JPH033821B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Technical Field] The present invention relates to a differential gear in which a working window is opened in a differential gear case.

[Conventional example]

As a conventional differential device, there is, for example, one described in NISSAN Service Bulletin No. 440 published by Nissan Motor Co., Ltd. in June 1981.
That is, this differential device includes a differential gear case that has a working window in the peripheral wall and is integrally provided with an outward flange, and a ring gear that has an inward flange on the inside. a differential gear case and the ring gear,
Both flanges are connected by bolts.

However, in such a conventional differential gear, although the thickness of both flanges is uniform and the rigidity of the flanges themselves is uniform in the rotational direction, the peripheral wall of the differential gear case has
Because there are parts of the working window that are open and parts that are not, the part with the window has low rigidity in the direction of rotation, and the part of the peripheral wall without the window has high rigidity. This non-uniformity in rigidity due to the presence or absence of the window has a negative effect on the rigidity of both flanges, and as a result, the rigidity of the ring gear is smaller in the vicinity of the window and in the vicinity of the peripheral wall without a window than the latter. was.

Incidentally, since the ring gear is a helical gear or a bevel gear, when a rotational force is input to the ring gear, a thrust force acts on the ring gear, and a force acts on the differential gear case in a direction to tilt it.

Then, as mentioned above, since the rigidity of the differential gear case including the ring gear is not uniform in the rotational direction, the input to the ring gear causes partial deformation of the ring gear, causing the transmission device that forms the final reduction gear to deform. There is a problem that the meshing area with the side gear (output gear or drive pinion) becomes uneven in the rotation direction. Figures 1 and 2 illustrate this situation. Figure 1 shows a differential gear case 400 and its flange 410.
4 is a schematic diagram of a state in which a ring gear 420 is attached to the differential gear case 400, and a working window 404 is opened in a peripheral wall 403 of a differential gear case 400. 430
is a pinion mate shaft, and 431 is its fixing pin. FIG. 2 shows the meshing area between the ring gear 420 and the gear on the transmission side in each part a to h in FIG. 1. FIG. 2 shows a portion A of the tooth surface of the ring gear 420 that is engaged and a portion B that is not engaged. In this way, if the meshing area becomes non-uniform in the rotational direction, it may cause uneven wear and damage of the tooth surfaces, and even cause noise.

[Purpose of the invention]

The present invention has been made by focusing on such conventional problems, and by making the rigidity of the ring gear mounting part of the differential gear case as uniform as possible in the rotational direction, the ring gear and the transmission side are improved. The purpose is to make the tooth contact with the gear even.

[Structure of the invention]

That is, the present invention comprises a differential gear case having a working window opened in a peripheral wall and integrally provided with an outward flange, and a ring gear provided with an inward flange on the inside. In a differential device in which a shear gear case and the ring gear are coupled by fixing both the flanges, the rigidity of at least one of the flanges is set to be higher than that of the peripheral wall where the working window is not provided. The present invention relates to a differential device characterized in that the size is reduced near the .

〔Example〕

Next, the present invention will be explained based on the embodiments shown in FIG. 3 and below. Figure 3 shows the gear train, final reduction gear, and differential device of a transaxle type manual transmission. 1 is a clutch housing, 2 is a transmission case, and both are integrated with 1 and 2. A differential housing 3 is configured by the extended portion. Transmission case 2
Includes input shaft 100, main shaft 200, and reverse idler gear shaft 300.
are constructed parallel to each other.

The input shaft 100 has bearings 101,1
02, and has one end protruding into the clutch housing 1, and a clutch disk of a clutch device (not shown) is spline-coupled to the protruding end. 103 is a clutch release bearing for operating the clutch device. The input shaft 100 includes a first gear 11 from the bearing 101 side to the bearing 102 direction.
0, reverse gear 160, second gear 120, third gear 130, fourth gear 140, and fifth gear 150 are provided in this order.

1st gear 110, reverse gear 160, and 2nd gear 120 are all formed integrally with input shaft 100, and 3rd gear 130, 4th gear 140, and 5th gear 150 are rotatably formed on input shaft 100. It is fitted directly onto the outside. 3rd gear 1
A 3-4 speed synchronizer 131 is provided in the input shaft 100 between the input shaft 100 and the 4th speed gear 140, and a 5th speed synchronizer 131 is provided in the input shaft 100 between the 5th speed gear 150 and the bearing 102. Device 1
51 is provided.

