CN210715628U - Connection structure between rotating member and rotating shaft, and power transmission device for vehicle - Google Patents
Connection structure between rotating member and rotating shaft, and power transmission device for vehicle Download PDFInfo
- Publication number
- CN210715628U CN210715628U CN201921026495.XU CN201921026495U CN210715628U CN 210715628 U CN210715628 U CN 210715628U CN 201921026495 U CN201921026495 U CN 201921026495U CN 210715628 U CN210715628 U CN 210715628U
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- Prior art keywords
- side gear
- shaft
- positioning ring
- vehicle
- power transmission
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 25
- 230000008878 coupling Effects 0.000 claims description 24
- 238000010168 coupling process Methods 0.000 claims description 24
- 238000005859 coupling reaction Methods 0.000 claims description 24
- 239000003921 oil Substances 0.000 claims description 14
- 239000010687 lubricating oil Substances 0.000 claims description 8
- 238000000354 decomposition reaction Methods 0.000 abstract description 3
- 238000003780 insertion Methods 0.000 description 8
- 230000037431 insertion Effects 0.000 description 8
- 230000001050 lubricating effect Effects 0.000 description 4
- 238000005461 lubrication Methods 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
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- General Details Of Gearings (AREA)
- Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
Abstract
The utility model provides a rotary member and rotation axis's connection structure and vehicle's power transmission device, the eccentric core that accompanies the holding ring when can prevent the decomposition of device, assembly block or drop of holding ring. In a connection structure of a side gear (6) and a drive shaft (2), the side gear (rotary member) (6) and the drive shaft (rotary shaft) (2) which is inserted into the axial center of the side gear (6) slidably in the axial direction by spline fitting are fixed in the axial direction by a positioning ring (7), the positioning ring (7) is fitted into a fitting groove (2a) formed in the outer periphery of one end in the axial direction of the drive shaft (2), the positioning ring (7) is formed into a non-circular ring shape, and the positioning ring (7) is brought into contact with the fitting groove (2a) formed in the drive shaft (2) at least at three points (P1, P2, P3).
Description
Technical Field
The present invention relates to a coupling structure of a rotary member and a rotary shaft, and a power transmission device of a vehicle having the coupling structure.
Background
For example, a differential device (differential device) is provided in a power transmission path (power transmission device) of a vehicle, and a side gear (side gear) provided in the differential device and a drive shaft (drive shaft) are coupled to each other by fitting a spline (spline) that rotates integrally. The spline fitting allows relative movement between the side gear and the drive shaft in the axial direction, and therefore relative movement between the side gear and the drive shaft in the axial direction is usually prevented by a positioning ring (snap ring) (see, for example, patent document 1).
Here, the positioning ring is a circular ring-shaped member partially cut out, and is fitted into a fitting groove formed in the outer periphery of the drive shaft, thereby preventing the relative movement between the side gear and the drive shaft in the axial direction and fixing the side gear and the drive shaft in the axial direction. The side gear and the drive shaft are spline-fitted and fixed in the circumferential direction (rotational direction), and therefore both rotate integrally.
[ Prior art documents ]
[ patent document ]
[ patent document 1] Japanese patent application laid-open No. Hei 10-009248
SUMMERY OF THE UTILITY MODEL
[ problem to be solved by the utility model ]
However, since the conventional positioning ring is formed in a circular ring shape, when the positioning ring is fitted into the fitting groove of the drive shaft, a radial gap inevitably occurs between the positioning ring and the fitting groove, and the positioning ring can move in the radial direction within the fitting groove to the extent of the radial gap. Therefore, the positioning ring is eccentric, and for example, when the drive shaft is inserted into or removed from the side gear when the differential device of the vehicle is disassembled and assembled as in the above-described example, the following problems may occur: the positioning ring is caught by a differential case (differential case) or the like and falls off, and the differential apparatus cannot be smoothly disassembled and assembled.
