JP2005098385A - Differential device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To make it possible to support an energization means, or fasten a differential case by commonly using a pin member for engagement of pressure plates and friction members instead of using dedicated parts or work. <P>SOLUTION: This differential device is provided with a differential case 3, side gears 5 and 7, and a pinion gear 9. It is also provided with friction plate assemblies 45 and 47 to be engaged with the differential case 3 and the side gears 5 and 7 to limit differential rotation of the side gears 5 and 7 in accordance with fastening force, and pressure plates 49 and 51 engaged with the differential case 3 to move in accordance with torque for providing fastening force to the friction plate assemblies 45 and 47. On the outer circumferential side in the differential case, a bolt 31 is provided in contact along a rotation axial center direction. The bolt 31 is engaged with the friction plate assemblies 45 and 47 and the pressure plates 49 and 51 to be engaged with the differential case 3. The bolt 31 is thus commonly used for fastening the differential case 3 and supporting a coil spring 65. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a differential device used for an automobile or the like.

  As a conventional differential device, for example, there is a device as shown in FIG. FIG. 7 is a cross-sectional view of the differential device.

  A differential device 201 in FIG. 7 represents a torque-sensitive LSD (torque-sensitive limit slip differential device).

  The differential device 201 includes a differential case 203. The differential case 203 has a flange portion 205 for fastening and fixing the ring gear. The differential case 203 is divided into two at the flange portion 205 and has a so-called two-piece structure of a main body portion 207 and a lid portion 209. A spline portion 208 for rotational engagement is provided on the inner peripheral surface of the main body portion 207 of the differential case 203 in a direction along the rotation axis.

  In the differential case 203, left and right side gears 211 and 213 are rotatably supported. Left and right axle shafts 215 and 217 are coupled to the left and right side gears 211 and 213, respectively. A plurality of pinion gears 219 in the circumferential direction mesh with the left and right side gears 211 and 213. Each pinion gear 219 is rotatably supported on the pinion shaft 221.

  Friction plate sets 223 and 235 are interposed between the differential case 203 and the side gears 211 and 213. The inner plate of each friction plate set 223, 225 meshes with the spline portion 227, 229 of each side gear 211, 213, and the outer plate meshes with the spline portion 208 on the differential case 203 side, and engages with the differential case 203 in the rotational direction. However, it can move in the direction along the rotation axis.

  Pressure rings 231 and 233 are provided adjacent to the friction plate sets 223 and 225, and spherical washers 235 and 237 are provided adjacent to the pressure rings 231 and 233. The pressure rings 231 and 233 and the spherical washers 235 and 237 mesh with the spline portion 208 on the differential case 203 side, engage with the differential case 203 in the rotational direction, and are movable in the direction along the rotational axis. .

  A cam surface is set between the pinion shaft 221 and the spherical washers 235 and 137.

  When a torque is input to the flange portion 205 from a drive pinion gear (not shown) via a ring gear, the differential case 203 rotates. As the differential case 203 rotates, the pressure rings 231 and 233 and the spherical washers 235 and 237 receive torque input via the spline portion 208. By this torque input, the pinion shaft 221 rotates around the rotational axis of the differential case 203 via the cam surface between the spherical washer 235 and the pinion shaft 221, and is moved to the left and right side gears 211 and 213 via the pinion gear 219. Torque is transmitted. Torque is transmitted from the left and right side gears 211 and 213 to the left and right axle shafts 215 and 217, and the left and right wheels are rotationally driven.

  In the torque transmission, the spherical washer 235, 237 receives a moving force in the left-right direction so as to widen the mutual space according to torque input by the action of the cam surface between the spherical washer 235, 237 and the pinion shaft 219. With this moving force, the pressure rings 231 and 233 are interlocked, and the left and right friction plate sets 223 and 225 are fastened between the end walls of the differential case 203.

By this fastening, the left and right side gears 211 and 213 are frictionally engaged with the differential case 203, and a differential limiting force is applied to the left and right side gears 211 and 213. Therefore, when the left and right wheels are about to rotate differentially, differential limitation is performed by the friction plate sets 223 and 225. This differential limiting force increases in accordance with the magnitude of torque input from the drive pinion shaft side.
(Problems with preload settings)
In the torque sensitive LSD, in order to improve the initial characteristics, the friction plate sets 223 and 225 are pressurized with a spring or the like to apply an initial torque. However, in order to incorporate a spring or the like, special parts, processing, and the like are required, which causes a cost increase.
(Problems with splines and lugs)
Since the torque of the differential case 203 is transmitted to the pinion gear 219, the side gears 211, 213 and the like, the spline portion 208 needs to be processed, resulting in high costs.

In addition, the material of the differential case 203 is set to be lower in strength than the pressure rings 231 and 233 and the friction plates 223 and 225 in consideration of workability and the like. For this reason, indentation or the like is generated in the spline portion 208, and smooth transmission of the axial thrust is hindered, resulting in a decrease in differential limiting torque, occurrence of hysteresis, and a corresponding decrease in response.
(Problem of flange division)
In the structure in which the differential case 203 is divided at the flange portion 205 as described above, the meshing position is likely to change due to the meshing reaction force of the ring gear fastened and fixed to the flange due to a decrease in the support rigidity at the flange portion 205. It was easy to invite a biting sound. In addition, there is a problem that the ring gear fastening bolt is liable to be loosened due to slippage of the split surface of the flange portion 205 or the like.

On the other hand, when the structure is divided at a portion other than the flange portion 205 and fastened with a bolt or the like, the inner diameter of the case has to be reduced in order to secure the space for the bolt hole and the screw portion, and as a result, the pinion gear 219, The diameters of the built-in components such as the side gears 211 and 213 are also reduced, and it may be difficult to ensure sufficient strength performance.
(Weight problem)
The LSD requires a very high strength because the engine torque is amplified and transmitted by the transmission and the final reduction gear. In particular, the lid shaft portion into which the bearing is inserted is light and small, and a strong meshing reaction force acts on the lid shaft portion. Further, since the bearing is usually press-fitted and held in the bearing insertion portion, if the portion is made of an aluminum alloy or the like, problems such as breakage or loose fitting of the bearing occur. Further, when the case main body is made of an aluminum alloy or the like, a significant dent or the like is generated in the spline portion that transmits torque to the pressing member or the friction member, which is problematic even with iron-based materials. For this reason, it has been extremely difficult to establish the differential case 203 using an aluminum alloy or the like. As a result, it has become the part where weight reduction has not progressed most.

JP 2000-230627 A

  Problems to be solved are that, in the torque-sensitive LSD, special parts and processing are required to incorporate a spring for preload setting, a spline part for transmitting the torque of the differential case, etc. Is difficult, and indentation due to torque transmission is likely to occur in the spline part, and the division at the flange part of the differential case reduces the rigidity at the flange part, and LSD is the least advanced in weight reduction Is a point.

  According to the present invention, a pin member extends in the direction along the rotation axis on the outer peripheral side in the first rotating member, and the friction member and the cam member are engaged with the pin member, whereby the first rotating member The main feature is that the pin member is used for other required functions.

  The first rotating member includes a main body portion and a lid body portion, and the pin member is commonly used as a fastener for fastening the lid body portion to the main body portion.

  The openings are provided at both ends in a direction along the rotation axis of the main body, and the lid is provided at both of the openings.

  The pin member supports and commonly uses urging means, and the urging means imparts a preload to the friction member.

  The biasing means includes a movable member and a disc spring, the movable member is displaced by an external operation, and the disc spring changes a biasing force according to the displacement of the movable member.

  The movable member is provided with an engagement receiving portion, and the engagement receiving portion is engaged with an engagement portion of a jig for external operation, and the movable member is displaced in conjunction with rotation by rotation of the axis of the jig. Features.

  In the differential device of the present invention, since the pin member that engages the friction member and the pressing member is shared for other required functions, it is possible to suppress an increase in special parts and processing. Thereby, the structure can be simplified, the increase in weight can be suppressed, and it can be manufactured at low cost.

  The first rotating member includes a main body portion and a lid body portion, and the main body portion includes an opening for incorporation at an end portion in a direction along the flange portion and the rotation axis, and the lid body Since the part is configured to be attached to the opening, the integral-type flange part is several times higher in cross-sectional secondary moment that determines rigidity even in the same space (same thickness) as compared to the two-part flange part. In addition, the rigidity increases dramatically.

