other in the axial direction, there is no restriction in the radial direction of the fixed portion 37 and the gear portion of the input gear 5, and the fixed portion 37. It is possible to give a degree of freedom to the setting of the fixed portion 37 and the gear portion of the input gear 5 such as the change of the arrangement position and the change of the radial size of the meshing portion 39. A rotor 53 is fixed to the other end side in the axial direction of the cylindrical member 35 by a welded portion 57 so as to be integrally rotatable. The configuration of the fixed case 7 is such that the input gear 5 is formed of a small member mainly having a gear portion, and is integrated with a fixing means such as welding on the outer peripheral side of the first side member 33 that contacts the bearing 25. The first side member 33 can be formed integrally with the cylindrical member 35 by forging, pressing, or flow forming. Even in this case, it does not depart from the structural features of the present invention.

  The rotor 53, which is the second side member, is made of a magnetic material in which a nonmagnetic material member is arranged in the middle portion in the radial direction, or a plurality of bridge portions are provided and gaps are provided in the circumferential direction. It abuts on a bearing 51 that is rotatably supported, and is disposed adjacent to the electromagnet 59 in the axial direction. The rotor 53 transmits the magnetic flux of the electromagnet 59 by energization of the electromagnet 59 and forms a magnetic flux loop as a magnetic path together with the pilot clutch 61 and the armature 63.

  A differential case 9 is disposed on the inner peripheral side of the fixed case 7 so as to be rotatable relative to the fixed case 7.

  The differential case 9 is disposed so as to be rotatable relative to the fixed case 7 via bearings 21 and 23 at boss portions 65 and 67. A spline-shaped connecting portion 69 is formed on the outer periphery of the differential case 9. The differential case 9 accommodates a differential mechanism 17, and a driving force input from the input gear 5 via the main clutch 19 is transmitted to the differential mechanism 17 via the differential case 9.

  The differential mechanism 17 includes a differential case 9, and includes a pinion shaft 71, a pinion 11, and a pair of side gears 13 and 15. The pinion shaft 71 is engaged with the differential case 9 at its end and is prevented from coming off by a pin 73, and is rotationally driven integrally with the differential case 9.

  The pinion 11 is supported by the pinion shaft 71 and revolves by the rotation of the differential case 9. In addition, the pinion 11 transmits a driving force to the pair of side gears 13 and 15 and is rotatably supported by the pinion shaft 71 so as to be driven to rotate when a differential rotation occurs between the pair of side gears 13 and 15 engaged with each other. ing. A spherical washer 75 is disposed between the back side of the pinion 11 and the differential case 9 to receive radial movement that occurs when the pinion 11 revolves. The differential mechanism 11 is composed of the above-described constituent members. However, if the differential mechanism 11 is configured to transmit the driving force input to the differential case 9 to the left and right drive shafts while having a differential function, other differential mechanisms are used. Even if they are arranged and configured, they do not particularly affect the gist of the present invention and can be regarded as equivalents.

  The pair of side gears 13 and 15 are supported by the boss case 77 and 79 so as to be relatively rotatable with respect to the differential case 9, and mesh with the pinion 11. In addition, thrust washers 81 and 83 are arranged between the rear sides of the side gears 13 and 15 and the differential case 9 to receive the movement of the side gears 13 and 15 in the axial direction by the meshing reaction force with the pinion 11. Spline-shaped connecting portions 85 and 87 formed on the inner peripheral side of the pair of side gears 13 and 15 are connected to the left and right wheels (see FIGS. 1 to 3) on the front wheel side or the rear wheel side of the vehicle, respectively. The drive shaft (not shown) is connected so as to be integrally rotatable, and transmits drive force to the left and right wheels.

  Between the outer peripheral side of the differential case 9 and the inner peripheral side of the fixed case 7 of the differential mechanism 17, a main clutch 19 that interrupts the driving force between the fixed case 7 and the differential case 9 is provided. .