The present invention has been made in view of the above problems, and an object of the present invention is to provide a coupling structure of a rotary member and a rotary shaft, which can prevent a positioning ring from being stuck or falling off due to misalignment of the positioning ring during disassembly or assembly of a device, and a power transmission device of a vehicle having the coupling structure.
[ means for solving problems ]
In order to achieve the above object, the present invention provides a coupling structure of a rotary member 6 and a rotary shaft 2, wherein the rotary shaft 6 is inserted slidably in an axial direction into an axial center of the rotary member 6 by spline fitting, the coupling structure fixes the rotary member 6 and the rotary shaft 2 in the axial direction by a positioning ring 7, the positioning ring 7 is fitted into a fitting groove 2a formed in an outer periphery of one end in the axial direction of the rotary shaft 2, and the positioning ring 7 is formed in a non-circular ring shape so that the positioning ring 7 contacts the fitting groove 2a formed in the rotary shaft 2 at least at three points P1, P2, and P3.
For example, the positioning ring 7 is formed in a C-ring shape such that three points of both circumferential ends and a circumferential center thereof are in contact with the fitting groove 2a formed in the rotary shaft 2.
The outermost dimension L of the positioning ring 7 from the axial center of the rotating shaft 2 is equal to the outermost dimension R of the circular ring-shaped positioning ring 107.
The utility model provides a power transmission device of vehicle, including foretell rotating member 6 and the connection structure of rotation axis 2. Here, the rotating member 6 may be, for example, a side gear of the differential device 1 provided in a power transmission path of the vehicle 10, and the rotating shaft 2 may be a drive shaft.
In the power transmission device for a vehicle, an oil passage 3b for supplying lubricating oil between the differential case 3 and the back surface of the side gear 6 may be formed in a part of an inner surface of the differential case 3 of the differential device 1 facing the side gear 6.
[ effects of the utility model ]
According to the utility model discloses, the holding ring is at least at three points and the gomphosis groove contact that forms in the rotation axis, therefore prevents its eccentric core, prevents blocking or coming off of the holding ring when decomposition, the assembly of device and carries out the decomposition, the assembly of device smoothly.
Drawings
Fig. 1 is a plan view schematically showing a power transmission device of a vehicle having a coupling structure according to the present invention.
Fig. 2 is a sectional view of a differential device portion of a vehicle showing a coupling structure according to the present invention.
Fig. 3 is an enlarged detailed view of a portion a of fig. 2.
Fig. 4(a) is an enlarged sectional view taken along line B-B of fig. 2, and fig. 4(B) is a view similar to fig. 4(a) of the conventional coupling structure.
Fig. 5 is an enlarged sectional view taken along line C-C of fig. 2.
Fig. 6 is a cross-sectional view taken along line D-D of fig. 5.
Fig. 7 is a partial sectional view showing a comparative example (conventional structure) of a lubricating structure of a differential device of a vehicle.
Fig. 8(a) and 8(b) are sectional views taken along line E-E of fig. 7.
[ description of symbols ]
1: differential gear
2: driving shaft (rotating shaft)
2 a: drive shaft fitting groove
3: differential box
3 b: oil circuit of differential case
6: side gear (rotating component)
7: locating ring
8: gasket (buffer component)
L: outermost dimension of the retaining ring
P1-P3: contact point of positioning ring
R: outermost dimension of circular ring-shaped positioning ring
S: clearance between back of side gear and inner surface of differential case
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Fig. 1 is a plan view schematically showing a power transmission device of a vehicle having a coupling structure according to the present invention, and the illustrated vehicle 10 employs a front-engine rear-drive system (FR system), and has an engine (E/G)11 mounted as a drive source on a front portion (left end portion in fig. 1). A torque converter (T/C)12 and a transmission (T/M)13 are connected to the engine 11 in this order, and a propeller shaft (propeller shaft)14 extends linearly from the transmission 13 toward the vehicle rear side (the right side in fig. 1) at the center in the vehicle width direction.