  Since the pin member is used as a fastener for fastening the lid portion to the main body portion, there is no need to provide a spline portion or the like for engaging the friction member and the pressing member on the first rotating member side, and processing is extremely easy. It becomes.

  A friction member and a pressing member can be engaged with the fastener, and a friction member and a pressing member can be engaged with a high-strength fastener. Can be done.

  Since the friction member and the pressing member are engaged with the fastener, a space for fastening the fastener and a space for engaging the friction member and the pressing member can be shared, and a space inside the first rotating member can be used. Can be secured. By securing this space, the diameters of the second rotating member, the third rotating member, etc. can be secured, and sufficient strength and performance can be secured.

  The openings are provided at both ends in the direction along the rotation axis of the main body, and the lids are provided at both the openings, so that the space for the contents is not sacrificed. A piece structure can be adopted. In addition, even if the main body portion is made of a relatively soft material, torque is transmitted through the pin member, so that no biting into the spline portion occurs. Further, since the flange portion is an integral structure, the rigidity is several times higher than that of the conventional structure with two divisions. Therefore, both ends that require the most strength are made of a high-strength material such as iron, and the main body including the flange that has the largest volume and affects the weight is made of a light material such as an aluminum alloy, magnesium alloy, or reinforced plastic. It is possible to produce. For this reason, it is excellent in strength reliability and overall weight reduction can be achieved.

  The pin member supports and shares the biasing means, and the biasing means imparts a preload to the friction member, so that no special parts or processing for supporting the biasing means are required, and the structure is simple. Further, it is possible to suppress the increase in weight and to manufacture at a low cost.

  The biasing means includes a movable member and a disc spring. The movable member is displaced by an external operation, and the disc spring changes the biasing force according to the displacement of the movable member. The urging force of the disc spring can be easily adjusted by operating.

  An engagement receiving portion is provided on the movable member, and the engagement receiving portion is engaged with an engaging portion of a jig for external operation, and is displaced in conjunction with rotation of the axis of the jig to displace the movable member. The movable member can be easily adjusted by rotating the jig shaft, and the biasing force of the disc spring can be easily changed.

  The purpose of suppressing special parts and processing was realized by sharing parts. The purpose of eliminating the need for processing the spline and the like and suppressing indentation due to torque transmission was realized by incorporating a pin member. The purpose of improving the rigidity of the flange part was realized by forming a flange part on the main body of the differential case. The objective of reducing the weight of the LSD was realized with a three-piece differential case.

  FIG. 1 is a cross-sectional view of a differential device according to a first embodiment of the present invention, and FIG.

  As shown in FIG. 1, the differential device 1 includes a differential case 3 as a first rotating member on the case, side gears 5 and 7 as a pair of second rotating members, and a pinion gear 9 as a third rotating member. Yes.

  The differential case 3 includes a main body portion 11 and a lid body portion 13.

  The main body portion 11 is integrally provided with a flange portion 15. A ring gear as a transmission member that receives torque input from the drive pinion gear is fastened to the flange portion 15. The main body 11 is provided with an opening 17 for incorporation at the end in the direction along the rotational axis. In the main body 3, a bolt insertion hole 21 is provided in the end wall 19 on the flange portion 15 side. A plurality of bolt insertion holes 21 are provided at predetermined intervals in the rotational circumferential direction of the differential case 3. Continuing from the bolt insertion hole 21, a bolt insertion groove 23 having a semicircular cross section is provided across the opening 17 at the end on the inner peripheral surface of the main body 11 as shown in FIGS. .

  An attachment window 25 is formed in the center of the main body 11 in the direction along the rotational axis. A boss portion 27 is provided on the end wall 19 side of the main body portion 11. The boss portion 27 is rotatably supported on the differential carrier side by a ball bearing or the like.

  A bolt through hole 29 is provided in the lid portion 13 so as to face the bolt insertion hole 21 and the bolt insertion groove 23.

  Bolts 31 that are fasteners are inserted as pin members from the respective bolt insertion holes 21 of the main body portion 11 and pass through the bolt insertion holes 29 of the lid body portion 13. A nut 33 is fastened to the bolt 31 outside the bolt insertion hole 29, and the main body 11 and the lid 13 are fastened and joined. With the arrangement of the bolt 31, the bolt 31 is extended as a pin member in the direction along the rotational axis on the outer peripheral side in the differential case 3.