  The main clutch 19 is provided between the fixed case 7 and the differential case 9 in the radial direction and between the first pair of bearings 21 and 23 and includes a plurality of outer plates and a plurality of inner plates. . The plurality of outer plates are connected to a connecting portion 55 formed on the inner periphery of the cylindrical member 35 so as to be movable in the axial direction and integrally rotatable with the fixed case 7. The plurality of inner plates are alternately arranged in the axial direction with respect to the plurality of outer plates, and are connected to a connecting portion 69 formed on the outer periphery of the differential case 9 so as to be axially movable and integrally rotatable with the differential case 9. An annular ring and a snap ring for positioning the annular ring with respect to the differential case 9 on the axial receiving side are disposed on the axial receiving side of the main clutch 19. By connecting the main clutch 19, the fixed case 7 and the differential case 9 are connected, and the driving force from the driving source is transmitted from the input gear 5 side to the differential mechanism 17 side. The main clutch 19 is a control type friction clutch that is operated by the actuator 45 and is capable of intermediate control of transmission torque with sliding friction.

  The actuator 45 is housed in the casing 3 and includes an electromagnet 59, a pilot clutch 61, an armature 63, and a cam mechanism 89 including the rotor 53 of the fixed case 7.

  The electromagnet 59 includes an electromagnetic coil 91 and a core 93, and supports the rotor 53 via a bearing 51. The core 93 is connected to a controller (not shown) that controls energization, and the electromagnetic coil 91 is energized so as to generate the necessary friction torque in the main clutch 19 under the control of the controller. The core 93 is prevented from rotating with respect to the casing 3, and the electromagnet 59 is prevented from rotating with respect to the casing 3, which is a stationary member, and the outer periphery thereof is fitted and fixed to the inner periphery of the casing 3. And is centered. By energizing the electromagnet 59, the pilot clutch 61 is operated.

  The pilot clutch 61 is axially movable in the axial direction with respect to the outer plates of the cam ring 97 and a plurality of outer plates which are axially movable to the connecting portion 55 of the cylindrical member 35 and are connected to the fixed case 7 so as to be rotatable together. And a plurality of inner plates that are axially movable and coupled to the cam ring 97 so as to be integrally rotatable. The pilot clutch 61 is operated by an armature 63 that is attracted and moved by energizing the electromagnet 59.

  The armature 63 is made of a magnetic material, is movable in the axial direction, and is disposed to face the rotor 53 with the pilot clutch 61 interposed therebetween in the axial direction. When the electromagnet 59 is energized, the armature 63 circulates the magnetic lines of force through the core 93, the rotor 53, the pilot clutch 61, and the armature 63, forms a magnetic flux loop, and is attracted to the electromagnet 59 side to move the pilot clutch 61. Connect. The fastening torque of the pilot clutch 61 is converted into an axial thrust through a cam mechanism 89 including a pressure ring 95 and a cam ring 97, and a predetermined drive torque is transmitted by pressing the main clutch 19.

  The cam mechanism 89 includes a cam ball 99 that is opposed to a pressure ring 95 and a cam ring 97 that are opposed to each other in the circumferential direction. The pressure ring 95 is arranged on the outer periphery of the boss portion 67 of the differential case 9 so as to be movable in the axial direction, and is connected to the connecting portion 69 of the differential case 9 so as to be integrally rotatable with the differential case 9. Further, between the pressure ring 95 and the differential case 9 in the axial direction, a plurality of pressure rings 95 are combined in series and in parallel to urge the main clutch 19 in the disengagement direction so that the spring force and the bending length are predetermined. A set return spring 101 is arranged. The pressure ring 95 is axially moved toward the main clutch 19 against the urging force of the return spring 101 by the thrust force generated by the cam mechanism 89 and presses the main clutch 19.

  The cam ring 97 is disposed on the outer periphery of the boss portion 67 of the differential case 9 so as to be movable in the axial direction, and the inner plate of the pilot clutch 61 is coupled so as to be integrally rotatable. A thrust bearing 105 that receives a thrust reaction force generated by the cam mechanism 89 is disposed between the cam ring 97 and the receiving member 103 whose axial position is fixed to the outer periphery of the boss portion 67 of the differential case 9.

  The cam ball 99 is disposed between the cam surfaces formed on the pressure ring 95 and the cam ring 97. This cam ball 99 causes the pressure ring 95 to move to the main clutch 19 side with a strength corresponding to the friction torque generated in the pilot clutch 61 when a differential rotation occurs between the cam ring 97 and the pressure ring 95 due to the connection of the pilot clutch 61. A cam thrust force is generated for axial movement.

  Thus, the fixed case 7 and the differential case 9 accommodated in the casing 3 are supported by a pair of bearings 21 and 23 so as to be relatively rotatable. Of the pair of bearings 21 and 23, the bearing 21 positioned on the side member 33 side of the fixed case 7 positions and supports the fixed case 7 and the differential case 9 in the axial direction.

