JP2000240772A - Lubricating oil feeding structure for transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To sufficiently lubricate members such as a bearing and a gear arranged in the outer circumferential side of a rotary shaft even in the case of having the rotary shaft long in its axial length. SOLUTION: An oil pipe 160 is fixedly provided in a lubricating oil channel 121 of a counter shaft 12 to transmission casings 4, 6, communicating holes 161, 162 are provided in the oil pipe 160, and a discharge oil passage 122 is provided in the counter shaft 12. Discharge oil from the hydraulic pump 170 is guided to an opening in one end side of the oil pipe 160 by oil channels 201, 202.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubricating oil supply structure for a transmission, and more particularly to a lubricating oil supply structure for a power transmission rotary shaft member. The present invention relates to a lubricating oil supply structure for performing the above.

[0002]

2. Description of the Related Art Conventionally, a lubricating oil supply structure in a transmission,
Particularly, as a structure for supplying lubricating oil to bearings and gears disposed on the outer peripheral surface of the power transmission rotary shaft, a lubricating oil passage is provided inside the rotary shaft so as to extend in the axial direction. There is a configuration in which a discharge oil passage that opens from the passage to the outer peripheral surface of the rotating shaft is provided, and lubricating oil discharged from the hydraulic pump is guided to the end of the lubrication oil passage through the oil passage. A method of providing a partition having an orifice in the lubricating oil passage to adjust the amount of lubricating oil supplied is also known (see Japanese Patent Publication No. 7-68894).

In such a configuration, the lubricating oil can be guided in the axial direction of the rotary shaft by the lubricating oil passage, and is provided on the way by the discharge pressure of the hydraulic pump and the centrifugal force generated by the rotation of the rotary shaft. Since the lubricating oil can be discharged from the discharged oil passage to the outside of the shaft, it is possible to efficiently lubricate members such as bearings and gears arranged in the axial direction on the outer peripheral surface side of the rotating shaft.

[0004]

However, in the above configuration, the lubricating oil supplied from the hydraulic pump into the lubricating oil passage is supplied from the end directly connected to the hydraulic pump to the other end. When the rotating shaft is long in the axial direction, sufficient lubricating oil is not supplied to the other end, and the other end of the rotating shaft is discharged. Even if members such as bearings and gears are provided on the side, there is a possibility that they cannot be sufficiently lubricated.

The present invention has been made in view of such a problem, and even if the axial length of the rotary shaft is long, the bearings, gears and the like provided on the outer peripheral surface side of the rotary shaft are provided. It is an object of the present invention to provide a lubricating oil supply structure for a transmission capable of sufficiently lubricating the above members.

[0006]

In order to achieve the above object, a lubricating oil supply structure for a transmission according to the present invention comprises a transmission case (for example, first to third cases 1, 2, 3 in the embodiment). ), A rotatable shaft (for example, the countershaft 12 in the embodiment) rotatably disposed inside
A lubricating oil passage extending axially through the interior of the rotary shaft, a pipe member provided in the lubricating oil passage and having both ends fixed to a transmission case (for example, an oil pipe 160 in the embodiment). , At least one communication oil passage (for example, the communication holes 161 and 1 in the embodiment) that opens from the internal space of the pipe member to the outer peripheral surface of the pipe member and communicates with the lubricating oil passage.
62), at least one discharge oil passage extending in the radial direction of the rotating shaft from the lubricating oil passage and opening to the outer peripheral surface of the rotating shaft, and a lubricating oil supply source at an opening at one end of the pipe member. (For example, oil passages 201 and 202 in the embodiment).

In such a configuration, first, the lubricating oil is supplied to the opening at one end of the pipe member provided in the lubricating oil passage of the rotary shaft. The lubricating oil supplied into the pipe member flows toward the other end of the pipe member, and is discharged from the communication oil passage into the lubricating oil passage under the discharge pressure of the hydraulic pump. The lubricating oil entering the lubricating oil passage is discharged to the outside of the rotating shaft from the discharging oil passage under the action of centrifugal force generated with the rotation of the rotating shaft, and a bearing disposed on the outer peripheral surface side of the rotating shaft. Lubricating parts such as gears and gears. Here, the pipe member is fixed to the transmission case,
Since the lubricating oil in the pipe member is not affected by the centrifugal force generated with the rotation of the rotary shaft, a sufficient amount of lubricating oil in the pipe member is supplied to the other end. Therefore, even when the length of the rotating shaft in the axial direction is long, it is possible to sufficiently lubricate members such as bearings and gears provided on the outer peripheral surface of the rotating shaft.