  The lid portion 13 is provided with a boss portion 35 similar to the boss portion 27. The boss portion 35 is rotatably supported on the differential carrier side by a ball bearing or the like.

  The side gears 5 and 7 are rotatably disposed in the differential case 3. Engaging lugs 41 and 43 are provided on the bosses 37 and 39 of the side gears 5 and 7. An axle shaft, which is a pair of shafts that pass through the boss portions 27 and 35 of the differential case 3, is coupled to the side gears 5 and 7.

  The pinion gear 9 is rotatably supported on the pinion shaft 44. The pinion gear 9 meshes with the side gears 5 and 7 and interlocks the side gears 5 and 7. This interlocking coupling enables torque transmission between the differential case 3 and the side gears 5 and 7 and allows relative rotation between the side gears 5 and 7.

  Between the side gears 5 and 7 and the differential case 3, multi-plate friction plate groups 45 and 47 are arranged as friction members. The friction plate sets 45 and 47 limit the differential rotation between the side gears 5 and 7 according to the fastening force. The inner plates of the friction plate assemblies 45 and 47 engage with the lug portions 41 and 43 of the side gears 5 and 7 in the rotational direction, and are movable in the direction along the rotational axis. The outer plates of the friction plate assemblies 45 and 47 engage with the bolts 31 in the rotational direction, and can move in the direction along the rotational axis. The friction plate sets 45 and 47 are configured to engage with the differential case 3 by engaging with the bolts 31.

  Adjacent to the friction plate sets 45 and 47, pressure plates 49 and 51 as pressing members are provided. The pressure plates 49 and 51 engage with the bolt 11 in the rotational direction, and are movable in a direction along the rotational axis. The pressure plates 49 and 51 are engaged with the differential case 3 by engaging with the bolts 31.

  The pressure plates 49 and 51 are provided with cam surfaces 53 and 55, respectively. The cam surfaces 53 and 55 are formed in, for example, a concave shape in a mountain shape, and are configured to engage with the pinion shaft 44 having a circular cross section in the rotation direction. It is also possible to provide a cam surface having a convex shape on the outer surface of the pinion shaft 44 so as to engage with the cam surfaces 53 and 55.

  The pressure plates 49 and 51 are provided with spherical portions 57 and 59 to support the pinion gear 9. The opposing surfaces 61 and 63 of the pressure plates 49 and 51 slightly protrude into the mounting window 25. A coil spring 65 as a biasing means is supported on the bolt 31 in the mounting window 25. The coil spring 65 is in elastic contact with the opposing surfaces 61 and 63 of the pressure plates 49 and 51. A preload is applied to the friction plate sets 45 and 47 through the pressure plates 49 and 51 by the biasing force of the coil spring 65.

  Next, the operation will be described.

  When torque is input from the drive pinion gear to the flange portion 15 via the ring gear, the differential case 3 rotates. As the differential case 3 rotates, torque is transmitted to the pressure plates 49 and 51 engaged with the bolt 31, and torque is transmitted to the pinion shaft 44 via the cam surfaces 53 and 55. By this torque transmission, the pinion gear 9 and the side gears 5 and 7 rotate together. Torque is transmitted from the side gears 5 and 7 via the left and right axle shafts, and the left and right wheels are rotationally driven.

  When the cam surfaces 53 and 55 abut on the pinion shaft 44 in the rotational direction, the pressure plates 49 and 51 are moved toward the friction plate sets 45 and 47 by the cam action. By this movement, the friction plate sets 45 and 47 are fastened between the pressure plates 49 and 51, the end wall 19, and the lid body portion 13.

  In this case, as the torque transmitted from the differential case 3 to the pressure plates 49 and 51 increases, the cam force of the cam surfaces 53 and 55 increases, so that the friction plate assemblies 45 and 47 increase the fastening force according to the torque. . The side gears 5 and 7 and the differential case 3 are frictionally engaged by the fastening force of the friction plate sets 45 and 47, and differential restriction between the side gears 5 and 7 is performed. As described above, the differential limiting force increases as the torque increases.