  The bearing 21 is disposed between the fixed case 7 and the differential case 9 in the radial direction and adjacent to the differential case 9 in the axial direction, and is interposed between the outer race 25, the inner race 27, and the outer race 25 and the inner race 27. A ball bearing is formed of balls that allow the outer race 25 and the inner race 27 to rotate relative to each other. The outer race 25 is in contact with the inner periphery of the side member 33 of the fixed case 7 to position and support the fixed case 7 in the axial direction. The outer race 25 is restricted from moving in the axial direction by a fixing member 29 such as a snap ring, and the position in the axial direction is fixed. The inner race 27 is in contact with the outer periphery of the boss portion 65 of the differential case 9 to position and support the differential case 9 in the axial direction. The inner race 27 is restricted from moving in the axial direction by a fixing member 31 such as a snap ring, and the position in the axial direction is fixed. By fixing the axial positions of the outer race 25 and the inner race 27 in this way, the fixed case 7 and the differential case 9 are positioned in the axial direction by the bearing 21 that supports the fixed case 7 and the differential case 9 so as to be relatively rotatable. Can be made.

  Of the pair of bearings 21 and 23, the bearing 23 positioned on the rotor 53 side of the fixed case 7 is a needle bearing that supports the fixed case 7 and the differential case 9 only in the radial direction. This is because one of the pair of bearings 21 and 23 is disposed adjacent to the differential case 9 to position and support the fixed case 7 and the differential case 9 in the axial direction, so that the other bearing 23 is fixed to the fixed case 7 and the differential case 9. This is because a bearing such as a needle bearing or a bush can be applied. For this reason, by positioning and supporting the fixed case 7 and the differential case 9 in the axial direction with one of the pair of bearings 21 and 23, the other bearing can be simplified, and the arrangement of each component in the apparatus The support structure can be stabilized while improving the degree of freedom and suppressing the lengthening of the apparatus. The bearing 23 is arranged so as to overlap the bearing 51 in the radial direction, that is, overlap in the radial direction. By arranging the bearings 23 in this way, it is possible to further suppress the apparatus from becoming longer in the axial direction.

  A plurality of sealing means for partitioning the inside and the outside of the casing 3 are arranged in the casing 3 that accommodates such members. Specifically, seals 107 and 109 are disposed between the casing 3 and a drive shaft connected to the pair of side gears 13 and 15. In addition, a seal 111 is disposed on the bearing 47 that supports the power transmission shaft 43, and a dust cover 113 that abuts the lip portion of the seal 111 on the flange member 48 to prevent intrusion of dust or muddy water into the casing 3. Is arranged. By these sealing means, the oil that lubricates and cools the meshing portion and the sliding portion of the gear can be sealed inside the casing 3.

  In the power transmission device 1 configured as described above, when the vehicle is in a four-wheel drive state, the armature 63 is attracted and moved by energization control to the electromagnet 59, the pilot clutch 61 is pressed, and the pilot clutch 61 is controlled. Connected with friction torque. When the pilot clutch 61 is connected, a cam thrust force is generated by the cam mechanism 89, and the pressure ring 95 is pressed and moved to the main clutch 19 side. The main clutch 19 is connected by the movement of the pressure ring 95, and the fixed case 7 and the differential case 9 are connected. Due to the connection between the fixed case 7 and the differential case 9, the driving force is transmitted from the input gear 5 side to the differential mechanism 17 side, so that the vehicle can drive the front and rear wheels so that the necessary driving force can be transmitted to the rear wheel side. 4 wheel drive state.

  Further, when the vehicle is in the two-wheel drive state, the pressure ring 95 is pushed and moved in the disconnection direction of the main clutch 19 by the urging force of the return spring 101 by stopping energization to the electromagnet 59. By the movement of the pressure ring 95, the connection of the main clutch 19 is released, and the connection between the fixed case 7 and the differential case 9 is released. By releasing the connection between the fixed case 7 and the differential case 9, the transmission of the driving force from the input gear 5 side to the differential mechanism 17 side is cut off, and the vehicle enters a two-wheel drive state of front wheel or rear wheel drive.

