JP2016156389A - Final speed reduction device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a final speed reduction device capable of improving lubricity without complicating the structure of a casing.SOLUTION: A final speed reduction device 1 comprises: a casing 3 in which a lubricant is accommodated; a final reduction gear 7 provided in an integrally rotatable manner in a rotary member 5 which is accommodated in the casing 3 and disposed in a rotatable manner; and a bearing 9 that is disposed at a back side of the final reduction gear 7 and supports the rotary member 5 in a rotatable manner. The casing 3 includes a first case portion 13 and a second case portion that are separated in a mating surface 11 where both the final reduction gear 7 and the bearing 9 are exposed outside. On the mating surface 11 of the first case portion 13 and the second case portion, an oil passage 17 is provided of which one end is opened towards an outer peripheral side of the final reduction gear 7 and the other end is opened towards the side of the bearing 9.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a final reduction gear applied to a vehicle.

  Conventionally, as a final reduction gear, a casing in which lubricating oil is accommodated, a final reduction gear that is rotatably provided integrally with a rotating member that is accommodated in the casing and is rotatably arranged, There is known one provided with a bearing that is disposed on the back side and rotatably supports a rotating member (see, for example, Patent Document 1).

  In this final reduction gear, in order to promote the supply of lubricating oil to the bearing disposed on the back side of the final reduction gear, one end of the casing is opened toward the outer peripheral side of the final reduction gear, and the other end is a bearing. An oil passage opened toward the side is provided.

  By providing the oil passage in the casing in this manner, the lubricating oil scraped up by the final reduction gear flows into the opening on one end side of the oil passage and flows through the oil passage, and from the opening on the other end side toward the bearing. Lubricating oil is supplied.

US Patent Application Publication No. 2012/0031727

  However, in the final reduction gear device as in Patent Document 1, an oil passage is provided in the casing. However, this oil passage must be processed many times by a processing member such as a drill from all directions with respect to the casing. It could not be provided, and the structure of the casing was complicated.

  Accordingly, an object of the present invention is to provide a final reduction gear that can improve lubricity without complicating the structure of the casing.

  The present invention includes a casing in which lubricating oil is housed, a final reduction gear that is rotatably provided integrally with a rotating member that is housed in the casing and rotatably disposed, and is disposed on the back side of the final reduction gear. A final reduction device comprising a bearing rotatably supporting the rotating member, wherein the casing is divided by a mating surface where the final reduction gear and the bearing are exposed to the outside. And at least one of the first case portion and the second case portion, one end is opened toward the outer peripheral side of the final reduction gear, An oil passage having the other end opened toward the bearing side is provided.

  In this power transmission device, at one end of the first case portion and the second case portion, one end is opened toward the outer peripheral side of the final reduction gear, and the other end is directed toward the bearing side. Since the opened oil passage is provided, the processing of the oil passage with respect to the casing can be simplified, and the structure of the casing is not complicated.

  Therefore, in such a final reduction gear, since the oil passage is provided on the mating surface of the casing, the processing of the oil passage can be simplified, and the lubricity can be improved without complicating the structure of the casing. it can.

  According to the present invention, there is an effect that it is possible to provide a final reduction gear that can improve lubricity without complicating the structure of the casing.

It is sectional drawing of the final reduction gear apparatus which concerns on embodiment of this invention. It is sectional drawing of the final reduction gear apparatus which concerns on embodiment of this invention. It is an enlarged view of the oil path of the final reduction gear device which concerns on embodiment of this invention. It is an enlarged view of the oil path of the other examples of the final reduction gear apparatus which concerns on embodiment of this invention.

  The final reduction gear device according to the embodiment of the present invention will be described with reference to FIGS.

  The final reduction gear device 1 according to the present embodiment is provided so as to be integrally rotatable in a casing 3 in which lubricating oil is housed and a differential case 5 as a rotating member housed in the casing 3 and rotatably disposed. A ring gear 7 as a final reduction gear and a bearing 9 disposed on the back side of the ring gear 7 and rotatably supporting the differential case 5 are provided.

  Moreover, the casing 3 has the 1st case part 13 and the 2nd case part 15 which were divided | segmented by the mating surface 11 to which both the ring gear 7 and the bearing 9 are exposed outside.

  An oil passage 17 having one end opened toward the outer peripheral side of the ring gear 7 and the other end opened toward the bearing 9 is formed on the mating surface 11 of the first case portion 13 and the second case portion 15. Is provided.

  Further, the opening 19 on one end side is enlarged from the inside of the oil passage 17 toward the ring gear 7 side.