[0008]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. FIGS. 1 to 4 show the internal structure of a countershaft type transmission equipped with a lubricating oil supply structure according to the present invention, which will be described with reference to these drawings. 2 to 4 are dashed lines AA in FIG.
And a portion divided into three by BB is shown in an enlarged manner. In these figures, the hatching at the cross section is
Not done for clarity.

This transmission is constructed by disposing a transmission gear mechanism in first to third cases 1 to 3 which are integrally arranged side by side from the engine side. A first partition wall 4 is formed in the first case 1, a second partition wall 5 is formed in the second case 2, and a cover wall 6 is formed on the left side of the third case 3 (the side opposite to the engine). I have. A main clutch CL is provided in a clutch installation space 7 formed on the right side (engine side) of the first partition wall 4, and a right end surface 1a of the first case 1 is provided.
Is connected to the engine case. The flywheel FW connected to the engine output shaft ES is located in the clutch arrangement space 7, and the main clutch CL is mounted on the flywheel FW.

The left end face 1b of the first case 1 is
The first space 8 is formed by being surrounded by the first partition wall 4 and the second partition wall 5 in this state, and the input shaft (first shaft) 11 and the counter shaft (second shaft) are formed. A shaft 12) extends in parallel with each other, and a total of seven transmission gear trains are mounted between the shafts 11 and 12.

The input shaft 11 is located at a right intermediate portion.
It is rotatably supported by a bearing 11a held by the first partition wall 4, penetrates through the first partition wall 4, protrudes into the clutch installation space 7, and is engaged with the main clutch CL. The main clutch CL controls engagement and disengagement of power transmission between the engine output shaft ES and the input shaft 11. The left end of the input shaft 11 is rotatably supported by a bearing 11b held on the second partition wall 5. The counter shaft 12 is rotatably supported at its right end by a bearing 12a held by the first partition wall 4, and is rotatably supported by a bearing 12b held by the second partition wall 5 at its left intermediate portion. It projects through the second partition wall 5 to the left. In addition, a circlip 15 for locking the bearing 12a to the first partition wall 4 is attached to the outer periphery of the bearing 12a. Assembling this circlip 15,
An opening for removal is formed in the lower surface of the first case 1, and this opening is covered by the cap 16.

The left end surface 2b of the second case 2 is the third case 3
, And the second space 9 is formed by being surrounded by the second partition wall 5 and the cover wall 6 in this state. The left end of the countershaft 12 penetrating the second partition wall 5 as described above projects into the second space 9, and an output shaft (third shaft) 13 extending in parallel with the second space 9 is provided in the second space 9. Have been. These two shafts 1
Transmission gear trains 28a, 28b meshing with each other
Are attached. Counter shaft 1
2 is a bearing 12c held by the cover wall 6.
It is rotatably supported by. The output shaft 13 is rotatably supported at its right end by a bearing 13a held by the second partition wall 5, and has a bearing 13a held by the cover wall 6 at its middle and left ends.
It is rotatably supported by b and 13c. Note that the left end of the output shaft 13 penetrates through the cover wall 6 and protrudes to the outside, and the protruding portion 14 is connected to the propeller shaft and to the driving wheel.

In the first space 8, the input shaft 11
A total of seven transmission gear trains arranged in parallel between the motor and the countershaft 12 include reverse gear trains 27a, 27b, 27c, LOW arranged in order from the right side in the axial direction.
Gear trains 21a, 21b, 2ND gear trains 22a, 22
b, 6TH gear train 26a, 26b, 5TH gear train 25
a, 25b, 4TH gear trains 24a, 24b, and 3RD gear trains 23a, 23b.