The main shaft 200 has a tapered roller bearing 201,
202, which includes an output gear 270 and a first speed main gear 21.
0, a reverse main gear 260, a 2nd speed main gear 220, a 3rd speed main gear 230, a 4th speed main gear 240, and a 5th speed main gear 250. The output gear 270 is formed integrally with the main shaft 200, and is also connected to the first speed main gears 210, 2.
The speed main gear 220 is rotatably fitted directly onto the main shaft 200, and the third speed main gear 230,
The 4th speed main gear 240 and the 5th speed main gear 250 are spline-fitted to the main shaft 200 so that they rotate together. 1st speed main gear 21
A 1-2 speed synchronizer 211 is provided in the main shaft 200 between the 0 and 2 speed main gears 220, and a reverse main gear 260 is formed in a coupling sleeve 212 of this synchronizer 211.

1st speed gear 110 and 1st speed main gear 210, 2nd speed gear 120 and 2nd speed main gear 220, 3rd speed gear 1
30 and 3rd speed main gear 230, 4th speed gear 140 and 4th speed main gear 240, and 5th speed gear 150 and 5th speed main gear 250, respectively, are always in mesh with each other.

The reverse idler gear shaft 300 has a front end fitted into the front cover 22 of the transmission case 2, and a bracket 2 fixed to the rear end.
3 is fixed to the transmission case 2 with a bolt 24, and this bracket 23 and bolt 2
Rotation is stopped by 4. A reverse idler gear 360 is fitted onto the reverse idler gear shaft 300 so as to be rotatable and slidable in the axial direction. In FIG. 3, the cross sections of the input shaft 100 and main shaft 200 and the reverse idler gear shaft 300 are not in the same plane, so the reverse idler gear 360 and the reverse main gear 260 are
Although shown in the figure as being isolated from the reverse idler gear 360, the reverse idler gear 360 is in the chain line position when
60 and input shaft 100 at the same time.
The rotation of the main shaft 200 is transmitted to the main shaft 200.

An axial hole 170 extending in the axial direction is bored at the center of the end of the input shaft 100 opposite to the clutch, and a radial hole extends from the axial hole 170 toward the outer periphery of the input shaft 100. 171, 172, and 173 are drilled. The outer end of the radial hole 171 faces the inner surface of the 5th speed gear 150, the outer end of the radial hole 172 faces the inner surface of the 4th speed gear 140, and the outer end of the radial hole 173 faces the inner surface of the 3rd speed gear 130. The space between the input shaft 100 and each of the gears is lubricated as described later.

The lubricant guide member 4 is arranged in the axial hole 170. The lubricant guide member 4 has a radial hole 17 at its tip.
Pipe 41 extending past 1 to the radial hole 172 side
and a flange 42 integrally formed at the end thereof.
and the pipe 41 near the outer periphery of the flange 42
It consists of a projection 44 integrally formed on the side surface, and the pipe 41 is inserted into the axial hole 170. The outer diameter of the pipe 41 is such that there is some clearance between it and the axial hole 170, and the outer end of the pipe 41 is
It communicates with a gap 25 formed at the inner end of the transmission case 2, and lubricating fluid is introduced into the gap 25 through a path not shown. The protrusion 44 of the flange 42 is connected to the bearing 102
The outer edge of the flange 42 is pressed between the outer ring of the bearing 102 and the transmission case 2, making the entire lubricant guide member 4 non-rotatable.

An axial hole 280 is also formed at the clutch side end of the main shaft 200, and radial holes 281 and 282 are formed between this and the inner surfaces of the first speed main gear 210 and second speed main gear 220. Furthermore, a lubricant guide member 5 is disposed at the opening of the axial hole 280 to introduce the lubricant supplied into the gap 26 through a path not shown into the axial hole 280.
Furthermore, radial holes 281 and 282 provide lubrication between the main shaft 200 and the first-speed main gear 210 and second-speed main gear 220.

Inside the differential housing 3,
A differential gear case 400 is rotatably supported by bearings 401 and 402. A ring gear 420 is fixed to the differential gear case 400 with bolts 421. Bolt 421 is differential gear case 400
The flange 410 of the ring gear 420 and the inward flange 422 of the ring gear 420 are fixed by pressure contact. The ring gear 420 is always meshed with the output gear 270 to constitute a final reduction gear.