The propeller shaft 14 has a rear end connected to a differential device (differential device)1, left and right drive shafts 2 extending horizontally from the differential device 1 to the outside in the vehicle width direction (the vertical direction in fig. 1), and a rear wheel WR as a drive wheel is attached to an outer end of each drive shaft 2. In addition, left and right axles (front axles) 15 are disposed in parallel with the rear drive shaft 2 in the front portion of the vehicle 10, and front wheels WF as steering wheels are mounted to outer end portions of the axles 15.
In the above power transmission device, the rotational power output from the engine 11 is transmitted to the differential device 1 via the torque converter 12, the transmission case 13, and the propeller shaft 14, and is distributed and transmitted to the left and right drive shafts 2 in the differential device 1. Further, since the rotation of the left and right drive shafts 2 is transmitted to the left and right rear wheels WR attached to the drive shafts 2, respectively, to rotationally drive the rear wheels WR, the vehicle 10 travels at a predetermined speed.
In the present embodiment, the coupling structure of the rotating member and the rotating shaft according to the present invention is used in the differential device 1 of the power transmission device, and the details of the coupling structure will be described below with reference to fig. 2 to 4(a) and 4 (b).
Fig. 2 is a sectional view of a differential device portion of a vehicle showing a coupling structure according to the present invention, fig. 3 is an enlarged detail view of a portion a of fig. 2, fig. 4(a) is an enlarged sectional view taken along line B-B of fig. 2, and fig. 4(B) is a view similar to fig. 4(a) of a conventional coupling structure.
As shown in fig. 2, the differential device 1 includes a spherical shell-shaped differential case 3 rotationally driven around the axial center C1 of the left and right drive shafts 2, and a cylindrical shaft insertion portion 3A for inserting the left and right drive shafts 2 is integrally provided in the differential case 3 so as to protrude in the first axis C1 direction (the left-right direction in fig. 2). Further, although not shown, an annular flange portion rising in the vertical direction of fig. 2 is integrally formed on the outer periphery of the differential case 3, and a ring gear for inputting the rotation transmitted from the engine 11 shown in fig. 1 to the differential case 3 via the torque converter 12, the transmission case 13, and the propeller shaft 14 is attached to the flange portion. The differential case 3 is supported by a housing (housing) via left and right shaft insertion portions 3A and is rotatably supported about a first shaft C1.
As shown in fig. 2, a pinion shaft 4 is fixedly inserted into a central portion of the differential case 3 in a direction of a second axis C2 (vertical direction in fig. 2) perpendicular to the first axis C1, and a pair of pinions (bevel gears) 5 rotatably supported by the pinion shaft 4 and a pair of side gears (bevel gears) 6 that are respectively meshed with the pinions 5 and rotatably supported around the first axis C1 are accommodated in the differential case 3. Here, the rotary member of the coupling structure of the rotary member and the rotary shaft of the present invention corresponds to the side gear 6, and the rotary shaft corresponds to the drive shaft 2.
The pair of pinion gears 5 are disposed in the differential case 3 at the upper and lower sides in fig. 2, and the pair of side gears 6 are disposed at the left and right sides thereof with the pinion shaft 4 interposed therebetween. The side gears 6 are spline-fitted to inner end portions of the pair of left and right drive shafts 2 facing the inside of the differential case 3, and the pair of drive shafts 2 are inserted into the shaft insertion portions 3A integrally formed in the differential case 3. Therefore, each side gear 6 rotates integrally with each drive shaft 2. Further, a helical oil groove 3A for feeding the lubricating oil to the side gear 6 side by the rotation of the differential case 3 (the shaft insertion portion 3A) is formed in the inner periphery of each shaft insertion portion 3A of the differential case 3.
As described above, the side gears 6 are coupled to the inner end portions of the drive shafts 2 facing the inside of the differential case 3 by spline fitting, but the spline fitting allows movement of the side gears 6 in the axial direction of the drive shafts 2. Therefore, the axial movement of each side gear 6 is prevented by a positioning ring (snap ring) 7 fitted in a fitting groove 2a (see fig. 3) formed in each drive shaft 2. More specifically, fitting grooves 2a of a predetermined width (a width slightly larger than the outer diameter of the positioning ring 7) are formed over the entire circumference of the inner end portion outer circumference of the spline fitting portion of each side gear 6 offset from each drive shaft 2, and the positioning ring 7 is fitted into each fitting groove 2 a.
Therefore, the axial movement of each drive shaft 2 is prevented by the abutment of the counter gear 6 of the positioning ring 7 against the spline fitting portion (spline tooth) of the drive shaft 2 and the abutment of the step portion 2b of the drive shaft 2 against the outer end surface of the shaft insertion portion 3A of the differential case 3.
In the present embodiment, as shown in fig. 4(a), the positioning ring 7 is formed as a non-circular ring, specifically, a flat C-ring shape partially cut out, and contacts the bottom surface of the fitting groove 2a of the drive shaft 2 (the outer peripheral surface of the portion of the drive shaft 2 where the fitting groove 2a is formed) at three points P1, P2, and P3 shown in the drawing. More specifically, the positioning ring 7 is in contact with the bottom surface of the fitting groove 2a at three points, i.e., the points P1 and P2 at both ends in the circumferential direction and the point P3 at the center (the center in the width direction of fig. 4 a) between the two points P1 and P2 in the circumferential direction.
Here, although fig. 4(b) shows a state where a conventional circular ring-shaped positioning ring 107 is fitted for reference, the positioning ring 107 can move in the radial direction with a radial gap δ formed between the positioning ring and the bottom surface of the fitting groove. In contrast, in the present embodiment, as shown in fig. 4(a), the positioning ring 7 is in contact with the bottom surface of the fitting groove 2a at three points P1, P2, and P3 shown in the figure, and thus the radial movement is prevented. Therefore, the misalignment of the positioning ring 7 does not occur, and the positioning ring 7 is prevented from being caught or dropped during the disassembly and assembly of the differential device 1, so that the disassembly and assembly of the differential device 1 can be smoothly performed. Further, the outermost dimension L of the retainer ring 7 from the axial center (the first axis C1) of the drive shaft 2 is set to be equal to (L ≈ R) the outermost dimension R of the circular ring-shaped retainer ring 107 shown in fig. 4 (b).
In the differential device 1 configured as described above, the rotational power (torque) output from the engine 11 shown in fig. 1 is input to the differential case 3 of the differential device 1 via the torque converter 12, the transmission case 13, and the propeller shaft 14. Then, the differential case 3 rotates about the first axis C1, the differential device 1 splits the rotational power into two and transmits the split rotational power to the left and right drive shafts 2, and the rotation of the left and right drive shafts 2 is transmitted to left and right rear wheels WR (see fig. 1) as drive wheels, so that the vehicle 10 travels on the road.
In the differential device 1, when the vehicle 10 travels straight, the left and right drive shafts 2 receive equal resistance from the road surface, and the pair of pinion gears 5 rotates together with the differential case 3 to distribute and transmit the rotational power to the pair of left and right side gears 6. At this time, the pair of pinions 5 do not rotate (rotate). In contrast, when the vehicle 10 turns, because a difference occurs in the resistance received by the left and right rear wheels WR from the road surface (a difference occurs in the moving distance of the left and right rear wheels WR), the pair of pinion gears 5 rotate to increase the rotational speed of one of the side gears 6 to be higher than the rotational speed of the other side gear 6, and the rotational power is distributed and transmitted to the left and right drive shafts 2 while the turning of the vehicle 10 is smoothly performed.
Next, a lubricating structure of the differential device 1 will be described below with reference to fig. 5 to 8(a) and 8 (b).
Fig. 5 is an enlarged sectional view taken along line C-C of fig. 2, fig. 6 is a sectional view taken along line D-D of fig. 5, fig. 7 is a partial sectional view showing a comparative example of the lubrication structure (a conventional structure corresponding to fig. 6), and fig. 8(a) and 8(b) are sectional views taken along line E-E of fig. 7, which show the lubrication structure on the back surface of only one of the side gears 6. The lubrication structure of the back surface of the other side gear 6 is the same as that of the back surface of the one side gear 6, and therefore, the illustration and description thereof are omitted.
In the present embodiment, as shown in fig. 5 and 6, linear oil passages 3b along the direction of the second shaft C2 (the vertical direction in fig. 5) are formed in a part of the end surface of the inner surface of the differential case 3d facing the side gear 6, specifically, in two places separated in the radial direction (the horizontal direction in fig. 5) from the first shaft C1. The inner diameter side end of each oil passage 3b opens to one end (axially inner end) of a spiral oil groove 3A (see fig. 6) formed in the inner peripheral surface of the shaft insertion portion 3A of the differential case 3, and the outer diameter side end opens to a gap (oil passage) S formed between the back surface of each side gear 6 and the inner surface of the differential case 3 facing the back surface.
As shown in fig. 7, 8 a and 8 b, in the conventional lubricating structure, a radial gap δ 1 having a constant width is formed between the outer periphery of the end portion of the side gear 6 and the inner surface of the differential case 3 facing the outer periphery in the radial direction in order to supply lubricating oil to a washer (sliding member) 8 provided in the gap S between the back surface of the side gear 6 and the inner surface of the differential case 3, and this gap δ 1 is configured as an oil passage. However, in the above-described configuration, as shown in fig. 8(b), the side gear 6 may be misaligned by the gap δ 1 to the maximum extent.
In contrast, in the present embodiment, as shown in fig. 5 and 6, since the oil passage 3b for supplying the lubricating oil to the washer 8 provided in the gap S between the back surface of the side gear 6 and the inner surface of the differential case 3 is formed in the flat surface portion of the differential case 3, the gap between the outer periphery of the end portion of the side gear 6 and the inner surface of the differential case 3 facing in the radial direction can be closed (see fig. 2 and 5). Therefore, the misalignment of the side gear 6 can be suppressed to be small, the side gear 6 and the drive shaft 2 can stably rotate integrally, and the generation of rotational vibration and noise can be prevented. Further, at the time of assembling the differential device 1, the positioning ring 7 can be prevented from being caught on the side gear 6, and thus the assembling of the differential device 1 can be smoothly performed.
When the differential case 3 rotates, the lubricating oil flows in the axial direction toward the side gear 6 in the helical oil groove 3A formed integrally on the inner periphery of the shaft insertion portion 3A of the differential case 3. The lubricating oil flows into two straight oil passages 3b formed in the surface of the differential case 3 facing the side gear 6, receives a centrifugal force generated by the rotation of the differential case 3, flows in the direction of arrows (opposite directions) in fig. 5 in the oil passages 3b, and is supplied from the respective flow passages 3b to the washer 8 provided in the gap S between the back surface of the side gear 6 and the inner surface of the differential case 3 as indicated by the arrows in fig. 6, thereby lubricating the same.
As is apparent from the above description, in the present embodiment, as shown in fig. 4(a) and 4(b), since the positioning ring 7 is formed in a non-circular ring shape and the positioning ring 7 is brought into contact with the fitting groove 2a of the drive shaft 2 at three points P1, P2, and P3 (see fig. 4(a)), core displacement is prevented, and the positioning ring 7 is prevented from being caught or released during disassembly and assembly of the differential device 1, thereby achieving the effects of smooth disassembly and assembly of the differential device 1.
In addition, although the embodiment of the coupling structure between the side gear 6 and the drive shaft 2 in the differential device 1 according to the present invention applied to the vehicle 10 has been described above, the present invention is also applicable to a coupling structure between a rotating member and a rotating shaft by spline fitting and a positioning ring in any other device.