  Further, a control mechanism 23 for controlling the power transmitted from the differential case 5 to the output side is disposed between the ring gear 7 and the bearing 9 in the axial direction, and the oil passage 17 is disposed on the outer peripheral side of the control mechanism 23. Yes.

  As shown in FIGS. 1 to 3, the final reduction gear 1 includes a casing 3, a differential case 5, a gear set 25, an input shaft 27, a differential mechanism 29 including the differential case 5, a control mechanism 23, and the like. Has been.

  The casing 3 includes a first case portion 13 having an accommodation space in which mainly the differential mechanism 29 and the control mechanism 23 are accommodated, and an accommodation space in which the gear set 25 and the input shaft 27 are mainly accommodated. And a second case portion 15 having

  The casing 3 has a mating surface 11 which is a plane in which the ring gear 7 and the bearing 9 are both exposed to the outside in a state where the ring gear 7 and the bearing 9 are accommodated in the first case portion 13 or the second case portion 15. The first case portion 13 and the second case portion 15 are combined and fixed by a fixing means such as a bolt.

  Here, the mating surface 11 of the first case portion 13 and the second case portion 15 is formed by a plane including the rotational axis of the differential mechanism 29, but is not limited thereto, and the first case portion 13 is not limited thereto. Alternatively, if the ring gear 7 and the bearing 9 are both exposed to the outside in a state where the ring gear 7 and the bearing 9 are accommodated in the second case portion 15, the first case portion 13 and the second case portion 15 The mating surface 11 may be set anywhere.

  Such a casing 3 accommodates a differential case 5, a gear set 25, an input shaft 27, a differential mechanism 29 including the differential case 5, a control mechanism 23, and the like.

  The differential case 5 is rotatably supported on the casing 3 via bearings 9 and 35 by boss portions 31 and 33 formed on both sides in the axial direction. The differential case 5 is formed with a flange portion in which the ring gear 7 is fixed by a bolt, and the ring gear 7 meshes with a drive pinion 37 that transmits a driving force, and the ring gear 7 and the drive pinion 37 constitute a gear set 25. ing.

  The gear set 25 is configured to be driven by a bevel gear set including a large-diameter ring gear 7 and a small-diameter drive pinion 37. For example, a driving force transmitted from a drive source such as an engine or an electric motor is transmitted. Change direction.

  The small-diameter drive pinion 37 constituting the gear set 25 is formed as one member continuous to the input shaft 27 on one end side in the axial direction of the input shaft 27, and changes the direction of the driving force input from the input shaft 27 to the differential case. 5

  The input shaft 27 is disposed in a direction orthogonal to the rotational axis of the differential case 5 and is rotatably supported by the casing 3 via two bearings 39 and 41 disposed in the axial direction. A spline-shaped connecting portion 43 is formed on the outer periphery of the other end side of the input shaft 27, and a connecting member 45 is connected so as to be integrally rotatable.

  One end side of the connecting member 45 is connected to the input shaft 27 through the connecting portion 43 so as to be integrally rotatable, and an input side member such as a propeller shaft that transmits driving force from the driving source side is integrated with the other end side. It is connected rotatably.

  A seal member 47 that divides the inside and the outside of the casing 3 is disposed between the connecting member 45 and the casing 3 in the radial direction, and a dust cover 49 that protects the seal member 47 on the outer periphery of the connecting member 45. Is arranged.

  The driving force transmitted to the input shaft 27 via the connecting member 45 is transmitted to the differential case 5 via the gear set 25 to form a differential mechanism 29 together with the differential case 5, and the pinion shaft 51 accommodated in the differential case 5. Is transmitted to the pinion 53 and the pair of side gears 55 and 57.

  The pinion shaft 51 is composed of one long pinion shaft and two short pinion shafts, and the inner end of the short pinion shaft is engaged with a hole provided in the middle of the long pinion shaft, The outer end portion of the pinion shaft is engaged with the differential case 5 and is prevented from being detached and prevented from rotating by a pin, and is rotated and driven integrally with the differential case 5. A pinion 53 is supported on the pinion shaft 51.

  The pinion 53 is a four-pinion type in which four are arranged at equal intervals in the circumferential direction of the differential case 5 and is supported on both ends of the long pinion shaft and the outer ends of the two short pinion shafts, respectively. Revolves with 5 rotations. A spherical washer 59 is disposed between the back side of the pinion 53 and the differential case 5 to receive radial movement that occurs when the pinion 53 revolves.