A pinion mate shaft 430 is installed inside the differential gear case 400 and is prevented from coming off by a pin 431. Two pinion gears 440 are fitted onto the pinion mate shaft 430 so as to be rotatable facing each other. The two side gears 450 are individually meshed to form a differential device. Both side gears 450 have
The inner ends of two driveshafts (not shown) with front wheels for disturbance attached to their outer ends are individually fixed. 4
60 is a ring gear for a speedometer.

Details of the differential gear case 400 are shown in FIGS. 4-6. That is, this differential gear case 400 is of a type that is integrally molded as a whole, and therefore the working window 404 for assembling and inspecting the pinion mate shaft 430, pinion gear 440, side gear 450, etc., is located on the peripheral wall. It opens at 403. Working window 4
04 has two openings at positions opposite to each other through the center of the differential gear case 400. Therefore, the differential gear case 4
00 rotation causes the peripheral wall 403 and the working window 404 to appear alternately.

The flange 410 of the differential gear case 400 has a thick wall portion 411 and a thin wall portion 412, and its rigidity varies depending on the location.
That is, the working window 4 in the flange 410
04 is increased to form a thick wall portion 411, while the thickness near the peripheral wall 403 where there is no working window 404 is reduced to form a thin wall portion 412, the rigidity of the flange 410 itself is reduced to a thickness similar to that of the working window. It increases near 404 and decreases near peripheral wall 403. Various methods can be used to vary the thickness, such as applying overlay or cutting to the flange 410, which has a uniform thickness throughout, or pre-forming a mold into the shape described above. Said flange 410
The unevenness due to the difference in the thickness of the flange 410
, expressed on the surface of the peripheral wall 403 and the working window 404 side,
The opposite surface is flat for mounting ring gear 420. In this embodiment, the thickness T of the thick wall portion 411 is set to 13 mm, and the thickness t of the thin wall portion 412 is set to 10 mm. It is naturally possible to set the thickness to another value depending on the conditions.

As described above and shown in FIG.
It sticks to the surface. The ring gear 420 itself has uniform rigidity in the rotational direction.

Therefore, differential gear case 400
Since the working window 404 is open, the flange 410 has a property that the rigidity is originally small, especially in the vicinity of the flange 410.
Since the portion near the working window 404 is made into a thick wall portion 411, the rigidity of the flange 410 is increased, while the flange 410 near the peripheral wall 403, which normally has high rigidity, is made into a thin wall portion 412. , reducing its rigidity. Therefore, although the rigidity of the flange 410 itself changes in size in the direction of rotation, the rigidity of the peripheral wall 403 and the working window 4
Due to the influence of 04, differential gear case 4
As for the flange 410 forming a part of 00, the rigidity at each position in the rotation direction is uniform.

Therefore, the rigidity of the differential gear case 400 including the ring gear 420 is uniform in the rotational direction.

Next, the action will be explained.

The transmission in Figure 3 shows the neutral position, and the input shaft 1 is connected from the engine via the clutch.
The rotational force transmitted to input shaft 100 causes first speed gear 110, reverse gear 160, and second speed gear 120 to rotate together with input shaft 100, so that first speed main gear 210 and second speed main gear 220 also rotate at all times. However, at this neutral position, 3rd gear 1
No rotational force is transmitted to 30, 4th gear 140, 5th gear 150, and reverse idler gear 360, and 1st gear main gear 210 and 2nd gear main gear 220
Since the main shaft 200 is only idling, the rotational force of the engine has not yet been transmitted to the main shaft 200.

Therefore, when shifting to the forward 1st gear position, 1-2
Speed synchronizer 211 operates to the first speed side and transmits the rotational force of first speed main gear 210 to main shaft 200 via this synchronizer 211 . In this way, the main shaft 200 rotates due to the gear ratio between the first speed gear 110 and the first speed main gear 210, and rotational force is transmitted from the output gear 270 that rotates together with the main shaft 200 to the ring gear 420, thereby decelerating the differential gear case 400. and rotate. And differential gear case 40
0, the pinion mate shaft 4
30 rotates around its longitudinal center to rotate the pinion gear 440 on a circular orbit, thereby rotating both side gears 450 while allowing differential movement between them. The rotation of this side gear 450 is directly transmitted to the drive wheels (front wheels) via the drive shaft.

