JP2002054728A - Oil passage structure of transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simply form an oil passage connected to an oil pump of a transmission without special parts. SOLUTION: An outer rotor 89 and an inner rotor 90 are stored in a recessed part 12 formed by recessing a casing 12 of the transmission, and the side surface is covered with a cover plate 91 (indicated by a chain line) to constitute an oil pump 88. An oil groove 80 formed by recessing the casing 12 is covered with a part of the cover plate 91 to form an oil passage 12j for guiding oil discharged by the oil pump 88 to a part to be lubricated. Thus, the oil passage 12j can be formed by simple machining without special parts.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil passage structure for a transmission having an oil passage connected to the oil pump in a casing of the transmission provided with the oil pump.

[0002]

2. Description of the Related Art An oil pump for supplying lubricating oil and hydraulic oil to various parts of a transmission is housed in a pump chamber formed by recessing a casing of the transmission, and a side face of the pump rotor is covered with a cover plate. The component is known from Japanese Utility Model Laid-Open No. 64-12963.

Conventionally, in such a transmission, an oil passage for supplying oil from a oil pump to a lubricated portion or a hydraulic device is formed by drilling a transmission case,
It was formed by piping a pipe.

[0004]

However, if the oil passage connected to the oil pump is formed by drilling of the transmission case or piping of the pipe, there is a problem that the number of processing steps and the number of parts are increased, resulting in an increase in cost. .

The present invention has been made in view of the above-mentioned circumstances, and has as its object to easily form an oil passage connected to an oil pump of a transmission without requiring any special parts.

[0006]

According to the first aspect of the present invention, there is provided a transmission for forming an oil passage connected to an oil pump in a casing of the transmission having the oil pump. In the oil passage structure, an oil pump is configured by covering a side surface of a pump rotor housed in a pump chamber formed by recessing a casing with a cover plate, and covering an oil groove formed in the casing with a part of the cover plate. Thus, there is proposed an oil passage structure for a transmission, wherein the oil passage is formed.

According to the above construction, the cover plate constituting the oil pump is used to cover the side surface of the pump rotor housed in the pump chamber of the casing, and a part of the cover plate covers the oil groove of the casing so as to cover the oil passage. Therefore, the oil passage can be formed by simple processing without requiring any special parts.

The clutch case 12 of the embodiment corresponds to the casing of the present invention, and the outer rotor 89 and the inner rotor 90 of the embodiment correspond to the pump rotor of the present invention.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

FIGS. 1 to 12 show an embodiment of the present invention. FIG. 1 is a map showing the arrangement of FIGS.
3 is an enlarged view of a portion A in FIG. 1 (a sectional view taken along line 2-2 in FIG. 4), FIG. 3 is an enlarged view of a portion B in FIG. 1 (a sectional view taken along a line 3-3 in FIG. 4), and FIG. 5, FIG. 5 is an enlarged view of a main part of FIG. 4, FIG. 6 is an enlarged view of a main part of FIG. 4, FIG. 7 is a cross-sectional view of the line 7-7 of FIG. 4, and FIG. FIG. 9 is a sectional view taken along line 9-8 in FIG.
9 is a sectional view taken along a line 9; FIG. 10 is a sectional view taken along a line 10-10 in FIG.
1 is a view taken on line 11-11 of FIG. 10, and FIG.
FIG. 13 is a sectional view taken along line -12.

As shown in FIGS. 1 to 4, a manual transmission T for a motor vehicle having six forward speeds and one reverse speed is provided for a vehicle.
A clutch case 12 and a transmission case 13 integrally fastened by a plurality of bolts 11 are provided. A main shaft Sm is rotatably supported by the clutch case 12 and the transmission case 13 via a pair of ball bearings 14 and 15, and a counter shaft Sc is rotatably supported via a roller bearing 16 and a ball bearing 17. The differential case 20 of the differential gear D is rotatably supported via a pair of roller bearings 18 and 19, and the reverse shaft Sr is non-rotatably supported. A clutch C operated by the release fork 50 is housed inside the clutch case 12, and an engine (not shown) and the main shaft Sm are connected via the clutch C.

A main first speed-main reverse gear 21 and a main second speed gear 22 are fixedly mounted on the main shaft Sm. A main third speed gear 23, a main fourth speed gear 24, a main fifth speed gear 25 and a main sixth speed gear are provided. 26 are supported so as to be relatively rotatable. On the counter shaft Sc, a counter first gear 27 and a counter second gear 28 meshing with the main first-main reverse gear 21 and the main second gear 22, respectively, are rotatably supported. , A counter third speed gear 29, a counter fourth speed gear 30, a counter fifth speed gear 31, and a counter sixth speed gear 32 meshing with the main fourth speed gear 24, the main fifth speed gear 25, and the main sixth speed gear 26, respectively, are fixed. .