  In such a power transmission device 1, the main clutch 19 is provided between the radial direction of the fixed case 7 and the differential case 9 and between the axial directions of the pair of bearings 21, 23. The bearings 21 can be arranged close to each other in the axial direction of the differential case 9 without being elongated in the axial direction. In addition, by providing the main clutch 19 between the fixed case 7 and the differential case 9 in the radial direction, the axial direction of the apparatus can be reduced.

  Further, the bearing 21 is disposed between the fixed case 7 and the differential case 9 in the radial direction and adjacent to the differential case 9 in the axial direction, and positions and supports the fixed case 7 and the differential case 9 in the axial direction. The axial transmission position between the fixed case 7 and the differential case 9 can be stabilized.

  Therefore, by providing the main clutch 19 between the fixed case 7 and the differential case 9 in the radial direction, the bearing 21 for positioning and supporting the fixed case 7 and the differential case 9 in the axial direction is disposed adjacent to the axial direction of the differential case 9. Thus, the support of the differential case 9 and the fixed case 7 in the axial direction can be stabilized.

  Further, since the outer race 25 and the inner race 27 of the bearing 21 are axially fixed by the fixing members 29 and 31, the axial positions of the outer race 25 and the inner race 27 that support the fixed case 7 and the differential case 9 in the axial direction. Is fixed, and the axial positions of the fixed case 7 and the differential case 9 can be reliably positioned.

  Furthermore, since a part of the fixed case 7 that contacts the outer race 25 of the bearing 21 and the input gear 5 are formed as one continuous member, the connection when the fixed case 7 and the input gear 5 are provided separately is provided. The driving force input from the input gear 5 can be transmitted to the fixed case 7 without loss. In addition, the number of parts can be reduced.

  Further, since the fixing portion 37 between the side member 33 and the cylindrical member 35 is formed on the axially rear side of the gear portion of the input gear 5, the fixing portion 37 is influenced by the radial size of the gear portion of the input gear 5. Without being received, the meshing part 39 and the fixing part 37 of the gear part can be set independently.

  Further, since the bearing 21 is fixed to the inner periphery of the first side member 33, maximization of the fixed case 7 can be suppressed, and the support span of the differential case 9 by the pair of bearings 21 and 23 is shortened. , Support stability can be improved.

  Furthermore, since the bearing 23 is supported by the inner periphery of the rotor 53, the differential case 9 can be stably supported by the small diameter portion.

  Further, since the bearing 23 supports the differential case 9 only in the radial direction, a bearing that supports only the radial direction such as a needle bearing or a sliding bush can be applied, and the structure on the bearing 23 side can be simplified. it can.

  Furthermore, since the bearing 23 is disposed so as to overlap the bearing 51 in the radial direction, the bearing 23 can be reduced in size in the axial direction, and the length of the apparatus can be suppressed.

(Second Embodiment)
The second embodiment will be described with reference to FIG.

  In the power transmission device 201 according to the present embodiment, the inner race 27 of the bearing 21 is fixed in the axial position by press-fitting. In addition, although the same code | symbol is described to the structure same as 1st Embodiment, description is abbreviate | omitted, but since it is the same structure as 1st Embodiment, a structure and functional description refer to 1st Embodiment. Although omitted, the obtained effects are the same.

  As shown in FIG. 5, the inner race 27 of the bearing 21 is press-fitted into the outer periphery of the boss portion 65 of the differential case 9, and the axial position of the bearing 21 is fixed. The outer race 25 of the bearing 21 is fixed in the axial direction by a fixing member 29. Thus, by fixing one of the outer race 25 and the inner race 27 of the bearing 21 by press-fitting, the number of parts can be reduced without using a fixing member. Note that it is preferable to fix the axial position by fixing one of the outer race 25 and the inner race 27 and fixing the other by press-fitting the other, but the axial position may be fixed by press-fitting both.

  In such a power transmission device 201, the axial position of the inner race 27 is fixed by press fitting, so that the axial position of the inner race 27 can be fixed without using a fixing member, and the number of parts can be reduced. can do.

(Third embodiment)
A third embodiment will be described with reference to FIG.

  In the power transmission device 301 according to the present embodiment, the fixing portion 303 between the first side member 33 and the cylindrical member 35 is disposed so as to overlap (overlap) the engagement portion 39 of the input gear 5 in the radial direction. ing. In addition, although the same code | symbol is described to the structure same as 1st Embodiment, description is abbreviate | omitted, but since it is the same structure as 1st Embodiment, a structure and functional description refer to 1st Embodiment. Although omitted, the obtained effects are the same.