Here, the LOW and 2ND gear trains are respectively driven gears 21a, 21a fixed to the input shaft 11.
22a, and driven gears 21b, 22b rotatably disposed on the counter shaft 12 and always meshing with the drive gears 21a, 22a. Further, synchromesh type LOW and 2ND clutches 31 and 32 for engaging and disengaging the driven gears 21b and 22b and the counter shaft 12 are provided. These clutches 3
The operations of 1 and 32 are performed by moving the 1-2 synchro sleeve 47 in the axial direction. The reverse gear train is rotatably supported by a drive gear 27a fixedly mounted on the input shaft 11 and the first partition wall 4, and has a drive gear 27a.
And an idler gear 27b meshing with the idler gear 2b.
7b and a driven gear 27c that meshes. A reverse clutch 37 of a synchromesh type for engaging and disengaging the driven gear 27c and the counter shaft 12 is provided. The operation of the clutch 37 is performed by moving the reverse synchro sleeve 48 in the axial direction.

On the other hand, the gear train for 3RD to 4TH gear shifting includes a driving gear 23 rotatably disposed on the input shaft 11.
a to 26a, and driven gears 23b to 26b fixed to the counter shaft 12 and always meshing with the corresponding drive gears 23a to 26a. Further, synchromesh type 3RD to 6TH clutches 33 to 36 for engaging and disengaging the drive gears 23a to 26a and the input shaft 11 are provided. These clutches 33 ~
36 is operated by the 3-4 synchro sleeve 45 or 5
-6 is performed by moving the synchro sleeve 46 in the axial direction.

As can be seen from the above configuration, in this transmission, LOW, 2ND to 6TH and the reverse clutches 31 to 37 are selectively operated to select power transmission by one of the transmission gear trains. , It is possible to perform a shift. Such a shift is performed by a driver manually operating a shift lever 41 provided in a driver's seat. The shift mechanism will be described below.

The shift lever 41 is supported by a spherical joint 41b so as to be able to swing back and forth and right and left. The driver grasps the shift knob 41a located at the upper end and moves forward and backward (Y direction in FIG. 1) and left and right (in the plane of FIG. This is referred to as the X direction in the vertical direction). The swing of the shift lever 41 is transmitted to the main shift rod 42,
The main shift rod 42 is rotated by the swing of the shift lever 41 in the X direction, and the main shift rod 42 is moved in the axial direction (the left-right direction in the drawing) by the swing in the Y direction. A selector arm 43 is fixed to the tip of the main shift rod 42, and the tip of the selector arm 43 is
In accordance with the operation of the shift lever 41 in the X direction, the shift lever 41 is selectively engaged with engagement grooves of a plurality of shift pieces described below.

FIG. 5 shows the structure of a shift force transmission system 50 having these shift pieces. The shift force transmission system 50 will be described with reference to FIG. Also,
This transmission is shown in FIG. 6 when looking at the first case 1 with the second case 2 removed, and will be described together with this figure. In FIG. 6, for convenience of explanation, the second
The detent mechanisms 52, 54, 56 provided in the case 2 are also shown.

The shift force transmission system 50 is provided above the first space 8 and has a right end supported by the first partition wall 4 and a left end supported by the second partition wall 5 in the axial direction. 1-2 shift rod 5 that can move freely
1, 3-4 shift fork shaft 53 and 5-6 shift fork shaft 55 are provided. 1-2 shift rod 5
1 is provided with a detent groove 51a, which is positioned by a detent mechanism 52 at three positions of 1ST, neutral, and 2ND. Similarly, 3-4 shift fork shaft 53,
The 5-6 shift fork shaft 55 also has a detent groove 5
3a, 55a are formed, and the detent mechanisms 54, 5
6, positioning is performed at three positions of 3RD, neutral, and 4TH and three positions of 5TH, neutral, and 6TH, respectively. The 1-2 shift rod 51 is provided with a detent 51c.