  The pinion 53 is rotatably supported by the pinion shaft 51 so as to transmit a driving force to the pair of side gears 55 and 57 and to rotate when a differential rotation occurs between the pair of side gears 55 and 57 engaged with each other. Yes.

  The pair of side gears 55 and 57 is supported by the boss portions 61 and 63 so as to be rotatable relative to the differential case 5, and meshes with the pinion 53. Further, between the side gears 55 and 57 and the differential case 5 in the axial direction, thrust washers 65 and 67 that receive the movement of the side gears 55 and 57 in the axial direction by the meshing reaction force with the pinion 53 are arranged.

  The pair of side gears 55 and 57 are provided with spline-shaped connecting portions 69 and 71 on the inner peripheral side, and for example, an output side member such as a drive shaft connected to the left and right wheels can rotate integrally with the side gears 55 and 57. The driving force input to the differential case 5 from the input side member is output to the output side member.

  Seal members 73 and 75 that partition the inside and the outside of the casing 3 are arranged between the drive shaft connected to the pair of side gears 55 and 57 and the casing 3 in the radial direction.

  Such differential of the differential mechanism 29 can be controlled by the intermittent state of the intermittent portion 77 of the control mechanism 23 provided between the differential case 5 and the side gear 55. The power transmitted to the output side member via 57 is controlled by the control mechanism 23.

  The control mechanism 23 is disposed between the back side of the ring gear 7 and the bearing 9 that rotatably supports the differential case 5, and includes an intermittent portion 77 and an actuator 79.

  The intermittent portion 77 is provided between the inner periphery of the differential case 5 and the outer periphery of the boss portion 61 of the side gear 55, and includes a plurality of outer clutch plates and a plurality of inner clutch plates.

  The plurality of outer clutch plates of the intermittent portion 77 are engaged with an engaging portion formed on the inner periphery of the differential case 5 so as to be axially movable and integrally rotatable with the differential case 5. The plurality of inner clutch plates are alternately arranged in the axial direction with respect to the plurality of outer clutch plates, can be moved in the axial direction to the engaging portion formed on the outer periphery of the boss portion 61 of the side gear 55, and can rotate integrally with the side gear 55. Is engaged.

  Such an intermittent portion 77 is a multi-plate clutch as a friction clutch including a plurality of control-type clutch plates capable of intermediate control of transmission torque with sliding friction. The intermittent portion 77 is intermittently operated by the actuator 79 so that the differential between the differential case 5 and the side gear 55 can be controlled.

  The actuator 79 includes a moving member 81, a pressing member 83, an activation member 85, and a conversion mechanism 87.

  The moving member 81 is formed in an annular shape, and has a protrusion protruding toward the differential case 5 in the circumferential direction, and the protrusion is inserted into a hole provided in a wall portion facing the axial direction of the differential case 5. By doing so, it is arranged so that it can move in the axial direction and can rotate integrally with the differential case 5.

  An urging member 89 that urges the moving member 81 in the disconnecting direction of the intermittent portion 77 is disposed between the moving member 81 and the wall portion of the differential case 5. The moving member 81 moves the pressing member 83 in the axial direction via a protrusion inserted into the differential case 5.

  The pressing member 83 is formed in an annular shape, is provided integrally with the protrusion of the moving member 81, and is accommodated in the differential case 5 so as to be movable in the axial direction, and is disposed adjacent to the plurality of clutch plates of the intermittent portion 77 in the axial direction. ing.

  The pressing member 83 moves the plurality of clutch plates of the intermittent portion 77 by moving the moving member 81 in the connecting direction of the intermittent portion 77 against the biasing force of the biasing member 89 by the operation of the starting member 85. The intermittent part 77 is connected by pressing.

  The starting member 85 is formed in an annular shape, and is arranged on the outer periphery of the cam ring 91 of the conversion mechanism 87 so as to be axially movable and rotatable relative to the cam ring 91. A thrust bearing that allows relative rotation between the starting member 85 and the moving member 81 and that transmits the axial movement of the starting member 85 to the moving member 81 is provided between the starting member 85 and the moving member 81 in the axial direction. Has been placed.

  A gear portion that meshes with a motor shaft of an electric motor (not shown) is formed on the outer diameter side of the activation member 85, and the activation member 85 is rotated by the operation of the electric motor. The rotation of the activation member 85 is converted into an axial operation force by the conversion mechanism 87.

  The conversion mechanism 87 is a ball cam mechanism, and is composed of a cam ball interposed between these cam surfaces, with a plurality of cam surfaces formed in the circumferential direction facing the activation member 85 and the cam ring 91.