  As shown in FIG. 6, the fixing portion 303 between the side member 33 and the cylindrical member 35 of the fixing case 7 includes a fitting portion 305 and a welding portion 307. The fitting portion 305 is configured by fitting the concave portion 309 provided in the side member 33 and the convex portion 311 provided in the cylindrical member 35 into an uneven shape. The welding part 307 is provided by welding the outer diameter side of the fitting part 305, and is fixing the side member 33 and the cylinder member 35 so that integral rotation is possible.

  Such a fixing portion 303 is disposed so as to overlap the engagement portion 39 of the input gear 5 and the power transmission gear 41 in the radial direction, that is, overlap in the radial direction. By arranging the fixing portion 303 and the meshing portion 39 in this way, it becomes easy to align the axis of the power transmission shaft 43 and the rotation center of the differential mechanism 17 on the same line. For this reason, for example, when the propeller shaft is disposed at the center of the vehicle, the distance from the center of the differential mechanism 17 to the left and right wheels can be made equal on both the left and right sides. In addition, for example, the lengths of the drive shafts connected to the pair of side gears 13 and 15 can be made uniform, so that one type of drive shaft can be connected to either side gear 13 or 15. The number of parts can be reduced.

  In such a power transmission device 301, the fixing portion 303 between the side member 33 and the cylindrical member 35 is disposed so as to overlap the meshing portion 39 of the input gear 5 in the radial direction, so that a driving force is input from the input gear 5. The rotational center of the differential mechanism 17 and the axis of the power transmission shaft 43 that meshes with the input gear 5 can be arranged on the same line. For this reason, the lengths of the drive shafts connected to the pair of side gears 13 and 15 can be made uniform depending on the device mounting layout of the vehicle, and it is not necessary to form the drive shafts having different lengths, thereby reducing the number of parts can do.

(Fourth embodiment)
A fourth embodiment will be described with reference to FIGS.

  In the power transmission device 401 according to the present embodiment, in the fixed case 7, the cylindrical member 35 and the rotor 53 as the second side member are coupled together by a screw fastening portion 403 so as to be integrally rotatable. In addition, although the same code | symbol is attached | subjected to the structure same as other embodiment, description is abbreviate | omitted, but since it is the same structure as other embodiment, a structure and functional description refer to another embodiment. Although omitted, the obtained effects are the same.

  As shown in FIG. 7, a screw-shaped screw fastening portion 403 is formed between the outer periphery of the cylindrical member 35 and the inner periphery of the rotor 53, and the cylindrical member 35 and the rotor 53 are screwed together so as to be integrally rotatable. ing. A nut 405 is screwed to the outer periphery of the cylindrical member 35 at the axial end of the rotor 53, and the cylindrical member 35 and the rotor 53 are more firmly fixed by a double nut function by the screw fastening portion 403 and the nut 405. ing. By fastening the cylinder member 35 and the rotor 53 with screws in this way, the cylinder member 35 can be easily released by releasing the fastening of the nut 405 and the screw fastening portion 403 even after the cylinder member 35 and the rotor 53 are assembled. And the rotor 53 can be disassembled. For this reason, it is possible to easily change the setting of the accommodation member accommodated in the fixed case 7, and it is possible to easily assemble the cylindrical member 35 and the rotor 53 even after the setting change of the accommodation member.

  In such a power transmission device 401, in the fixed case 7, the cylindrical member 35 and the rotor 53 are coupled so as to be integrally rotatable by the screw fastening portion 403, so that the setting of the pilot clutch 61, the cam mechanism 89, and the like is changed. In addition, the cylinder member 35 and the rotor 53 can be easily disassembled and assembled, and the disassembly / assembly performance can be improved.

  In the power transmission device 501 as in the second embodiment, as shown in FIG. 8, the cylindrical member 35 and the rotor 53 can be coupled together by a screw fastening portion 403 so as to be integrally rotatable. Since the position of the inner race 27 of the bearing 21 is fixed by press-fitting, the number of parts can be reduced.

  By the way, conventionally, in a power transmission device having a fixed case integrated with a fixed portion, a welded portion, or the like, an intermittent portion, a differential mechanism, a part of an actuator, and the like are accommodated inside the fixed case.