Furthermore, when shifting to the second forward speed position, the 1st-2nd speed synchronizer 211 operates to the 2nd speed side, and the rotational force of the 2nd speed main gear 220 is transmitted to the main shaft 200 via this synchronizer 211. Thus, the main shaft 200 rotates depending on the gear ratio between the second speed gear 120 and the second speed main gear 220.
Next, when shifting to the third forward speed position, the 3rd-4th speed synchronizer 131 operates to the 3rd speed side, causing the input shaft 100 and the 3rd speed gear 130 to rotate together. The rotational force of the 3rd speed gear 130 is transmitted to the main shaft 200 via the 3rd speed main gear 230 that is constantly meshed with the third speed gear 130. Depending on the shift to the 4th forward speed position, the 3rd-4th speed synchronizer 131 operates to the 4th speed side to shift the input shaft 100 and 4th speed.
The speed gear 140 is rotated together. Therefore, the rotational force of 4th speed gear 140 is transmitted to main shaft 200 via 4th speed main gear 240. Furthermore, when the gear is shifted to the 5th forward speed position, the 5th speed synchronizer 151 operates to integrally rotate the input shaft 100 and the 5th gear 150.
The rotational force of 0 is transmitted to the main shaft 200 via the 5th speed main gear 250. The rotational force of the main shaft 200 at each of these shift positions is transmitted to the driving wheels via the differential device in the same manner as described above.

Furthermore, when shifted to the reverse position, the reverse idler gear 360 slides on the reverse idler gear shaft 300 to the position indicated by the chain line in FIG.
mesh with. As a result, the rotational force of the reverse gear 160 is transmitted to the reverse main gear 260 via the reverse idler gear 360, and this rotational force is further transmitted to the main shaft 200, which rotates integrally with the coupling sleeve 212 on which the reverse main gear 260 is formed. transmitted to. In this case, a reverse idler gear 360 is provided in the rotational force transmission path.
is interposed, so the main shaft 200 is
The rotation is in the opposite direction to that in the case of the first to fifth forward speeds. Then, the rotational force of the main shaft 200 is transmitted to the drive wheels through the same path as described above, but the rotation direction is reversed.

Next, input shaft 100 and 3rd gear 1
To explain the lubrication between 30, 4th gear 140, and 5th gear 150, the lubricant supplied to the gap 25 through a path (not shown) is introduced into the axial hole 170 from the pipe 41 of the lubricant guide member 4. Ru. The lubricating fluid passes from the axial hole 170 to the radial holes 171, 172, and 173, respectively, to each gear 1.
30, 140, 150 and input shaft 10
0 to lubricate each friction part.
Here, since the tip of the pipe 41 extends past the radial hole 171 and toward the radial hole 172,
The lubricating fluid is sufficiently supplied even to the radial hole 173 at the back of the axial hole 170.

The reason why the lubricant is sufficiently supplied to the depths of the axial hole 170 when the pipe 41 is extended is because the pipe 41 does not rotate, so centrifugal force is applied to the lubricant inside the pipe 41. This is because the lubricating fluid is not pressed in the centrifugal direction, and its flow resistance becomes extremely small. The lubricant is supplied to the radial hole 171 from the tip of the pipe 41 through the gap between the outer circumference of the pipe 41 and the inner circumference of the axial hole 170.
Since the tip of the pipe 41 and the axial hole 170 are relatively close to each other, sufficient lubricating fluid is supplied to the axial hole 170 even through the gap as described above.

Further, in the case of the differential gear case 400, by forming the thick portion 411 and the thin portion 412 in the flange 410 as described above, the flange 410 forming a part of the differential gear case 400 can be , the rigidity at each position in the rotation direction is uniform. Therefore, the rigidity of the differential gear case 400 including the ring gear 420 becomes uniform in the rotational direction, and as a result, the rigidity of each part of the ring gear 420 fixed to the differential gear case 400 becomes uniform in the rotational direction. Therefore, the main shaft 200
The meshing between the output gear 270 and the ring gear 420 is always the same, and the meshing area does not change depending on the position of the ring gear 420 in the rotational direction. FIG. 8 illustrates this state, and shows a portion A that is engaged and a portion B that is not engaged on the tooth surfaces at the same positions a to h of the ring gear 420 shown in FIG. represents. As is clear from this figure, the ring gear 420 and the output gear 270 mesh uniformly at any position in the rotational direction.