  Torque is transmitted to the left and right wheels while performing differential restriction in accordance with torque increase.

  Further, since the preload is applied to the friction plate sets 45 and 47 through the pressure plates 49 and 51 by the biasing force of the coil spring 65, torque transmission can be performed while obtaining the differential limiting force from the beginning.

  Therefore, at the time of differential rotation of the left and right wheels, the pinion gear 9 rotates around the pinion shaft 44 to allow differential rotation between the side gears 5 and 7. , 47 preload and frictional force according to torque.

  With this configuration, in this embodiment, since the flange portion 15 is formed integrally with the main body portion 11 of the differential case 3, the flange portion 15 can be made highly rigid and the ring gear can be reliably supported. With this reliable support, the meshing sound of the ring gear with the drive pinion gear can be suppressed.

  Further, unlike the conventional flange portion having a mating structure, the occurrence of loosening of the bolts that fasten and fix the ring gear can be greatly suppressed.

  The bolt 31 serves as a fastening connection between the body portion 11 and the lid portion 13 of the differential case 3, an engaging portion such as the pressure plates 49 and 51, and a support portion of the coil spring 65. A sufficient circumference can be secured. For this reason, the side gears 5 and 7, the pinion gear 9, the pressure plates 49 and 51, the friction plates 45 and 47, etc., which are the contents of the differential case 3, can be increased, and sufficient strength and performance can be ensured.

  Since the bolt 31 is used as an engaging portion for the pressure plates 49, 51, etc., special processing such as an engaging spline portion and a lug portion is not required, and the manufacture becomes easy and can be manufactured at low cost.

  The bolt 31 has strength, and even if the pressure plates 49 and 51 and the friction plates 45 and 47 are strongly engaged at the time of torque transmission, the generation of indentations and the like can be suppressed. By suppressing the indentation or the like, the thrust force generated by the cam surfaces 53 and 55 can be efficiently transmitted to the friction plate assemblies 45 and 47 via the pressure plates 49 and 51. By such thrust force transmission, the performance can be reliably maintained and a high drive response can be obtained.

  Since the coil spring 65 for generating a preload is incorporated using the bolt 31, it can be securely held without requiring special processing or members, and an inexpensive and highly reliable device can be obtained. .

  FIG. 3 is a cross-sectional view of a differential device according to a second embodiment of the present invention. Note that components corresponding to those in the first embodiment are described with the same reference numerals.

  In the differential apparatus 1A of the present embodiment, the differential case 3 has a three-piece configuration. The differential case 3 includes openings 67 and 17 at both ends in the direction along the rotation axis of the main body 11 </ b> A including the flange 15. Lids 69 and 13 are provided in both the openings 67 and 17.

  The lid 69 is provided with the bolt insertion hole 21, and the main body 11 </ b> A is provided with a bolt insertion groove 23.

  The bolt 31 passed through the bolt insertion hole 21 and the bolt insertion groove 23 passes through the bolt through hole 29 and the nut 33 is fastened in the same manner as described above.

  Therefore, this embodiment can achieve the same effects as those of the first embodiment.

  In the present embodiment, the lid portions 69 and 13 can be made of steel, and the main body portion 11A having the largest volume can be made of an aluminum alloy or the like.

  The boss portions 27 and 35 of the lid portions 69 and 13 on both sides have a small diameter and a small section modulus, and a bearing is press-fitted to receive a high load due to the meshing reaction force of the ring gear. For this reason, the boss portions 27 and 35 need to be made of iron castings or steel, and it is extremely difficult to establish them with an aluminum alloy or the like.

  As described above, by using only the main body portion 11A as an aluminum alloy, the portions of the boss portions 27 and 35 that require high strength can be made of steel or the like, and the overall weight can be significantly reduced. However, it is possible to obtain an LSD with excellent reliability.

  Further, even if the main body 11A is made of an aluminum alloy or the like, torque transmission to the pressure plates 49 and 51 and the friction plates 45 and 47 is performed via the bolt 31 having a large contact area. Degradation and the like can also be suppressed.

  FIG. 4 is a cross-sectional view of a differential device according to a third embodiment of the present invention. Note that components corresponding to those in the second embodiment will be described with the same reference numerals.

  In the differential apparatus 1B of the present embodiment, the urging means is changed to enable preload adjustment by an external operation.

  In this embodiment, the urging means 71 is composed of a movable member 73 and a disc spring 75. Both the movable member 73 and the disc spring 75 are fitted to the bolt 31.

  The movable member 73 includes a pressing movement member 77 and a rotation driving member 79. A cam structure 81 is provided between the pressing and moving member 77 and the rotation driving member 79. Therefore, when the rotation drive member 79 is rotated, the cam structure 81 works due to relative rotation with the pressing movement member 77, and the pressing movement member 77 moves in a direction in which the disc spring 75 is pressed.

  The rotational drive member 79 is provided with a face gear 83 as an engagement receiving portion. The rotation drive member 79 is in contact with the inner end surface 63 of the pressure plate 49. The pressing moving member 77 is provided with an engaging portion 85. The engaging portion 85 is engaged with the main body portion 11 </ b> A side of the differential case 3.

  The disc spring 75 is in contact with the spacer 87, and the spacer 87 is in contact with the facing surface 61 on the pressure plate 49 side.

  The rotational drive of the rotational drive member 79 is externally operated by a jig 89. The jig 89 is provided with a face gear 89 as an engaging portion in a circular shape. A projection 93 is provided at the tip of the jig 89. The main body portion 11A of the differential case 3 is provided with a support hole 95 into which the convex portion 93 is fitted. When the convex portion 93 is fitted into the support hole 95, the face gear 91 of the jig 89 engages with the face gear 83 of the rotation drive member 79.

  The jig 89 is inserted from the outside of the differential carrier and performs an external operation.

  FIG. 5 is a cross-sectional view illustrating the differential carrier 99. In FIG. 5, the differential device 1 </ b> B is supported in the main body 101 of the differential carrier 99. The ring gear 103 of the differential device 1B meshes with the drive pinion gear 107 of the drive pinion shaft 105. A rear cover 109 is attached to the rear portion of the main body 101 of such a differential carrier 99.

  The rear cover 109 is provided with a hole for filling the differential carrier 99 with oil, and a filler plug is attached to the hole. The jig 89 can be easily inserted by removing this filler plug. It is also possible to set other dedicated holes for inserting the jig 89.

  As shown in FIG. 4, the protrusion 93 of the inserted jig 89 is fitted into the support hole 95 of the main body 11 </ b> A, and the face gear 91 of the jig 89 is engaged with the face gear 83 of the rotation drive member 79. When the jig 89 is rotated in this state, the rotation drive member 79 is interlocked with the rotation. By this rotation interlocking, the cam structure 81 works, and the pressing movement member 77 moves to the disc spring 75 side. By this movement, the disc spring 75 is pressed between the spacer 87 and the pressing movement member 77, and the reaction force of the disc spring 75 increases. The reaction force of the disc spring 75 is transmitted on the one hand to the friction plate assembly 47 via the pressing and moving member 77, the rotation driving member 79, and the pressure plate 51, and on the other hand, to the friction plate via the spacer 87 and the pressure plate 49. It is transmitted to the set 45.

  Accordingly, the preload can be applied to the friction plate sets 45 and 47 by the disc spring 75, and the differential limiting force can be applied from the beginning.

  Moreover, the set reaction force of the disc spring 75 can be adjusted by an external operation of the jig 89, and the preload can be adjusted very easily.

  That is, in general, this kind of preload adjustment is performed by removing the drive pinion shaft 105 in FIG. 5 and the work is large, and the user cannot easily adjust it.

  On the other hand, as in the present embodiment, the preload adjustment can be performed very easily by the user or the like by an external operation using the jig 89.

  After the preload adjustment is completed, the jig 89 is pulled out and the filler plug is attached to the rear cover 109 again.

  FIG. 6 is a cross-sectional view of a differential device according to a fourth embodiment of the present invention. Note that components corresponding to those in the third embodiment are denoted by the same reference numerals for description.

  In the differential device 1C of the present embodiment, the pin member 111 itself is used instead of the bolts of the respective embodiments. The differential case 3 is divided into two parts by a flange part 15C, and includes a main body part 11C and a lid part 69C.

  In addition to the bolt insertion groove 23, the main body portion 11C is provided with a fitting portion 115 having a circular cross section on the end wall 113 side. The inner diameter of the fitting portion 115 is formed substantially the same as the semicircular inner diameter of the bolt insertion groove 23C. The lid portion 69C is provided with a fitting portion 117 corresponding to the fitting portion 115 and a pin insertion groove 119 corresponding to the pin insertion groove 23C.

  The pin member 111 is inserted into the pin insertion grooves 23 </ b> C and 119, and both ends are fitted into the fitting portions 115 and 117, and are fixed in the differential case 3. The pressure plates 49 and 51 and the friction plate assemblies 45 and 47 are engaged with the pin member 111 in the rotation direction, and the urging means 71 is attached to the attachment window 25.

  Further, the jig 89C used in this embodiment has a configuration in which the face gear 91 is provided in a semicircular shape instead of a circular shape, and is simplified.

  In the present embodiment, the effect as in the flange portion 15 is not achieved as compared with the first embodiment, but by using the bolt 31 as the pin member 111, an equivalent effect can be achieved.

  Moreover, in this embodiment, the pin member 111 does not need to be particularly fastened, and the number of parts can be reduced and the structure can be simplified.

It is sectional drawing of a differential apparatus (Example 1). (Example 1) which is principal part sectional drawing of a differential case main-body part. (Example 2) which is sectional drawing of a differential apparatus. (Example 3) which is sectional drawing of a differential apparatus. (Example 3) which is sectional drawing explaining a differential carrier. (Example 4) which is sectional drawing of a differential apparatus. It is sectional drawing of a differential apparatus (conventional example).

Explanation of symbols

1, 1A, 1B, 1C Differential device 3 Differential case (first rotating member)
5,7 Side gear (second rotating member)
9 Pinion gear (third rotating member)
11, 11A, 11C Body part 13, 69, 69C Cover part 15 Flange part 17, 67 Opening part 31 Bolt (pin member, fastener)
45, 47 Friction plate assembly (friction member)
49, 51 Pressure plate 65 Coil spring (biasing means)
71 Biasing means 73 Movable member 75 Belleville spring 83 Face gear (engagement receiving portion)
91 Face gear (engagement part)
89, 89C Jig 111 Pin member

Claims (6)

A case-like first rotating member that inputs and outputs torque from a transmission member that is rotatably supported on the vehicle body side and is attached to a flange portion on the outer peripheral surface;
A pair of second rotating members supported in a relatively rotatable manner in the first rotating member and coupled to a pair of shafts;
A third rotating member disposed in the first rotating member and coupled to each second rotating member to allow relative rotation between the second rotating members by rotation;
A friction member for engaging the first and second rotating members and limiting differential rotation of the second rotating member according to a fastening force;
Engage the first and third rotating members to allow torque transmission by rotating the first rotating member as revolution of the third rotating member, and move according to the torque to give a fastening force to the friction member In a differential device comprising a pressing member,
On the outer peripheral side in the first rotating member, a pin member is extended in a direction along the rotation axis,
The pin member is engaged with the friction member and the pressing member and engaged with the first rotating member,
A differential apparatus characterized in that the pin member is shared by other functions. The differential device according to claim 1,
The first rotating member is composed of a main body portion and a lid portion,
The main body has an opening for incorporation at an end in a direction along the flange and the rotation axis.
The lid portion is attached to the opening,
The differential apparatus according to claim 1, wherein the pin member is shared as a fastener for fastening the lid portion to the main body portion. A differential device according to claim 2, wherein
The openings are provided at both ends in a direction along the rotation axis of the main body,
The differential device according to claim 1, wherein the lid is provided in both of the openings. A differential device according to any one of claims 1 to 3,
The pin member is shared by supporting the biasing means,
The differential unit according to claim 1, wherein the biasing unit applies a preload to the friction member. A differential device according to claim 4, wherein
The biasing means comprises a movable member and a disc spring,
The movable member is displaced by an external operation,
The differential device according to claim 1, wherein the disc spring changes an urging force according to a displacement of the movable member. A differential device according to claim 5, wherein
The movable member is provided with an engagement receiving portion,
The differential receiving device is characterized in that the engaging portion engages with an engaging portion of a jig for external operation, and displaces the movable member in conjunction with rotation by rotation of the axis of the jig.

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