  The cam ring 91 is disposed on the outer periphery of the boss portion 31 of the differential case 5 so as to be rotatable relative to the differential case 5 via a needle bearing. In addition, a regulating member 93 fixed to the outer periphery of the boss portion 31 of the differential case 5 via a thrust bearing is disposed adjacent to one side in the axial direction of the cam ring 91, and one side in the axial direction of the cam ring 91 due to thrust reaction force. Movement to is restricted.

  A plurality of cam surfaces formed in the circumferential direction are formed on the opposing surfaces of the cam ring 91 and the activation member 85 in the axial direction, cam balls are interposed between these cam surfaces, and the rotation of the activation member 85 Due to the differential rotation between the cam ring 91 and the cam ring 91, a cam thrust force is generated that causes the pressing member 83 to be axially pressed and moved toward the intermittent portion 77 via the moving member 81.

  In the final reduction gear 1 configured as described above, the activation member 85 is rotated by the operation of the electric motor, and this rotation is transmitted to the conversion mechanism 87. The rotation transmitted to the conversion mechanism 87 is converted into an axial operation force, and the moving member 81 is moved toward the intermittent portion 77 against the urging force of the urging member 89.

  By the movement of the moving member 81 in the axial direction, the pressing member 83 is moved in the axial direction in the connecting direction of the intermittent portion 77, and the pressing member 83 presses the plurality of clutch plates of the intermittent portion 77, so that the differential case 5 and the side gear 55 An intermittence portion 77 is connected so as to transmit the power controlled between them.

  By the connection of the intermittent portion 77, the differential in the differential mechanism 29 is controlled, and the driving force from the input side member is transmitted to the output side member via the differential mechanism 29 in which the intermittent state of the intermittent portion 77 is controlled. Is output.

  On the other hand, the connecting portion 77 is connected by rotating the electric motor in the reverse direction so that the moving member 81 is axially moved by the biasing member 89 in the disconnecting direction of the connecting portion 77, and the pressing member 83 is moved by the movement of the moving member 81. Are moved together and released.

  The connection between the differential case 5 and the side gear 55 is released by releasing the connection of the intermittent portion 77, the differential restriction in the differential mechanism 29 is released, and the driving force from the input side member is released from the differential restriction. It is output to the output side member via the differential mechanism 29.

  In such a final reduction gear 1, the casing 3 contains lubricating oil therein. The lubricating oil circulates in the casing 3 by the rotation of the gear set 25, and lubricates and cools the sliding portion inside the casing 3, the meshing portion of the gear, and the like.

  However, the lubricating oil that is scraped up by the rotation of the ring gear 7 constituting the gear set 25 is less supplied to the back side of the ring gear 7 and the bearing 9 that rotatably supports the differential case 5 located on the back side of the ring gear 7. There was a risk of lack of lubrication.

  Therefore, the casing 3 is provided with an oil passage 17 having one end opened toward the outer periphery of the ring gear 7 and the other end opened toward the bearing 9.

  The oil passages 17 are respectively provided on the mating surfaces 11 of the first case portion 13 and the second case portion 15, and a portion located on the outer peripheral side of the control mechanism 23 from the back side of the ring gear 7 to the bearing 9 side is lubricating oil. An opening 19 that opens toward the outer peripheral side of the ring gear 7 is provided at one end of the flow path, and an opening 21 that opens toward the bearing 9 is provided at the other end. .

  In this oil passage 17, the lubricating oil scraped up by the rotation of the ring gear 7 flows in from the opening 19, the lubricating oil flows out from the opening 21 through the flow passage, and the sliding portion on the bearing 9 side is lubricated by the lubricating oil.・ Cooled.

  By providing the oil passage 17 in the casing 3 in this way, the lubricating oil can be sufficiently supplied to the bearing 9 side, the lack of lubrication on the bearing 9 side can be eliminated, and the lubricity in the casing 3 can be improved. it can.

  By providing such an oil passage 17 on the mating surface 11 of the first case portion 13 and the second case portion 15, the oil for the casing 3 is not involved in the operation of using a machining member such as a drill a plurality of times. The passage 17 can be easily formed, and the structure of the casing 3 is not complicated.

  The opening 19 on the ring gear 7 side of the oil passage 17 is provided with a receiving portion 95 that is inclined so as to expand from the inside of the oil passage 17 toward the ring gear 7 side.

  Thus, by providing the receiving portion 95 in the opening 19 on the ring gear 7 side, the lubricating oil that is scraped up and diffused by the rotation of the ring gear 7 can be reliably received by the receiving portion 95, and the lubricating oil can be received in the oil passage 17. It is possible to flow in stably.