In the present embodiment, the contact points of the positioning ring 7 with the fitting groove 2a of the drive shaft 2 are three points P1, P2, and P3 (see fig. 4 a), but the contact points of the positioning ring 7 with the fitting groove 2a may be four or more points.
The present invention is not limited to the embodiments described above, and various modifications can be made within the scope of the technical ideas described in the specification and the drawings.
Claims (7)
1. A coupling structure of a rotary member and a rotary shaft that is inserted slidably in an axial direction into a shaft center of the rotary member by spline fitting, the coupling structure axially fixing the rotary member and the rotary shaft by a positioning ring that is fitted in a fitting groove formed in an outer periphery of one axial end of the rotary shaft, the coupling structure of the rotary member and the rotary shaft being characterized in that,
the positioning ring is formed in a non-circular ring shape, and is brought into contact with the fitting groove formed in the rotating shaft at least at three points.
2. The structure for coupling a rotating member and a rotating shaft according to claim 1, wherein the positioning ring is formed in a C-ring shape such that three points of both circumferential ends and a circumferential center thereof are in contact with the fitting groove formed in the rotating shaft.
3. The coupling structure of a rotary member and a rotary shaft according to claim 1 or 2, wherein an outermost dimension of the positioning ring from an axial center of the rotary shaft and an outermost dimension of the circular ring-shaped positioning ring are set to be equal.
4. A power transmission device of a vehicle, characterized by comprising: the coupling structure of a rotary member and a rotary shaft according to claim 1 or 2,
the rotating member is a side gear of a differential device provided in a power transmission path of the vehicle, and the rotating shaft is a drive shaft.
5. The vehicle power transmission device according to claim 4, characterized in that an oil passage for supplying lubricating oil between the differential case and a back surface of the side gear is formed in a part of an inner surface of the differential case of the differential device that faces the side gear.
6. A power transmission device of a vehicle, characterized by comprising: the coupling structure of a rotary member and a rotary shaft according to claim 3,
the rotating member is a side gear of a differential device provided in a power transmission path of the vehicle, and the rotating shaft is a drive shaft.
7. The vehicle power transmission device according to claim 6, characterized in that an oil passage for supplying lubricating oil between the differential case and a back surface of the side gear is formed in a part of an inner surface of the differential case of the differential device that faces the side gear.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-156165 | 2018-08-23 | ||
| JP2018156165A JP2020029919A (en) | 2018-08-23 | 2018-08-23 | Connection structure between rotating member and rotating shaft, and power transmission device of vehicle with the same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210715628U true CN210715628U (en) | 2020-06-09 |
Family
ID=69624156
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921026495.XU Expired - Fee Related CN210715628U (en) | 2018-08-23 | 2019-07-03 | Connection structure between rotating member and rotating shaft, and power transmission device for vehicle |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2020029919A (en) |
| CN (1) | CN210715628U (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5548890Y2 (en) * | 1976-12-17 | 1980-11-14 | ||
| JPS6046338U (en) * | 1983-09-02 | 1985-04-01 | 株式会社豊田自動織機製作所 | Fixed structure of drive shaft in power transmission equipment for industrial vehicles |
| JP3219979B2 (en) * | 1995-01-12 | 2001-10-15 | 栃木富士産業株式会社 | Differential device |
| JP2005172093A (en) * | 2003-12-10 | 2005-06-30 | Nissan Motor Co Ltd | Differential case and differential device |
| JP2010276050A (en) * | 2009-05-26 | 2010-12-09 | Ntn Corp | Shaft slipping-out preventive structure |
-
2018
- 2018-08-23 JP JP2018156165A patent/JP2020029919A/en active Pending
-
2019
- 2019-07-03 CN CN201921026495.XU patent/CN210715628U/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP2020029919A (en) | 2020-02-27 |
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| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20200609 |