The first-speed counter gear 27 and the second-speed counter gear 28 are selectively coupled to a counter shaft Sc via a first-second speed-synchronizer 34 operated by a first-second speed shift fork 33. The main third-speed gear 23 and the main fourth-speed gear 24 are a third-speed to fourth-speed shift fork 35.
Is selectively coupled to the main shaft Sm via a third-speed / fourth-speed synchronizing mechanism 36 that operates at the same speed. Main 5th gear 2
The fifth and sixth sixth speed gears 26 are selectively coupled to the main shaft Sm via a fifth to sixth speed synchronization mechanism 38 operated by a fifth to sixth speed shift fork 37.

On the reverse shaft Sr, a reverse driven gear 39 and a reverse drive gear 40 are relatively rotatably supported by two needle bearings 41, 42 and four thrust bearings 43 to 46. The main first speed-main reverse gear 21 always meshes with the reverse drive gear 40
Always meshes with the counter reverse gear 47 fixed to the counter shaft Sc. The reverse driven gear 39 and the reverse drive gear 40 can be connected to each other by a sleeve 49 operated by a reverse shift fork 48.

A final drive gear 51 fixed to the counter shaft Sc meshes with a final driven gear 52 provided on the differential case 20 of the differential gear D. Differential case 20
A pair of differential pinions 54, 54 rotatably supported on pinion shafts 53, 53 fixed to the
Mesh with differential side gears 56 fixed to the shaft ends of the left and right drive shafts 55 penetrating the differential case 20.

When the first speed gear 27 is fastened to the counter shaft Sc by the first speed-second speed shift fork 33, the first speed stage is established, and the second speed gear 28 of the first speed-second speed shift fork 33 is established. Is fastened to the counter shaft Sc, the second speed is established, and the third-speed / fourth-speed shift fork 35 connects the main third-speed gear 23 to the main shaft Sm.
The third speed stage is established, and the third speed-fourth shift fork 35 connects the main fourth speed gear 24 to the main shaft S.
m, the fifth gear is established when the main fifth gear 25 is fastened to the main shaft Sm with the fifth-sixth shift fork 37, and the fifth gear is established with the fifth-sixth shift fork 37. When the main sixth speed gear 26 is engaged with the main shaft Smc, the sixth speed is established.

When the first to sixth speeds are established, the reverse driven gear 39 and the reverse drive gear 40 are disengaged by the reverse shift fork 48 and the main first speed-main reverse gear 21 The reverse driven gear 39 meshing with the reverse drive gear 40 meshing with the counter reverse gear 47
Is rotating relative to. Therefore, the first speed-second speed shift fork 33, the third speed-fourth speed shift fork 35 and the fifth speed-fork
When the reverse driven gear 39 and the reverse drive gear 40 are fastened by the reverse shift fork 48 from the state where the sixth speed shift fork 37 is in the neutral position,
The rotation of the main shaft Sm is the main first speed-main reverse gear 21 → reverse driven gear 39 → sleeve 49
→ Reverse drive gear 40 → Counter reverse gear 4
7, the counter shaft Sc is rotated in the reverse direction, and the reverse gear is established.

As is clear from FIGS. 2, 5 and 7, one end of the reverse shaft Sr is
The other end is fitted into a concave portion 13b having an arc-shaped cross section of a boss portion 13a formed in the transmission case 13 in a circular shape.
Although the central angle of the concave portion 13b having an arc-shaped cross section is less than 180 °, the reverse shaft Sr is connected to the reverse driven gear 39.
In addition, the reverse drive gear 40 is held so as not to fall out of the concave portion 13b due to a meshing reaction force received from the main first speed-main reverse gear 21 and the counter reverse gear 47.

The reverse shaft Sr has a hollow portion 61 penetrating in the axial direction, and a plurality of oil holes 62 penetrating from the hollow portion 61 in the radial direction. A gutter-shaped oil groove 13c is formed on the inner wall surface of the transmission case 13, and the oil groove 13c is formed in the hollow portion 6 of the reverse shaft Sr.
Communicate with 1. The oil groove 13c of the transmission case 13 is inclined downward at a slight angle to guide oil by gravity toward the inlet opening of the hollow portion 61 of the reverse shaft Sr. Since FIG. 2 is a development view of the transmission T, the transmission T is shown upside down such that the bottom of the oil groove 13c faces upward. Six ribs 13d to 13i extend radially from the boss 13a of the transmission case 13, and their outer ends are connected to the inner wall of the transmission case 13. Of the six ribs 13d to 13i, the uppermost rib 13d extends obliquely downward from the inner wall of the transmission case 13 toward the recess 13b that supports the reverse shaft Sr.

A portion of the oil adhering to the inner wall of the transmission case 13 flows in the downwardly inclined oil groove 13c in the direction of arrow a in FIG.
Flows into the hollow portion 61, and another part of the oil is further provided with a rib 13d inclined downward from the inner wall of the transmission case 13.
Flows in the direction of arrow b in FIG. 5 by gravity, and flows into the hollow portion 61 of the reverse shaft Sr from the concave portion 13b. Hollow part 61
The oil inside flows out through the oil holes 62 to the outer periphery of the reverse shaft Sr, and effectively lubricates the needle bearings 41 and 42 and the thrust bearings 43 to 46 supporting the reverse driven gear 39 and the reverse drive gear 40 there. be able to.

As described above, the oil is guided to the hollow portion 61 of the reverse shaft Sr by the oil groove 13c and the rib 13d formed in the transmission case 13, so that the oil is supplied from the oil supply source such as an oil pump to the hollow portion 61 of the reverse shaft Sr. This eliminates the need for a special oil passage for supplying oil, which can contribute to simplification of the structure and cost reduction. In the case where the reverse driven gear 39 and the reverse drive gear 40 are provided on the reverse shaft Sr as in this embodiment, it is particularly effective because more oil is required for lubrication of the bearings. Further, the hollow structure of the reverse shaft Sr can contribute to weight reduction.

As is apparent from FIGS. 4, 6 and 7, the clutch case 12 and the transmission case 13 include the first-speed-second speed shift fork shaft 63, the third-speed fourth-speed shift fork shaft 64, and the fifth-speed-6. The speed shift fork shaft 65 is supported slidably in the axial direction. 1
The second speed shift fork shaft 63, the third speed fourth speed shift fork shaft 64 and the fifth speed sixth speed shift fork shaft 65 have a first speed second speed shift piece 6
The sixth, third and fourth speed shift pieces 67 and the fifth and sixth speed shift pieces 68 are integrally fixed, respectively.
The slider 69 is attached to the low-speed-6-speed shift fork shaft 65.
Are slidably supported in the axial direction.

A shift arm 71 is supported by a shift arm shaft 70 fixed between the clutch case 12 and the transmission case 13 so as to be slidable and swingable in the axial direction. The driving unit 71a provided at one end of the shift arm 71
A first speed-second speed shift piece 66, a third speed-fourth speed shift piece 67, a fifth speed-sixth speed shift piece 68, and a reverse shift piece 69a provided on a slider 69 can be selectively engaged. A shift select arm 73 that operates in conjunction with a change lever operated by a driver is engaged with a driven portion 71b provided at the other end of the shift arm 71. The fifth-speed to sixth-speed shift fork shaft 65 can be stably stopped at a neutral position, a fifth-speed position, or a sixth-speed position by a detent mechanism 74. A similar detent mechanism is provided for the first-second speed fork shaft 63 and the third-speed fourth speed fork shaft 64.

Boss portion 12b provided on clutch case 12
An intermediate portion of a reverse shift lever 76 is pivotally supported via a fulcrum pin 75, and a driven portion 7 formed at one end thereof
6a engages with the notch 69b of the slider 69. Reverse shift fork shaft 77 supported between clutch case 12 and transmission case 13 slidably in the axial direction
, The reverse shift fork 48 is fixed, and a forked drive portion 76b formed at the other end of the reverse shift lever 76 engages with a driven portion 48a formed integrally with the base of the reverse shift fork 48. . The reverse shift fork shaft 77 has a detent mechanism 78
To selectively stop at either the reverse position or the forward position.

Thus, the shift arm 71 is swung about the shift arm shaft 70 to engage with the first speed-second speed shift piece 66, and the first speed-second speed shift fork shaft 6
When the third gear is moved from the neutral position to both sides in the axial direction, the first gear or the second gear is established. Shift arm 71
Is engaged with the third-speed / fourth-speed shift piece 67 and the third-speed / fourth-speed shift fork shaft 64 is moved from the neutral position to both sides in the axial direction, thereby establishing the third speed or the fourth speed. Shift arm 71 is shifted to 5-speed-6-speed shift piece 6
8 and the fifth-speed to sixth-speed shift fork shaft 65
Is moved from the neutral position to both sides in the axial direction, the fifth gear or the sixth gear is established. When the shift arm 71 is engaged with the reverse shift piece 69a of the slider 69 and is moved in the direction of arrow c in FIG.
The reverse shift lever 76 whose driven portion 76a is pressed by the notch 69b of No. 9 swings in the direction of arrow d in FIG. 7, and the reverse shift fork 48 whose driven portion 48a is pressed by the driving portion 76b of the reverse shift lever 76. Is the arrow e in FIG.
, The reverse driven gear 39 and the reverse drive gear 40
Are combined to establish the reverse gear.

Further, since the reverse shift fork 48 is driven by using the reverse shift lever 76 whose intermediate portion is pivotally supported by the fulcrum pin 75, even if the driven portion 48a is formed integrally with the reverse shift fork 48, the fulcrum pin The drive portion 76b of the reverse shift fork 48 is driven by the drive portion 76b of the reverse shift
And the degree of freedom in design is improved.

As described above, since the driven portion 48a to be engaged with the driving portion 76b of the reverse shift lever 76 is constituted by a part of the reverse shift fork 48, the driven portion mounted so as to protrude from the reverse shift fork shaft 77 is provided. Section or reverse shift fork shaft 77
It is not necessary to provide a driven part with a cutout,
This can contribute to a reduction in the number of parts and a reduction in the number of processing steps, and can also prevent a reduction in the rigidity of the reverse shift fork shaft 77.

As is apparent from FIG. 9, the oil pan 8 is provided at the bottom of the clutch case 12 and the transmission case 13.
The strainer case 13j projecting into the oil pan 81 is formed integrally with the transmission case 13. The oil strainer 82 inserted into the strainer case 13j from the opening 13k of the transmission case 13 is fixed by a spring 85 disposed between the oil strainer 82 and the lid 84 fixed to the opening 13k by bolts 83. The oil pan 81 and the inlet side of the oil strainer 82 are connected to the communication hole 1 formed in the lower surface of the strainer case 13j.
It communicates via 3m. A hollow pump shaft 8 is provided between the tip of the strainer case 13j and the clutch case 12.
6 is rotatably supported, and the pump shaft 8
The pump drive gear 87 fixed to 6 meshes with the final driven gear 52.

As is apparent from FIG. 11, a first seating surface 12d formed so as to surround the circular pump chamber 12c is provided on the surface of the clutch case 12 facing the transmission case 13.
And a U-shaped second seat surface 12e surrounding the oil groove 80 formed above the first seat surface 12d. Pump room 12
The oil pump 88 housed in the outer rotor 89 having internal teeth is composed of a trochoid pump.
And an inner rotor 90 having external teeth,
The inner rotor 90 is fixed to the pump shaft 86.

Referring to FIG. 8 together, it is apparent that
First seat surface 12d and second seat surface 1 of clutch case 12
The plate-shaped cover plate 91 covering 2e is fixed to the first seating surface 12d with three bolts 92. The cover plate 91 constitutes one side plate of the oil pump 88, and the pump shaft 86 penetrates a central portion thereof.

As is apparent from FIGS. 9 and 11, an arc-shaped suction port 93 and a discharge port 94 are formed on the side of the oil pump 88 opposite to the cover plate 91, and the suction port 93 is connected to the communication groove 12f. The outlet port of the pump shaft 86 communicates with the outlet port of the pump shaft 86, and the discharge port 94 communicates with the communication groove 12g. Further, referring to FIG. 10, a communication groove 12 g communicating with the discharge port 94 is
h penetrates, one end of which is closed by a blind plug 95.
The other end of the oil passage 12h is connected to the oil groove 80 and the cover plate 9 surrounded by the U-shaped second seat surface 12e via an oil passage 12i.
1 communicate with the oil passage 12j defined by the first and second oil passages. The oil groove 80 surrounded by the U-shaped second seating surface 12e is opened toward the final driven gear 52 which is a lubricated portion.

As is clear from FIGS. 9, 11 and 12, another oil passage 12k passes through the communication groove 12g communicating with the discharge port 94, and one end thereof is closed by a blind plug 96. A relief valve 97 communicating with the oil pan 81 faces the oil passage 12k, and an upper end of the oil passage 12k communicates with the oil supply pipe 98 via the oil passage 12m.

When the pump shaft 86 is rotated by the final driven gear 52 of the differential gear D via the pump driving gear 87, the inner rotor 90 and the outer rotor 89 of the oil pump 88 which mesh with each other rotate to rotate the suction port. Negative pressure is generated at 93. As a result, the oil in the oil pan 81 is sucked into the suction port 93 through the path of the opening 13k of the strainer case 13j → the oil strainer 82 → the inside of the pump shaft 86 → the communication groove 12f (arrows f, g, h in FIG. 9). reference).
The oil discharged from the discharge port 94 of the oil pump 88 is supplied to the oil passage 12h from the communication groove 12g, and then lubricates the final driven gear 52 through the oil passage 12i and the oil passage 12j (arrow i in FIGS. 10 and 11). , J
reference). The oil discharged from the discharge port 94 of the oil pump 88 is supplied to the oil passage 12k from the communication groove 12g, and then lubricates another portion of the transmission T through the oil passage 12m and the oil supply pipe 98 (FIG. 1).
1 and arrow m in FIG. 12). Oil pump 88
When the discharge pressure becomes excessive, the relief valve 97 facing the oil passage 12k is opened, and the excess oil is returned to the oil pan 81 (see the arrow k in FIGS. 11 and 12).

By covering the oil groove 80 formed in the clutch case 12 with a cover plate 91 constituting a side plate of the outer rotor 89 and the inner rotor 90 of the oil pump 88, the oil discharged by the oil pump 88 is a part to be lubricated. Oil path 12 leading to final driven gear 52
Since j is formed, the oil passage 12j can be formed without using a special member, which can contribute to a reduction in the number of parts. In addition, since the oil groove 80 is formed at the same time when the clutch case 12 is cast, special processing such as drilling is not required, and the cost can be reduced.

Although the embodiments of the present invention have been described in detail, various design changes can be made in the present invention without departing from the gist thereof.

For example, in the embodiment, the manual transmission T is exemplified, but the present invention can be applied to an automatic transmission.

In the embodiment, a trochoid pump is exemplified as the oil pump 88. However, other types of pumps such as an internal gear pump, an external gear pump, and a vane pump can be used in addition to the trochoid pump.

Although the oil passage 12j is formed on the downstream side of the oil pump 88 in the embodiment, it may be provided on the upstream side of the oil pump 88. Instead of providing the oil pump 88 on the clutch case 12, It may be provided in the transmission case 13.

The oil passage 12j is not limited to the one for supplying oil for lubrication, and may be one for supplying oil for operating hydraulic equipment.

In the embodiment, the oil passage 12j is opened toward the final driven gear 52, which is a lubricated portion, but it may be a passage communicating with another oil passage.

[0041]

As described above, according to the first aspect of the present invention, the cover plate constituting the oil pump is used by covering the side surface of the pump rotor housed in the pump chamber of the casing. Since the oil passage is formed by partially covering the oil groove of the casing, the oil passage can be formed by simple processing without requiring any special parts.

[Brief description of the drawings]

FIG. 1 is a map showing the arrangement of FIGS. 2 and 3

2 is an enlarged view of a portion A in FIG. 1 (a sectional view taken along line 2-2 in FIG. 4);

3 is an enlarged view of a portion B in FIG. 1 (a sectional view taken along line 3-3 in FIG. 4).

FIG. 4 is a sectional view taken along line 4-4 of FIGS. 2 and 3;

FIG. 5 is an enlarged view of a main part of FIG. 4;

FIG. 6 is an enlarged view of a main part of FIG. 4;

FIG. 7 is a sectional view taken along line 7-7 of FIG. 4;

8 is a sectional view taken along line 8-8 in FIG. 3;

9 is a sectional view taken along line 9-9 in FIG.

FIG. 10 is a sectional view taken along line 10-10 of FIG. 8;

FIG. 11 is a view taken along line 11-11 of FIG. 10;

FIG. 12 is a sectional view taken along line 12-12 of FIG. 8;

[Explanation of symbols]

 T transmission 12 clutch case (casing) 12c pump chamber 12j oil passage 80 oil groove 88 oil pump 89 outer rotor (pump rotor) 90 inner rotor (pump rotor) 91 cover plate

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Shinji Fujimoto 1-4-1 Chuo, Wako-shi, Saitama F-term in Honda R & D Co., Ltd. (Reference) 3J063 AA02 AB02 AC06 BA01 BA11 CA01 CD46 XA22 XD24 XD34 XD43 XD47 XD62 XD72 XD73

Claims (1)

[Claims] In a transmission oil path structure in which an oil path (12j) connected to an oil pump (88) is formed in a casing (12) of a transmission (T) including an oil pump (88), a casing (12) Pump chamber (12)
c) cover the side surfaces of the pump rotors (89, 90) with a cover plate (91) to form an oil pump (88), and to insert an oil groove (80) formed in the casing (12) into the cover plate (89). 91), wherein the oil passage (12j) is formed by covering a part of the oil passage (12j).