Further, 1-2 shift rods 51, 3-4
The shift fork shaft 53 and the 5-6 shift fork shaft 55 have 1-2 shift pieces 61 and 3 respectively.
The -4 shift piece 62 and the 5-6 shift piece 63 are fixed, and the reverse shift piece 64 is
It is mounted on the four-shift fork shaft 53 so as to be movable in the axial direction. These shift pieces 61
The selector grooves 61a-64a are formed in the selector grooves 61-64. These selector grooves 61a to 64a are arranged side by side in the horizontal direction, and the tip of the selector arm 43 engages with any of the selector grooves 61a to 64a. By pivoting the shift lever 41 in the X direction in this state, the engagement between the tip of the selector arm 43 and the selector grooves 61a to 64a can be selected. When the shift lever 41 is pivoted in the Y direction, Selector groove 61a selectively engaged as described above.
The shift pieces 61 to 64 having 64a can be moved in the axial direction.

Here, 3-4 shift fork shaft 5
3-4 for the 3 and 5-6 shift fork shafts 55
Shift forks 57 and 5-6 shift forks 58 are attached. However, 3-4 shift fork 57
Is fixed to the 3-4 shift fork shaft 53 and is slidably attached to the 5-6 shift fork shaft 55 in the axial direction. The 5-6 shift fork 58 is fixed to the 5-6 shift fork shaft 55 and slidably attached to the 3-4 shift fork shaft 53 in the axial direction. The 3-4 shift fork 57 engages with the 3-4 synchro sleeve 45 for operating the 3RD and 4TH clutches 33 and 34, and the 5-6 shift fork 58 operates for operating the 5TH and 6TH clutches 35 and 36. -6 is engaged with the synchro sleeve 46. For this reason, the shift lever 4
By the operation of 1, the selector arm 41 is engaged with the selector grooves 62a, 63a of the 3-4 shift piece 62 or the 5-6 shift piece 63, and the 3-4 shift fork shaft 53 or the 5-6 shift fork shaft 55 is pivoted. 3RD ~ 6TH clutch 33 ~
36 can be selectively activated to set any of the corresponding gears.

On the other hand, 1ST and 2ND clutches 31,
1-2 synchro sleeve 47 for operating the M.32
And a reverse synchro sleeve 48 for operating the reverse clutch 37 are located above the counter shaft 12 and below the transmission. For this reason, the 1-2 shift fork 73 and the reverse shift fork 76 which engage with these synchro sleeves 47 and 48 are provided on the lower side of the transmission so that the 1-2 shift fork shaft 71 can be moved in the axial direction. And a reverse shift fork shaft 75. The 1-2 shift fork 73 is fixed to the 1-2 shift fork shaft 71 and is slidably mounted on the reverse shift fork shaft 75 in the axial direction. On the other hand, the reverse shift fork 76 is 1-2 shift fork shaft 71
To be slidable in the axial direction.

If the 1-2 shift fork shaft 71 and the reverse shift fork shaft 75 arranged in this way are moved in the axial direction by operating the shift lever 41, the 1-2 shift fork shaft 71 and the reverse shift fork 76 are moved through the 1-2 shift fork 73 and the reverse shift fork 76. 1-2 to move the synchro sleeve 47 and the reverse synchro sleeve 48 in the axial direction.
ST, 2ND and reverse clutch 31, 32, 37
Can be selectively activated. As described above, the operating force of the shift lever 41 is reduced by the 1-2 shift fork shaft 7.
A 1-2 reversing lever 65 and a reverse reversing lever 66 are disposed on the side of the first space 8 for transmitting the power to the first and reverse shift fork shafts 75, as shown in detail in FIGS.

The reversing levers 65 and 66 are made of long plate materials and are independently swung by a pair of holding ribs 4a and 4b projecting from the first partition wall 4 into the first space 8 in an overlapping state. It is movably supported. Specifically, as can be clearly understood from FIG. 6, a holding hole penetrating the holding ribs 4a and 4b is formed from the outer surface of the first case 1, and the holding pin 67 inserted into the holding structure from the case outer surface. The centers of the reversing levers 65 and 66 are supported and can swing freely. With the reversing levers 65 and 66 thus positioned between the holding ribs 4a and 4b, the reversing levers 65 and 66 can be swingably attached only by inserting the holding pin 67 from the outside. Easy to assemble.

As shown in FIG. 7, the upper end 65a of the 1-2 reversing lever 65 is engaged with a notch groove 51b formed in the 1-2 shift rod 51, and the lower end 65b is connected to the 1-2 shift rod 51.
Locking member 72 fixed to shift fork shaft 71
Are locked in the locking groove 72a. For this reason, when the 1-2 shift rod 51 is moved in the axial direction by the operation of the shift lever 41, the 1-2 shift rod 51 is moved through the 1-2 reversing lever 65.
The shift fork shaft 71 is moved in the opposite direction in the axial direction, the 1-2 synchro sleeve 47 is moved in the axial direction via the 1-2 shift fork 73, and 1ST and 2ND
The clutches 31 and 32 are selectively operated.

As shown in FIG. 8, the reverse reversing lever 66 has an upper end 66a locked in a locking groove 64b formed in the reverse shift piece 64, and a lower end 66b formed in the reverse shift fork shaft 75. It is locked in the notch groove 75a. For this reason, the shift lever 41
When the reverse shift piece 64 is moved in the axial direction on the 3-4 shift rod 53 by the operation of, the reverse shift fork shaft 7 is
5 is moved in the opposite direction in the axial direction, the reverse synchro sleeve 48 is moved in the axial direction via the reverse shift fork 76, and the reverse clutch 37 is operated.

Next, the lubrication system of the transmission will be described. As shown in FIGS. 2 and 3, a lubricating oil passage 111 is provided in the input shaft 11 so as to extend in the axial direction.
A plurality of discharge oil passages 112 extending from the lubricating oil passage 111 in the radial direction of the input shaft 11 and opening to the outer peripheral surface of the input shaft 11 are provided. As shown in FIGS. 3 and 4, a lubricating oil passage 131 is provided in the output shaft 13 so as to extend in the axial direction.
There are provided a plurality of discharge oil passages 132 extending in the radial direction of the output shaft 13 and opening to the outer peripheral surface of the output shaft 13. Here, the outlet openings of both the discharge oil passages 112 and 132 are provided in the vicinity of members such as bearings and gears disposed on the outer peripheral surfaces of the respective shafts 11 and 13.

As shown in FIG. 9, a cylindrical oil chamber 150 is formed in a portion of the second partition wall 5 between the left end of the input shaft 11 and the right end of the output shaft 13. The first and second oil guide members 151 and 152 are attached to the oil chamber 150.

The first oil guide member 151 has a disk-shaped support portion 151a and a cylindrical portion 151b extending vertically from the support portion 151a. The support portion 151a is formed in a circular shape formed on the second partition wall 5. Of the lubricating oil passage 1 of the input shaft 11 while being restrained in the radial direction by being fitted into the concave portion 5a of the input shaft 11 while being pressed to the left by the bearing 11b via the clip C1.
11 is inserted into the opening on the left end side.

The second oil guide member 152 has a disk-shaped support portion 152a and a cylindrical portion 152b extending vertically from the support portion 152a. The support portion 152a is formed on the second partition wall 5. The cylindrical portion 152b is fitted into the circular concave portion 5b to restrain the displacement in the radial direction, and is pressed rightward by the bearing 13a via the clip C2 to be clamped. It is inserted into the right end opening. In addition, as described above, the two oil guide members 151,
152 are mounted on bearings 11b and 13a, respectively.
Since the clips C1 and C2 are used, there is no need to prepare a dedicated product, and the installation is easy.

Here, the opening area of the cylindrical portion 151b of the first oil guide member 151 is
(The reason will be described later). In addition, in order to prevent erroneous assembly of the two oil guide members 151 and 152 having different shapes, the outer diameter of the support portion 151a of the first oil guide member 151 and the concave portion 5a provided in the second partition wall 5 are formed. The inner diameter is
The outer diameter of the support portion 152a of the second oil guide member 152 and the inner diameter of the concave portion 5b provided in the second partition wall 5 are formed larger. The second oil guide member 152
The opening of the cylindrical portion 152b is relatively small,
In order to facilitate such a forming process, it is preferable that the second oil guide member 152 is formed of a resin material.

At the left end opening of the lubricating oil passage 111,
A first end plate 153 having a circular hole formed in the center is press-fitted and attached.
The 51 cylindrical portion 151b is inserted into the circular hole.
The cylindrical portion 151b of the first oil guide member 151 and the circular hole of the first end plate 153 have a slight clearance so as to maintain a non-contact state. 151 and 153 do not interfere with each other.