  On the other hand, the opening 21 on the bearing 9 side of the oil passage 17 opens toward the axial direction between the bearing 9 and the seal member 73 disposed between the drive shaft connected to the side gear 55 and the casing 3 in the radial direction. Has been.

  In this way, by opening the opening 21 on the bearing 9 side in the axial direction between the bearing 9 and the seal member 73, the lubricating oil flowing out from the oil passage 17 is not only on the bearing 9 but also on the drive shaft side. It is supplied and the lubricity can be further improved.

  In addition, although the oil path 17 is each provided in the mating surface 11 of the 1st case part 13 and the 2nd case part 15, as shown in FIG. 4, for example, the mating surface 11 ( Alternatively, the oil passage 17 may be provided only on the mating surface 11) of the second case portion 15.

  In such a case, it is only necessary to provide the oil passage 17 only in the first case portion 13 or the second case portion 15, so that the structure of the casing 3 can be further simplified.

  In such a final reduction gear 1, one end is opened toward the outer peripheral side of the ring gear 7 and the other end is opened toward the bearing 9 on the mating surface 11 of the first case portion 13 and the second case portion 15. Since the oil passage 17 is provided, the processing of the oil passage 17 with respect to the casing 3 can be simplified, and the structure of the casing 3 is not complicated.

  Therefore, in such a final reduction gear 1, since the oil passage is provided in the mating surface 11 of the casing 3, the processing of the oil passage 17 can be simplified, and the lubricity can be improved without complicating the structure of the casing 3. Can be improved.

  Further, since the opening 19 on one end side of the oil passage 17 is enlarged from the inside of the oil passage 17 toward the ring gear 7 side, the lubricating oil scraped up by the ring gear 7 can be reliably received, and the bearing 9 side The lubricating oil can be supplied stably.

  Further, since the oil passage 17 is disposed on the outer peripheral side of the control mechanism 23 disposed between the ring gear 7 and the bearing 9 in the axial direction, the oil passage 17 can be provided without affecting the control mechanism 23. In addition, even when the bearing 9 is far from the ring gear 7, the lubricating oil can be supplied to the bearing 9 side via the oil passage 17.

  In the final reduction gear device according to the embodiment of the present invention, the differential mechanism having a differential case in which the final reduction gear is provided so as to be integrally rotatable is accommodated in the casing. The configuration of the present invention can be applied even when a power transmission mechanism having a shaft-like member provided so as to be integrally rotatable is accommodated in the casing.

  The control mechanism is a mechanism for controlling the differential of the differential mechanism. However, the control mechanism is not limited to this, and a control mechanism having a differential lock function for locking the differential of the differential mechanism is provided on the output shaft. The control mechanism may be any mechanism as long as it is a mechanism that controls the power transmitted from the rotating member to the output side, such as an axle disconnect that interrupts the power transmitted to the side.

  Further, the casing may be divided not only into the first case portion and the second case portion but also into a plurality of case portions, and the final reduction gear and the bearing of both the case portions are exposed to the outside. What is necessary is just to provide an oil path in the mating surface of the case part which has a surface.

DESCRIPTION OF SYMBOLS 1 ... Final reduction gear 3 ... Casing 5 ... Differential case 7 ... Ring gear 9 ... Bearing 11 ... Matching surface 13 ... 1st case part 15 ... 2nd case part 17 ... Oil path 19 ... Opening of one end side 23 ... Control mechanism

Claims (3)

A casing in which lubricating oil is accommodated, a final reduction gear provided to be rotatable integrally with a rotary member accommodated in the casing and rotatably arranged, and the rotary member arranged on the back side of the final reduction gear A final reduction device comprising a bearing that rotatably supports
The casing includes a first case portion and a second case portion which are divided by a mating surface where the final reduction gear and the bearing are exposed to the outside,
At least one of the first case portion and the second case portion has one end opened toward the outer peripheral side of the final reduction gear, and the other end opened toward the bearing side. A final reduction gear, characterized in that an oil passage is provided. The final reduction gear according to claim 1,
The opening on the one end side is enlarged from the inside of the oil passage toward the final reduction gear side. The final reduction gear according to claim 1 or 2,
Between the axial direction of the final reduction gear and the bearing, a control mechanism for controlling the power transmitted from the rotating member to the output side is disposed,
The said oil path is arrange | positioned at the outer peripheral side of the said control mechanism, The final reduction gear apparatus characterized by the above-mentioned.

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