  However, since the fixed case has an integral structure, it cannot be easily disassembled. For this reason, when you want to change the setting of the storage member housed inside the fixed case, you must forcefully disassemble the fixed case once, change the setting of the storage member, and then reassemble the fixed case by welding or the like. As a result, the disassembly and assembly of the fixed case was reduced.

  Therefore, according to the power transmission device according to the present embodiment, the disassembly and assembling property of the fixed case can be improved.

(Fifth embodiment)
The fifth embodiment will be described with reference to FIGS.

  The power transmission device 601 according to the present embodiment includes a first space 603 in which the input gear 5 between the inside of the casing 3 and the outside of the fixed case 7 is disposed between the fixed case 7 and the differential case 9. First sealing means 605 and 607 for partitioning are provided. Between the differential case 9 and the pair of side gears 13 and 15, and between the pair of side gears 13 and 15, there is a main between the inside of the fixed case 7 and the outside of the differential case 9. Second seal means 611, 613, 615, and 617 are provided to partition the second space 609 and the first space 603 in which the pinion 11 inside the clutch 19 and the differential case 9 and the pair of side gears 13 and 15 are disposed. Yes. In addition, although the same code | symbol is attached | subjected to the structure same as other embodiment, description is abbreviate | omitted, but since it is the same structure as other embodiment, a structure and functional description refer to another embodiment. Although omitted, the obtained effects are the same.

  As shown in FIG. 9, between the outer periphery of the pair of boss portions 65 and 67 of the differential case 9 and the inner periphery of the side member 33 of the fixed case 7 and the inner periphery of the rotor 53, the first sealing means 605 and 607 are respectively provided. An X-ring is arranged. The first sealing means 605 and 607 define a first space 603 in which the input gear 5 is disposed between the inside of the casing 3 and the outside of the fixed case 7. The first space 603 is filled with lubricating oil that lubricates and cools the meshing portion 39 of the input gear 5 and the sliding portion of the fixed case 7.

  Between the inner periphery of the differential case 9 and the outer periphery of the boss portions 77 and 79 of the pair of side gears 13 and 15, X-rings as second seal means 611 and 613 are arranged, respectively, inside the pair of side gears 13 and 15. Is provided with a cap as a second sealing means 615,617. The second seal means 611, 613, 615, 617 includes a main clutch 19 between the inside of the fixed case 7 and the outside of the differential case 9, a pinion 11 inside the differential case 9, and a pair of side gears 13, 15. The second space 609 is partitioned from the first space 603. The second space 609 is filled with lubricating oil for lubricating and cooling the main clutch 19, the meshing portion and the sliding portion of the differential mechanism 17.

  In such a power transmission device 601, the first space 603 in which the input gear 5 is arranged by the first seal means 605, 607 and the second seal means 611, 613, 615, 617, the main clutch 19, and the pinion 11 are paired. Since the second space 609 in which the side gears 13 and 15 are arranged is partitioned, different types of lubricating oil suitable for the respective characteristics can be sealed in the first space 603 and the second space 609. The meshing of the meshing part 39 and the intermittent characteristics of the main clutch 19 can be maintained.

  As shown in FIG. 10, in the power transmission device 701 as in the fourth embodiment, an O-ring as the first sealing means 703 that partitions the first space 603 between the cylindrical member 35 and the rotor 53 is disposed. Has been. In this power transmission device 701, different types of lubricating oils suitable for the respective characteristics can be sealed in the first space 603 and the second space 609, and the disassembly and assembling property of the fixed case 7 can be improved. it can.

(Sixth embodiment)
The sixth embodiment will be described with reference to FIGS. 11 and 12.

  In the power transmission device 801 according to the present embodiment, cone clutches 803 and 805 as differential limiting mechanisms for limiting the differential of the differential mechanism 17 are provided between the differential case 9 and the pair of side gears 13 and 15. It has been. In addition, although the same code | symbol is attached | subjected to the structure same as other embodiment, description is abbreviate | omitted, but since it is the same structure as other embodiment, a structure and functional description refer to another embodiment. Although omitted, the obtained effects are the same.

  As shown in FIG. 11, cone clutches 803 and 805 for limiting the differential of the differential mechanism 17 are provided between the back side of the pair of side gears 13 and 15 and the differential case 9. The cone clutches 803 and 805 are operated when a differential rotation of a predetermined value or more occurs between the pair of side gears 13 and 15, and connect the pair of side gears 13 and 15 and the differential case 9 so as to be integrally rotatable.

  In such a power transmission device 801, the cone clutches 803 and 805 for limiting the differential of the differential mechanism 17 are provided between the differential case 9 and the pair of side gears 13 and 15, so that differential limitation is required. The differential of the differential mechanism 17 can be limited on rough roads, and the running performance of the vehicle on rough roads can be improved.

  Also in the power transmission device 901 as in the fifth embodiment, as shown in FIG. 12, the cone clutches 803 and 805 can be provided between the differential case 9 and the pair of side gears 13 and 15, thereby The running performance on the road can be improved, and the disassembly and assembling property of the fixed case 7 can be improved.

  The cone clutches 803 and 805 are torque-sensitive clutches whose frictional force changes depending on the torque value of the driving force input to the differential case 9. The differential limitation of the differential mechanism 17 in the present embodiment employs another torque sensitive mechanism or a speed sensitive mechanism in which the differential limiting force changes according to the differential rotational speed of the differential mechanism. You can also

(Seventh embodiment)
A seventh embodiment will be described with reference to FIG.

  In the power transmission device 1001 according to the present embodiment, a rotation fixing member 1003 is provided at a portion of the differential case 9 where the main clutch 19 is provided so as to be rotatable integrally with the differential case 9, and between the differential case 9 and the rotation fixing member 1003. Between the second space 609, the main clutch 19 between the third space 1005 in which the pinion 11 inside the differential case 9 and the pair of side gears 13, 15 are arranged, the inside of the fixed case 7, and the outside of the differential case 9. Third sealing means 1009 and 1011 are provided to partition into a fourth space 1007 in which is disposed. In addition, although the same code | symbol is attached | subjected to the structure same as other embodiment, description is abbreviate | omitted, but since it is the same structure as other embodiment, a structure and functional description refer to another embodiment. Although omitted, the obtained effects are the same.

  As shown in FIG. 13, a rotation fixing member 1003 is provided at a portion of the differential case 9 where the main clutch 19 is provided so as to be rotatable integrally with the differential case 9. The rotation fixing member 1003 is fixed to the outer periphery of the differential case 9 so as to be integrally rotatable with the differential case 9 by a fixing means (not shown) such as a bolt. The rotation fixing member 1003 is provided with a connecting portion 69 that is connected to the inner plate of the main clutch 19. Between the rotation fixing member 1003 and the differential case 9, the second space 609 includes a third space 1005 in which the pinion 11 inside the differential case 9 and the pair of side gears 13 and 15 are arranged, the inside of the fixed case 7, and the differential case. 9, O-rings are arranged as third seal means 1009 and 1011 that divide into a fourth space 1007 in which the main clutch 19 between them is arranged. The third space 1005 is filled with lubricating oil that lubricates and cools the meshing portion between the pinion 11 and the pair of side gears 13 and 15, the sliding portion inside the differential case 9, and the like. The fourth space 1007 is filled with lubricating oil that lubricates and cools the sliding portions and the like inside the main clutch 19 and the fixed case 7 and outside the differential case 9.

  In such a power transmission device 1001, the second space 609 in which the main clutch 19 and the pinion 11 and the pair of side gears 13 and 15 are arranged by the rotation fixing member 1003 and the third seal means 1009 and 1011 is formed into the pinion 11 and the pair of pairs. Since it is partitioned into a third space 1005 in which the side gears 13 and 15 are arranged and a fourth space 1007 in which the main clutch 19 is arranged, the lubricating oil in which the pieces of the members generated at the meshing portion are mixed is the main clutch. Therefore, the intermittent characteristics of the main clutch 19 can be maintained reliably.

  By the way, conventionally, in a power transmission device in which an input gear and an intermittent portion are accommodated in a casing, lubricating oil for lubricating and cooling the meshing portion and the intermittent portion of the input gear is enclosed in the casing.

  However, since the lubricating oil sealed in the casing is one type of lubricating oil dedicated to the input gear and is not dedicated to the intermittent portion, the intermittent portion is incompatible with the lubricating oil dedicated to the input gear, and the intermittent portion is intermittently connected. The characteristics could be degraded.

  Therefore, according to the power transmission devices according to the fifth to seventh embodiments, a plurality of types of lubricating oil can be sealed in the casing, and the intermittent characteristics of the intermittent portion can be stabilized.

  The power transmission device according to the embodiment of the present invention is applied to a power system in which a drive source is disposed on the front wheel side and the front wheel side or the rear wheel side is driven in the two-wheel drive state. Alternatively, the present invention can be applied to a power system in which a drive source is disposed on the rear wheel side and the front wheel side or the rear wheel side is driven in a two-wheel drive state.

1, 201, 301, 401, 501, 601, 701, 801, 901, 1001 ... Power transmission device 3 ... Casing 5 ... Input gear 7 ... Fixed case 9 ... Differential case 11 ... Pinion 13, 15 ... Side gear 17 ... Differential mechanism 19 ... Main clutch (intermittent part)
21, 23 ... Bearings (first pair of bearings)
25 ... Outer race 27 ... Inner race 29, 31 ... Fixed member 33 ... First side member 35 ... Cylindrical member 37, 303 ... Fixed portion 39 ... Engagement portion 49, 51 ... Bearings (second pair of bearings)
45 ... Actuator 53 ... Rotor (second side member)
DESCRIPTION OF SYMBOLS 59 ... Electromagnet 61 ... Pilot clutch 63 ... Armature 89 ... Cam mechanism 403 ... Screw fastening part 603 ... First space 605, 607, 703 ... First seal means 609 ... Second space 611, 613, 615, 617 ... Second seal Means 1003 ... Rotation fixing member 1005 ... Third space 1007 ... Fourth space 1009, 1011 ... Third sealing means

Claims (9)

A casing, an input gear accommodated in the casing for inputting driving force, a fixed case in which the input gear is fixed to be integrally rotatable, and relative to the fixed case on the inner peripheral side of the fixed case. A differential case provided rotatably, a pinion supported by the differential case and capable of rotating, and revolved by rotation of the differential case; a pair of side gears meshed with the pinion and relatively rotatable; the differential case and the pinion; A differential mechanism comprising the pair of side gears, an intermittent portion provided between the fixed case and the differential case for interrupting power transmission between the fixed case and the differential case, and the differential case with respect to the fixed case A power transmission device comprising a first pair of bearings that are rotatably supported,
The intermittent portion is provided between a radial direction of the fixed case and the differential case and between an axial direction of the pair of bearings, and a bearing on one axial side of the first pair of bearings is the fixed A power transmission device, wherein the power transmission device is disposed between a radial direction of the case and the differential case and adjacent to the differential case in the axial direction, and positions and supports the fixed case and the differential case in the axial direction. The power transmission device according to claim 1,
The bearing on one side in the axial direction has an outer race that contacts the fixed case and an inner race that contacts the differential case, and at least one of the outer race and the inner race is fixed in an axial position by a fixing member. Power transmission device characterized by being made. The power transmission device according to claim 2,
The other of the outer race and the inner race has an axial position fixed by press-fitting. The power transmission device according to any one of claims 1 to 3,
A part of the fixed case that contacts the outer race of the bearing on one side in the axial direction and the input gear are formed by a single continuous member. The power transmission device according to any one of claims 1 to 4,
The fixed case includes a first side member in which the input gear is formed and a cylindrical member to which the intermittent portion is connected, and the bearing on one side in the axial direction is an inner periphery of the first side member. A power transmission device characterized by being fixed to the motor. The power transmission device according to claim 5,
The fixed case includes a second side member connected to the cylindrical member, and the differential case includes the second side member via a bearing on the other axial side of the first pair of bearings. A power transmission device that is supported on an inner periphery. The power transmission device according to any one of claims 1 to 6,
Of the pair of bearings, a bearing on the other axial side supports the differential case only in a radial direction. The power transmission device according to any one of claims 1 to 7,
A second pair of bearings rotatably supporting the fixed case with respect to the casing, wherein at least one of the pair of bearings overlaps one of the second pair of bearings in a radial direction; Power transmission device characterized by being arranged. The power transmission device according to claim 6,
The casing houses an actuator that operates the intermittent portion. The actuator includes an electromagnet, a pilot clutch that is operated by the electromagnet, an armature that operates the pilot clutch by energizing the electromagnet, and the electromagnet. And a cam mechanism that connects the intermittent portion by connecting the pilot clutch, and the rotor forms the second side member. Power transmission device.

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