The right end of the lubricating oil passage 131 has a second end plate 15 having a circular hole at the center.
4 is press-fitted and attached, and the cylindrical portion 152b of the second oil guide member 152 is inserted into the circular hole. The cylindrical portion 152b of the second oil guide member 152 and the circular hole of the second end plate 154 have a slight clearance to maintain a non-contact state, and the output shaft 13
Are rotated around the axis so that the two members 152 and 154 do not interfere with each other.

As shown in FIG. 10, a lubricating oil passage 121 is formed inside the countershaft 12 so as to extend in the axial direction and penetrate therethrough. Oil passages 12 extending to the outer surface of counter shaft 12
2 are provided. The outlet openings of the discharge oil passages 122 are provided near members such as bearings and gears that rotatably support the countershaft 12.

An oil pipe 160 is provided in the lubricating oil passage 122 of the counter shaft 12 so as to extend in the axial direction. As shown in FIG. 10, the oil pipe 160 has a right end press-fitted into a press-fitting hole H formed in the first partition wall 4 and is fixed, and a left end formed by a ring member R press-fitted into the cover wall 6. Since it is mounted with the radial displacement restricted, the stationary state is maintained in the lubricating oil passage 121 even when the counter shaft 12 rotates (see also FIGS. 2 and 4). As shown in FIGS. 2 to 4, the oil pipe 160 has a communication hole 161 at the rightmost end of the lubricating oil passage 121 and a communication hole 162 at a position substantially opposed to the discharge oil passage 122 of the counter shaft 12. (Plurality) are formed.

As shown in FIG. 10, a hydraulic pump 170 for supplying and discharging lubricating oil is provided below the oil chamber 150 (see also FIG. 11). The drive gear 171 of the hydraulic pump 170 is always meshed with the gear 29 of the counter shaft 12, and the hydraulic pump 170 is driven with the rotation of the counter shaft 12, from an oil tank (not shown) via the strainer S and the suction port 172. Suck oil
This is discharged to the discharge port 173 as lubricating oil. Note that the hydraulic pump 170 is provided at such a position because oil discharged from the hydraulic pump 170 is supplied to the input shaft 1.
1, because it can be supplied to any of the output shaft 13 and the counter shaft 12 via a short oil passage (details will be described later).

A part of the lubricating oil discharged to the discharge port 173 is guided to the left end of the oil pipe 160 through the oil passage 201 and the oil passage 202 as shown in FIG. The lubricating oil guided to the left end of the oil pipe 160 flows through the oil pipe 160 to the right end,
A part of the lubricating oil receives the discharge pressure of the hydraulic pump 170 and passes through the communication hole 162 provided in the oil pipe 160 to the outside of the oil pipe 160, that is, the lubricating oil passage 121.
Released into Further, the lubricating oil reaching the right end of the oil pipe 160 is discharged from the communication hole 161 into the lubricating oil passage 121.

The lubricating oil discharged into the lubricating oil passage 121 in this way is subjected to the action of the centrifugal force generated by the rotation of the countershaft 12, from the discharging oil passage 122 provided in the countershaft 12 to the outside of the shaft 12. Will be released. As a result, members such as bearings and gears disposed on the outer peripheral surface side of the counter shaft 12 are lubricated.

Here, the oil pipe 160 is fixed to the first partition wall 4 and the cover wall 6 as described above, and the lubricating oil in the oil pipe 160 receives the action of the centrifugal force generated by the rotation of the counter shaft 12. Without being supplied from the left end to the right end,
It is also possible to supply a sufficient amount of lubricating oil to members such as bearings and gears on the right end side. In addition, many FR type transmissions are laid out by being inclined several degrees so that the rear side is downward from the engine side to the rear wheel side, but in such a case, particularly as described above. The use of a simple oil pipe is effective.

Further, as the opening area of the communication hole 162 provided in the oil pipe 160 is larger, a larger amount of lubricating oil can be discharged from the discharge oil passage 122 located at the opposite position. For this reason, the communication holes 16 corresponding to members (bearings, gears, etc.) requiring more lubricating oil are required.
The opening area of the second communication hole 162 is preferably larger than the opening area of the other communication hole 162. In the case of this transmission, the opening area of the communication hole 162 corresponding to members such as the synchromesh type clutches 31 to 37 and the synchronization sleeves 45 to 48 is formed larger than the opening areas of the other communication holes 162.

Further, a part of the lubricating oil discharged to the discharge port 173 passes through the oil passages 203 and 204 formed in the second case 2 and the third case 3 and the oil chamber 150 described above.
(See FIG. 11). The lubricating oil supplied to the oil chamber 150 is guided by the cylindrical portions 151b and 152b of the first and second guide members 151 and 152 and enters the lubricating oil passage 111 of the input shaft 11 and the lubricating oil passage 131 of the output shaft 13. Distributed and supplied.

The lubricating oil supplied into the lubricating oil passage 111 of the input shaft 11 is discharged from the discharge oil passage 112 to the outside of the input shaft 11 by the action of the centrifugal force generated by the rotation of the input shaft 11, Lubricating members such as bearings and gears disposed on the outer peripheral surface side of 11.
Further, the lubricating oil flowing into the lubricating oil passage 131 of the output shaft 13 is subjected to the action of centrifugal force generated by the rotation of the output shaft 13, and from the discharge oil passage 132 to the output shaft 13.
And lubricates members such as bearings and gears disposed on the outer peripheral surface side of the output shaft 13.

Here, as described above, the opening area of the cylindrical portion 151b of the first guide oil member 151 is larger than the opening area of the cylindrical portion 152b of the second guide member 152. The inflowing lubricating oil is supplied more into the lubricating oil passage 111 of the input shaft 11 than in the lubricating oil passage 131 of the output shaft 13. Thus, the opening area of the cylindrical portion 151b of the first oil guide member 151 is smaller than that of the cylindrical portion 152 of the second oil guide member 152.
b is formed larger than the opening area of the output shaft 13.
The reason why more lubricating oil is supplied to the lubricating oil passage 111 of the input shaft 11 than to the lubricating oil passage 131 is that as shown in FIG. ) Are arranged more on the outer peripheral surface side of the input shaft 11 than on the outer peripheral surface side of the output shaft 13.

As described above, by adjusting the ratio between the opening area of the cylindrical portion 151b of the oil guide member 151 and the opening area of the cylindrical portion 152b of the oil guide member 152, the lubrication supplied to the lubricating oil passage 111 of the input shaft 11 is adjusted. Since the ratio between the amount of oil and the amount of lubricating oil supplied to the lubricating oil passage 131 of the output shaft 13 can be set as desired, the two shafts 11,
This is particularly effective when the distribution of members such as bearings and gears provided on the outer peripheral surface of the thirteen is uneven. Further, in order to supply the lubricating oil into the lubricating oil passage 111 of the input shaft 11 and the lubricating oil passage 131 of the output shaft 13, the lubricating oil is supplied to one oil chamber 150 provided between the shafts 11 and 13. Since the lubricating oil may be guided, the configuration becomes compact as compared with the case where lubricating oil is separately supplied to both lubricating oil passages 111 and 131.

As described above, the first end plate 153 and the cylindrical portion 151b of the first oil guide member 151 are provided.
The clearance between the second end plate 153 and the second
Since the clearance between the oil guide member 152 and the cylindrical portion 152b is very small, the input shaft 11
The lubricating oil flowing backward from the lubricating oil passage 111 and the lubricating oil passage 131 of the output shaft
13 is prevented from flowing out. As a result, the lubricating oil supplied to the two lubricating oil passages 111 and 131 is reliably discharged from the discharge oil passages 112 and 132.

A part of the lubricating oil discharged from the discharge port 173 is sent to the shower pipe 180 through an oil passage 205 provided in the second case 2 as shown in FIG. As shown in FIGS. 12 and 6, the shower pipe 180 is provided on the side between the input shaft 11 and the output shaft 13 and almost in parallel with the shafts 11 and 13. When lubrication oil is supplied, lubricating oil is ejected from a plurality of ejection ports 181 provided on the side like a shower, and a member (particularly, a meshing portion of gears) disposed on the outer peripheral surface side of both shafts 11 and 13 is provided. ) Can be lubricated.

The shower pipe 180 shown in FIG.
13 is supported by a support member 182 that rotatably supports one end of the idler gear 27b, as shown in FIG. 13, and is guided from the left to the right in FIG. The lubricating oil is supplied to the support member 18.
Bearings 185, etc., which are discharged from the lubricating oil passages 182a and 182b formed in the inside 2 and the lubricating oil passage 183 and the discharge oil passage 184 provided in the idler gear 27b into the idler gear 27b and rotatably support the idler gear 27b. It can be lubricated.

[0048]

As described above, in the lubricating oil supply structure for a transmission according to the present invention, the pipe member is provided in the lubricating oil passage of the rotary shaft, and the lubricating oil supplied from the opening at one end of the pipe member is provided. By discharging the oil to the outside of the rotary shaft through the communication oil passage provided in the pipe member and the discharge oil passage provided in the rotary shaft, members such as bearings and gears disposed on the outer peripheral surface side of the rotary shaft can be removed. Although the lubrication is performed, the pipe member is fixed to the transmission case, and the lubricating oil in the pipe member does not receive the action of centrifugal force generated with the rotation of the rotating shaft. A sufficient amount of oil is supplied to the other end. Therefore, even when the length of the rotating shaft in the axial direction is long, it is possible to sufficiently lubricate members such as bearings and gears provided on the outer peripheral surface of the rotating shaft.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing an internal configuration of a countershaft type transmission provided with a lubricating oil supply structure according to the present invention.

FIG. 2 is a sectional view showing an internal configuration of a right side portion of the transmission.

FIG. 3 is a sectional view showing an internal configuration of an intermediate portion of the transmission.

FIG. 4 is a cross-sectional view showing an internal configuration of a left portion of the transmission.

FIG. 5 is a plan sectional view showing a configuration of a shift force transmission system of the transmission.

FIG. 6 is a cross-sectional view showing the inside of the transmission and a configuration of a shift force transmission system as viewed from an engine side.

FIG. 7 is a cross-sectional view showing a configuration around a 1-2 reversing lever constituting the shift force transmission system.

FIG. 8 is a cross-sectional view showing a configuration around a reverse reversing lever constituting the shift force transmission system.

FIG. 9 is a cross-sectional view showing members constituting an oil chamber.

FIG. 10 is a sectional view showing a configuration near a counter shaft.

FIG. 11 is a cross-sectional view showing an internal configuration of the transmission including the hydraulic pump when viewed from an engine side.

FIG. 12 is a diagram showing a configuration of a shower pipe.

FIG. 13 is an enlarged view of a portion XIII in FIG.

[Explanation of symbols]

1, 2, 3 First, second, third case (transmission case) 12 Counter shaft (rotating shaft) 121 Lubricating oil passage 122 Discharge oil passage 160 Oil pipe (tube member) 161, 162 Communication hole (Communication oil passage) ) 170 Hydraulic pump (lubricating oil supply source) 201, 202 Oil passage

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Seiichi Okubo 1-4-1, Chuo, Wako, Saitama Prefecture Inside Honda R & D Co., Ltd. (72) Toshiharu Kumagai 1-4-1, Chuo, Wako, Saitama Prefecture No. F-term in Honda R & D Co., Ltd. (reference) 3J028 EA12 EA13 EB08 EB14 EB33 EB35 FA11 FA54 3J063 AB02 AB55 AC06 BA11 CA01 CB41 CD41 XD03 XD23 XD42 XD43 XD56 XD72 XD73 XE15

Claims (1)

[Claims] A rotating shaft rotatably disposed in a transmission case; a lubricating oil passage extending through the inside of the rotating shaft in an axial direction; and both ends provided in the lubricating oil passage. A pipe member fixed to the transmission case, at least one communication oil path that opens from the internal space of the pipe member to the outer peripheral surface of the pipe member and communicates with the lubricating oil passage, At least one discharge oil passage extending in the radial direction of the rotary shaft and opening to the outer peripheral surface of the rotary shaft, and supplying lubricating oil from a lubricating oil supply source to an opening on one end side of the pipe member. A lubricating oil supply structure for a transmission, comprising: an oil passage for guiding.