FIG. 7 shows another embodiment, in which the rigidity of the inward flange 422 of the ring gear 420 is changed in the rotation direction. That is, the working window 404 in the inward flange 422
By setting the thickness T of the portion near the peripheral wall 403 to a thick portion 411 as shown in FIG. 7a, and setting the thickness t of the portion near the peripheral wall 403 to a thin portion 412 as shown in FIG. 7b, The same effect as in the previous embodiment is obtained.

In both of the above embodiments, the thick part 411 and the thin part 412 are provided on either the flange 410 of the differential gear case 400 or the inward flange 422 of the ring gear 420. By providing the thick part 411 and the thin part 412 on both the flanges 410 and 422, the combined rigidity of the flanges 410 and 422 is lower than that in the vicinity of the working window 404 in the peripheral wall 403 without the working window. The ring gear 4 is made smaller in the vicinity of the ring gear 4 and fixed to the differential gear case 400.
Of course, the rigidity of the shaft 20 may be made uniform in the direction of rotation.

Further, as means for changing the rigidity of the flanges 410, 422 as described above, not only means for changing the thickness, but also various means such as changing the material of the part, providing slits, etc. can be adopted.

Furthermore, although each of the above embodiments has shown an example in which the ring gear 420 is used in a final reduction gear connected to a transaxle type manual transmission, it is also possible to use the ring gear 420 in a final reduction gear connected to a transaxle type automatic transmission. Alternatively, a ring gear provided in a differential of a front engine rear wheel drive vehicle may be used. In the latter case, the ring gear is constituted by a bevel gear.

〔Effect of the invention〕

As explained above, according to the present invention, the rigidity of at least one of the flange of the differential gear case and the inward flange of the ring gear is increased near the peripheral wall without the working window, rather than near the working window. Because of the small size, the rigidity of the differential gear case including the ring gear becomes uniform in the rotational direction, and as a result, the rigidity of the ring gear fixed to the differential gear case becomes uniform at each part in the rotational direction. Therefore, the ring gear does not undergo partial deformation even when rotational force is input, and always maintains the same meshing state with the gear on the transmission side. Therefore, the meshing area of the ring gear is
Since the area is always the same regardless of the position in the rotational direction, there is no risk of uneven wear or damage to the ring gear, and noise generation is also suppressed.

[Brief explanation of the drawing]

Fig. 1 is a schematic diagram of a differential gear case and a ring gear, Fig. 2 is an explanatory diagram showing the meshing area of each part of the ring gear in Fig. 1, and Fig. 3 is a schematic diagram of a differential gear case and a ring gear.
The figure is an overall sectional view showing one embodiment of the present invention.
The figures are a front view of a differential gear case in half cross section, FIG. 5 is a plan view of the same half cross section, FIG. 6 is a side view of the same half cross section, and FIG. 7 shows another embodiment.
A is a sectional view of a thick part of the flange of the ring gear, and b is a sectional view of a thin part of the flange of the ring gear. 8a to 8h show the first ring gear in the embodiment shown in FIGS. 3 to 6.
FIG. 2 is an explanatory diagram showing the respective meshing areas at the same positions as the positions a to h of the ring gear shown in the figure. DESCRIPTION OF SYMBOLS 1... Clutch housing, 2... Transmission case, 3... Differential housing, 4... Lubricating fluid guide member, 100... Input shaft, 200... Main shaft, 3
00...Reverse idler gear shaft, 400
...Differential gear case, 401...
Peripheral wall, 402... Working window, 410... Flange, 411... Thick wall portion, 412... Thin wall portion, 42
0...Ring gear, 422...Inward flange,
430...Pinion mate shaft, 440...
Pinion gear, 450...Side gear, T, t...
...Thickness.

Claims (1)

[Claims] 1. A differential gear case having a working window opened in a peripheral wall and integrally provided with an outward flange, and a ring gear provided with an inward flange on the inside, wherein the differential gear case and the ring gear and a differential device in which the above-mentioned flanges are connected by fixing them together, and the rigidity of at least one of the above-mentioned flanges is smaller near the peripheral wall without the working window than near the working window. A differential device characterized by: