JPH10103430A - Gear type transmission structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear type transmission which certainly supplies lubricating oil to the end of the output side of an output shaft without an alternate oil path. SOLUTION: The gear type transmission consists of a gear room where plural pairs of speed change gears and shaft sections Si, So, Sc supporting speed change gears are stored, and a shift gate room 19 accommodating a speed change operating section 18. An oil inflow path 27 leading oil into the shift gate room and an oil outflow path 29 exhausting oil out of the shift gate room are arranged between the gear room and the shift gate room. The shift gate room is placed upward of an output shaft So, the oil inflow path is arranged in the speed change gear side, and the oil outflow path is arranged in the output shaft side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a manually operated gear type transmission structure.

[0002]

2. Description of the Related Art As is well known, in a gear type transmission in which a plurality of transmission gear pairs and a shaft member supporting each transmission gear are housed in a transmission case, the input side of the transmission is usually connected to an engine via a clutch. While connected to the output shaft, the output side is finally connected to a propeller shaft that transmits driving force to the rear wheel side via a sleeve shaft fitted to an end of the output shaft. In general, a shift gate chamber (a shift operation chamber) in which a shift operation section for operating a shift rod by a shift lever is stored above the output shaft.

[0003] The sleeve shaft is usually spline-fitted to the outer periphery of the output side end of the output shaft, and moves back and forth while rotating with the output shaft. Therefore, it is necessary to reliably supply lubricating oil to the sliding portion. Regarding the supply of the lubricating oil to the output shaft side, for example, Japanese Utility Model Laid-Open No. 62-86456 discloses a separate oil path leading from a gear chamber in which a transmission gear train is stored to an output end of the output shaft. Is provided to reliably supply lubricating oil.

[0004]

However, when a separate oil path is provided as in the prior art, the number of parts is increased, and the layout of the transmission is difficult inside the transmission where space is originally limited. Further, there is a problem that an assembling work for the oil path is required, and the structure becomes complicated. Further, in order to enhance the lubrication performance, it is necessary to lower the lubricating oil temperature. However, if a separate oil path is provided, it is impossible to take measures against this point.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned technical problem, and can surely supply lubricating oil to an output end of an output shaft without providing another oil path. The purpose is to:

[0006]

For this reason, the invention according to claim 1 of the present application (hereinafter referred to as a first invention) includes a plurality of transmission gear pairs and a shaft member supporting each transmission gear. In a gear transmission including a gear chamber and a shift operation chamber in which a shift operation unit is housed, an oil introduction passage for guiding oil to the shift operation chamber between the gear chamber and the shift operation chamber;
An oil discharge passage for discharging oil from the speed change operation chamber is provided.

Further, the invention according to claim 2 of the present application (hereinafter referred to as “the invention”)
According to a second aspect of the present invention, in the first aspect, the speed change operation chamber is disposed above the output shaft, and the oil introduction passage is provided on the side of the speed change gear, while the oil discharge passage is provided It is characterized by being provided on the output shaft side.

Further, the invention according to claim 3 of the present application (hereinafter referred to as “the invention”)
According to a third aspect of the present invention, in the first or second aspect, an air bleeding mechanism is provided above the speed change operation chamber.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings, in which the present invention is applied to, for example, a so-called output reduction gear type gear transmission. FIG. 1 is an explanatory longitudinal sectional view schematically showing an overall configuration of a gear transmission TM according to the present embodiment. As shown in this figure, in the transmission TM, the input shaft Si and the output shaft So are arranged so as to be adjacent to each other on the same axis, and below these two shafts Si,
A counter axis Sc is arranged in parallel with So. A plurality of gear pairs 1G to 6G meshing with each other corresponding to each gear position are formed by the input shaft Si and the output shaft S.
o and the counter shaft Sc are provided as a pair.

In the transmission TM, as will be described in detail later, each of the gears 4Gc and 4Go of the reduction gear pair 4G capable of transmitting the rotation of the counter shaft Sc to the output shaft So at a reduced speed is both output from the counter shaft Sc. A so-called output reduction gear type which is configured to rotate integrally with the shaft with the shaft So, and the reduction gear pair 4G is preferably provided at the rear end (the output side) of the counter shaft Sc. End). The transmission TM is mounted on, for example, a so-called FR-type vehicle with an engine installed vertically, and has five forward speeds and one reverse speed.
A direct connection stage for directly connecting the input shaft Si and the output shaft So is configured.

The input side (front end: left end in FIG. 1) of the input shaft Si of the gear transmission TM is a clutch 1
Connected to the engine output shaft (not shown) via
The output side (rear end side: right end side in FIG. 1) is combined with the input side end (front end) of the output shaft So. The output side of this output shaft So (rear end side: right end side in FIG. 1)
Are finally connected to a propeller shaft (not shown) that transmits driving force to the rear wheel side via the sleeve shaft 3.

The clutch housing 4, the transmission case 5, and the extension housing 6 are connected in the front-rear direction to form a case body of the transmission TM. The case body has a plurality of shafts projecting inward from its inner wall. Branch 1
1 to 13 are provided. And these shaft supports 11
To 13, the input shaft Si, the output shaft So and the counter shaft S
The bearings which respectively rotatably support c are provided. The clutch housing 4 and the transmission case 5
A case body in which the extension housing 6 and the extension housing 6 are connected in the front-rear direction forms a “gear chamber in which a plurality of transmission gear pairs and a shaft member that supports each transmission gear” are housed.

The input side of the shaft support 11 on the most input side among the shaft supports 11 to 13 is covered by a front cover 15. Further, a shift gate chamber 19 for housing a connecting portion between the shift lever 2 and the three shift rods 17 is provided on the rear side of the shaft support portion 13 on the most output side,
The shift gate chamber 19 is provided with the shift control cover 1.
6 covers the upper part. The shift gate chamber 19 corresponds to the “shift operation chamber in which the shift operation unit is stored” described in the claims of the present application.

As described above, the transmission TM is driven forward 5
It has a first speed and a reverse speed, and six sets of speed change gear pairs 1G to 6G are provided corresponding to each speed. In the present embodiment, these six gear pairs 1G-
For 6G, for example, a 5-R gear unit is formed by combining a gear pair 5G for fifth speed and a gear pair 6G for reversing, and a gear unit 1G is formed by combining a gear pair 1G for first speed and a gear pair 2G for 2nd speed.
A -2 gear unit, and a 3-4 gear unit by combining the third speed gear pair 3G and the fourth speed gear pair 4G,
Each is configured.

These gear units are arranged, for example, in the order of the 5-R gear unit, the 1-2 gear unit and the 3-4 gear unit from the input side (front side) in the gear train. The 5-R gear unit has a reverse transmission gear pair 6G, the 1-2 gear unit has a second speed transmission gear pair 2G, and the 3-4 gear unit has a fourth speed transmission gear pair (reduction gear pair) 4G. Are arranged on the output side (rear side) of the gear unit. That is, from the input side (front side), the above-mentioned six gear pairs 1G to 6G are provided with a fifth gear pair 5G, a reverse gear pair 6G, a first gear pair 1G, a second gear pair 2G, and a third gear. The gear pair 3G and the fourth speed gear pair 4G are arranged in this order.

In this embodiment, each of the gear pairs 1
As for the gears G to 6G, the gears (counter gears 1Gc to 6Gc) provided on the counter shaft Sc side include, for example, 3Gc and 4Gc gears for 3rd speed and 4th speed integrally rotating with the shaft (counter shaft Sc). While all other counter gears 1Gc, 2Gc, 5Gc
And 6Gc are formed as idle gears rotatable relative to a shaft (counter shaft Sc). Further, in the case of the reversing (reverse) gear pair 6G, as is well known, the fixed gear 6Gi and the idle gear 6Gc are formed by an idle gear (reverse idle gear: not shown).
And the reverse idle gear causes the driven gear to rotate in a direction opposite to that of the forward gear pair.

One of the four-speed gear pair (reduction gear pair) 4G (counter gear 4Gc) has a counter shaft Sc.
Is provided at the rear end (output side end) as a fixed gear that rotates integrally with the shaft Sc.
Go) is provided near a front end (input side end) of the output shaft So as a fixed gear that rotates integrally with the shaft So. The output gear 4Go for the fourth speed is rotated, for example, to the rear end (output side end) of the input shaft Si via a needle bearing attached to the front end (input side end) of the output shaft So. The input shaft Si is freely rotatable relative to the input shaft Si. A reduction gear pair 4G having a predetermined gear ratio is formed by the fourth speed counter gear 4Gc and the output gear 4Go.

That is, each gear 4G of the reduction gear pair 4G capable of reducing and transmitting the rotation of the counter shaft Sc to the output shaft So.
Both c and 4Go rotate integrally with the shaft between the counter shaft Sc and the output shaft So. By laying out the reduction gear pair 4G in this manner, as described above,
A so-called output reduction gear type gear transmission TM is configured. In the output reduction gear type transmission TM, the counter shaft Sc does not run idle in a neutral state such as when idling.

The gear type transmission TM according to the present embodiment
Since the output reduction gear type is adopted, the rotational torque of the input shaft Si is transmitted to the counter shaft Sc without being amplified.
The input load to each of the transmission gears other than Gc is small. Therefore, it is more preferable to reduce the size of these gears by reducing the radial dimension and the tooth width. On the other hand, for the reduction gear pair 4G provided on the most output side of the gear train, the counter shaft S
In view of the fact that the rotation of c is reduced by the gear pair 4G (the rotational torque is amplified) and transmitted to the output shaft So, more preferably, the strength and the strength are higher than those of the conventional input reduction gear type. Rigidity is required, and the tooth width is set to be larger.

Synchromesh devices Ya to Yc are provided between the idler gears so as to selectively connect one of the front and rear idler gears so as to rotate integrally with the shaft. . In this case, the 1-2 gear unit and the 5-
As for the R gear unit, since all the counter gears are idler gears, a 1-2 speed switching synchro Ya for switching between 1st speed and 2nd speed and a 5th speed for switching between reverse speed and 5th reverse speed (reverse). The speed-R switching synchro Yc is provided on the counter shaft Sc. On the other hand, regarding the 3-4 gear unit, since the input gear is an idle gear, a 3-4 speed switching synchro Yb for switching between the 3rd speed and the 4th speed is provided on the input shaft Si. Become. Each of the synchromesh devices Ya to Yc has the same configuration and performs the same operation as a conventionally well-known device, and therefore detailed illustration and description of the structure will be omitted.

In the above configuration, when any of the speeds other than the fourth speed is selected by the switching operation of the shift lever 2, the idle gear of the speed is rotated so as to rotate integrally with the shaft. The counter shaft Sc is driven by rotating with the idler gear being engaged with a pair of fixed gears. And this counter axis Sc
The rotation of the output shaft S is reduced while the rotation of the
transmitted to o. On the other hand, when the shift lever 2 is switched to the fourth speed from another shift speed, the output shaft So is connected to the input shaft Si, so that the input side and the output side are directly connected. ing.

In an output reduction gear type transmission, as described above, the counter shaft S
The rotation speed of c is the same as that of the conventional input reduction gear
Unlike the type (which is always slower than the input shaft and is proportional to the input rotation speed), the speed differs depending on the shift speed, and at a speed higher than a certain level, the speed is increased to be higher than the input shaft Si. As described above, when the rotation speed of the counter shaft Sc is increased, the lubrication condition of the bearing during idling becomes severe for the idle gear that is rotatable relative to the shaft among the gears. In particular, in the case of the idle gear 6Gc (reverse idle gear) of the reversing transmission gear pair, the idle gear Gr rotates in the opposite direction to the rotation of the shaft Sc, and the relative rotation difference with the shaft Sc is reduced. A phenomenon of becoming extremely large occurs. In particular, when the small-diameter gears are idler gears for the first-speed and reverse (reverse) gear pairs 1G and 6G having a large reduction ratio, the idler gears rotate with respect to the shaft at the high speed stage. The relative rotational speed of the bearing becomes very high, and the lubrication conditions of the bearing become particularly severe.

When the rotation speed of the counter shaft Sc is increased as described above, for example, if all the synchromesh devices are arranged on the input shaft, all the transmission gears on the input shaft are idlers that can rotate relative to the shaft. In particular, with regard to the first-speed and reverse (reverse) gear pairs having a large reduction ratio, the small-diameter gears are idler gears on the input shaft. The relative rotation speed at the time becomes extremely high, and there is a possibility that a problem such as seizure may occur in the bearing. In particular, in the case of the reverse idle gear, the phenomenon that the rotation of the shaft rotates in the opposite direction to the rotation of the shaft due to the action of the idle gear, and the relative rotation difference with the shaft becomes extremely large occurs.

For this reason, in the present embodiment, a 5-speed-R switching synchro Yc for switching between the 5th speed and the reverse gear (reverse), and a 1-2-speed switching synchro Ya for switching between the 1st and 2nd speeds are provided. Are arranged on the counter Sc axis, and the small-diameter gears 6Gi and 1Gi of the reverse gear pair 6G and the first-speed gear pair 1G are both provided as fixed gears that rotate integrally with the input shaft Si. It rotates at a constant rotational speed (the rotational speed of the input shaft Si) regardless of the gear position. Further, the large-diameter gears 6Gc and 1Gc provided on the counter shaft as idler gears have a lower relative rotation speed with respect to the counter shaft, so that both the synchromesh devices Ya, Yc
Are arranged on the input shaft Si, the idler gears of the reverse gear pair 6G and the first speed gear pair 1G and the input shaft S
Such a large relative rotation speed difference as occurs with i does not occur.

In the gear type transmission TM according to the present embodiment, the transmission T
M case body (specifically, mission case 5
The lubricating oil is stored to a certain level (see the two-dot chain line in FIG. 1) in the lower portion of the extension housing 6 and the meshing portions of the transmission gear pairs 1G to 6G and the idler gears 1Gi to 3Gi, 5Gi and 6G
Supply of the lubricating oil to the bearing portion i or other parts requiring lubrication is performed by using the lubricating oil stored in the lower part of the inside of the above-mentioned case body by the gear provided on the counter shaft Sc which is the lower shaft. It is performed by turning it up with rotational force.

At this time, most of the scrubbed lubricating oil collides with the inner wall of the case body and falls along this inner wall to some extent, so that heat is deprived and cooled to some extent. It is supplied to necessary places. In the case of the transmission TM according to the present embodiment, the transmission TM is attached to the vehicle body in a state where it is slightly inclined in the front-rear direction, and the oil level of the lubricating oil is also inclined in a stationary state accordingly.

When lubricating oil is supplied by such a method, as described above, the stirring resistance of the oil (lubricating oil) generated by the rotation of the counter shaft Sc and the counter gear is reduced to suppress an increase in the oil temperature. Therefore, it is preferable to reduce the amount of lubricating oil as much as possible within a necessary limit. In particular, in the case of the present embodiment, since it is of the output reduction gear type, as described above, the counter in the high speed stage is used. The number of rotations of the shaft is considerably higher than in the case of the input reduction gear type, and a reduction in the amount of lubricating oil is more strongly required.

In the transmission TM according to the present embodiment, as described above, the input shaft Si and the output shaft So are arranged so as to be adjacent to each other on the same axis, and as shown in detail in FIG. The output side end of the shaft Si is supported on the case body of the transmission TM via the bearing Bo1 and is combined with the input side end of the output shaft So provided with the reduction gear 4Go, and is disposed between the two. For example, needle bearing Bi2
As a result, the output shaft So is rotatably supported on the input end of the output shaft So. And the output shaft So
The lubricating oil is forcibly supplied from the oil hole 49 provided on the output shaft So to the needle bearing Bi2 included in the input side end of the needle bearing Bi.

As described above, in the above-described gear type transmission TM of the output reduction gear type, the radial dimension and the tooth width of each transmission gear other than the reduction gear 4Gc are reduced. Although the size of the reduction gear pair 4G provided at the most output side of the gear train is considerably reduced, the counter shaft S
Since the rotation of the gear c is reduced by the gear pair 4G (the rotational torque is amplified) and transmitted to the output shaft So, higher strength and rigidity are required as compared with the conventional input reduction gear type. , The tooth width is set larger. Further, in the gear type transmission TM of the output reduction gear type, as described above, the rotational speed of the counter shaft Sc is higher than that of the conventional input reduction gear type at a certain high speed or higher. Since the speed is considerably high, the speed reduction gear pair 4G also rotates at a considerably high speed.

Therefore, it is necessary to firmly support both sides of the portion where the reduction gears 4Gc and 4Go of the counter shaft Sc and the output shaft So are provided. For this reason, in this embodiment, the shaft support 1 is provided on the input side and the output side of the reduction gear pair 4G.
2, a partition wall portion formed by the shaft support portion 13 is provided, and the reduction gear chamber 25 is formed by the partition wall portions 12 and 13 and the wall portion of the case body (the transmission case 5 and the extension housing 6) of the transmission TM. The reduction gear pair 4G (counter-side reduction gear 4G) of the counter shaft Sc and the output shaft So is formed on each of the partition walls 12 and 13.
c, bearings Bc2, Bc3 and B respectively supporting the input side and the output side of the portion provided with the output side reduction gear 4Go).
o1 and Bo2 are arranged. Note that the reduction gear chamber 2
5 constitutes a part of the "gear chamber" described in the claims of the present application.

As described above, in the gear type transmission TM of the output reduction gear type, the rotation speed of the counter shaft Sc is high, so that the reduction gear pair 4G rotates at a considerably high speed. . As a result, a certain degree of negative pressure is generated inside the reduction gear chamber 25, so that lubricating oil from the outside is easily drawn into the reduction gear chamber 25. That is, the reduction gear pair 4G is
More preferably, a pump action can be performed in the reduction gear chamber 25.

Then, the counter shaft Sc and the output shaft So
In order to firmly support both sides of the portion provided with the reduction gears 4Gc and 4Go, the bearings Bc2, Bc3 and B
For o1 and Bo2, tapered roller bearings having high load capacity not only in the radial direction but also in the axial direction were used. When this tapered roller bearing is used, as is well known, the action of the centrifugal force accompanying the rotation of the shaft supported by the bearing (that is, the rotation of the bearing inner ring and the rolling element) expands from the reduced diameter side of the bearing inner ring. A flow in the direction toward the radial side occurs, and the lubricating oil is easily drawn in this direction. Thereby, tapered roller bearing B
Output shaft So supported by c2, Bc3 and Bo1, Bo2
As shown by a solid line arrow in FIG. 8, due to the action of the centrifugal force accompanying the rotation of the counter shaft Sc (that is, the rotation of the bearing inner ring and the rolling element), a certain amount of The lubricating oil can be forcibly drawn in and supplied to the reduction gear chamber 25.

More preferably, five counter gear groups 5Gc, 6Gc, 1Gc, 2Gc are arranged five from the input side.
And a transmission case between the oil storage unit 10 corresponding to 3Gc and the oil storage unit corresponding to the counter-side reduction gear 4Gc (that is, the lower part of the reduction gear chamber 25). Shaft support 12 provided on 5
The oil path portion 5a is formed by depressing the lower part of the oil path portion downward. Thereby, the counter gear groups 5Gc, 6Gc,
Oil storage unit 10 corresponding to 1Gc, 2Gc and 3Gc
Is easily drawn into the lower portion inside the reduction gear chamber 25.

On the other hand, more preferably, the reduction gear pair 4
Above G, as can be clearly seen from FIGS. 3 and 4,
Oil receiving means 26 for receiving and collecting the lubricating oil scooped up by the counter reduction gear 4Gc is provided integrally with the case body (the transmission case 5 and the extension housing 6) of the transmission TM. Thus, the lubricating oil scooped up by the reduction gear 4Gc is reliably discharged to the outside of the reduction gear chamber 25 after being received by the oil receiving means 26. In the present embodiment, more preferably, as an oil scraping means for scraping oil toward an oil hole 49 provided in the output shaft So, on the input side surface of the reduction gear 4Go provided in the output shaft So. Fins 50
Are integrally formed. Thus, even if the amount of lubricating oil is reduced to some extent, the lubricating oil is reliably and efficiently supplied to the oil hole 49 provided in the output shaft So, and the needle bearing at the output end of the input shaft Si is provided. It is possible to prevent the seizure of Bi2 and the like.

In the present embodiment, as described above, the clutch housing 4, the transmission case 5, and the extension housing 6 are formed by a case body that is connected in the front-rear direction. As shown in detail in FIG. A gear chamber in which the transmission gear pairs 1G to 6G and the shaft members (the input shaft Si, the output shaft So, and the counter shaft Sc) that support the transmission gears are housed, and are formed on the rear side of the most output-side shaft support portion 13. And a shift gate chamber 19 for accommodating a connecting portion 18 (shift operation portion) between the shift lever 2 and the three shift rods 17.
(Shift operation room) is provided, and between these two rooms,
Oil introduction passage 2 for guiding oil to the shift gate chamber 19
8 and an oil discharge passage 29 for discharging oil from the shift gate chamber 19 are provided.

That is, the shift gate chamber 19 is disposed above the output shaft So, and the oil introduction passage 2
Numeral 8 is formed on the shaft support portion 12 and communicates with the reduction gear chamber 25 (that is, on the side opposite to the transmission gear). On the other hand, the oil discharge passage 29 is formed in an oblique rib 6 a provided on the output side of the extension housing 6 and communicates with the output side end of the output shaft So. A sleeve shaft 3 connected to a propeller shaft (not shown) for transmitting a driving force to the rear wheel side is spline-fitted on the outer peripheral side of the output side end of the output shaft So. It moves forward and backward while rotating with the output shaft So. The oil discharge passage 29 supplies lubricating oil to a sliding portion on the outer periphery of the sleeve shaft 3 through a small hole 31a of a holding member 31 fixed to the output side of the extension housing 6. I have. The relationship between the oil introduction passage 28 and the oil discharge passage 29 is such that the inlet of the oil discharge passage 29 is set lower than the outlet of the oil introduction passage 28 in a horizontal plane (see the broken line in FIG. 5). The discharge passage 29 is set so as to be easily processed from diagonally above, as shown by the dashed line in FIG.

As described above, a part of the lubricating oil discharged from the reduction gear chamber 25 to the outside is supplied into the shift gate chamber 19 through the oil introduction passage 27 provided in the shaft support 13, and 5 and FIG. 6, the shift gate chamber 1
The oil is sent to the oil discharge passage 29 mainly through the space below the connecting portion 18 in the pipe 9, and is supplied to the sliding portion on the outer periphery of the sleeve shaft 3. The other part of the lubricating oil discharged to the outside of the reduction gear chamber 25 is:
It is returned to the speed change gear train via a communication passage 28 provided in the shaft support 12.

Thus, the gear chamber and the shift gate chamber 19
An oil introduction passage 27 for guiding oil to the shift gate chamber 19 and an oil discharge passage 29 for discharging oil from the shift gate chamber 19 are provided between the shift gate chamber 19 and the shift gate chamber 19. It can be used as an oil path, eliminating the need to provide a separate oil path, saving space, and requiring no assembly work.
The structure can be simplified. In this case, in particular, the shift gate chamber 19 is disposed above the output shaft So, and the oil introduction passage 27
Is provided on the transmission gear pair side (the reduction gear chamber 25 side), while the oil discharge passage 29 is provided on the output shaft So side. The lubricating oil can be reliably supplied to the output shaft So via the shift gate chamber 19 to lubricate the sliding portion on the outer periphery of the sleeve shaft 3.

In the present embodiment, the shift gate chamber 19 is covered by the shift control cover 16 and the shift lever 2
A holding plate 32 for holding the ball portion 2a is fixed. As shown in detail in FIG. 7, a sealing member made of an elastic material such as rubber is provided between the holding plate 32 and the shaft portion of the shift lever 2. 33 are provided. A breather hole 33h for bleeding air is formed in the seal member 33, and the breather hole 33h is covered with a cover body 34 that comes into contact with the outer periphery of the seal member 33. Then, as is well known, when the pressure inside the shift gate chamber 19 is increased due to the presence of air,
The air is released to the outside of the transmission TM by pushing and spreading the cover body 34 from the breather hole 33h.

As described above, since the air bleeding mechanism is provided above the shift gate chamber 19, the lubricating oil can be circulated through the shift gate chamber 19 without fail.
The air in the transmission TM can be discharged to the outside relatively quickly, and the breather function of the air bleeding mechanism can be enhanced.

Although the above embodiment has been described with reference to a so-called output reduction gear type gear transmission, the present invention is not limited to such a case. Type, etc.
The present invention can be effectively applied to other types of gear transmissions. In addition, the present invention is not limited to the above embodiments, and without departing from the gist thereof,
It goes without saying that various improvements, modifications, changes in design, and the like are possible.

[0042]

According to the first aspect of the present invention, a gear chamber in which a plurality of transmission gear pairs and a shaft member supporting each transmission gear are accommodated, and a gear operation chamber in which a gear operation unit is accommodated. Between,
Since an oil introduction passage for guiding oil to the shift operation chamber and an oil discharge passage for discharging oil from the shift operation chamber are provided, the shift operation chamber can be used as an oil path for lubricating oil. There is no need to provide an oil path for the body, space is saved, no assembly work is required, the structure can be simplified, and the lubricating oil temperature can be reduced due to the heat dissipation of the case body of the transmission. It can be reduced effectively.

According to the second aspect of the present invention, basically, the same effects as those of the first aspect can be obtained. Particularly, the shift operation chamber is disposed above the output shaft, and the oil introduction passage is provided on the transmission gear pair side, while the oil discharge passage is provided on the output shaft side. When performing the lubrication, the lubricating oil on the side of the transmission gear pair can be reliably supplied to the output shaft side via the transmission operation chamber.

Further, according to the third aspect of the present invention, basically the same effects as those of the first or second aspect can be obtained. In particular, since the air release mechanism is provided above the speed change operation chamber, the breather function of the air release mechanism can be enhanced by reliably flowing the lubricating oil into the speed change operation chamber.

[Brief description of the drawings]

FIG. 1 is an explanatory longitudinal sectional view schematically showing an overall configuration of a gear transmission according to the present embodiment.

FIG. 2 is an enlarged longitudinal sectional view showing a main part on the output side of a gear train of the gear transmission.

FIG. 3 is an end view of the transmission case taken along line CC of FIG. 2;

FIG. 4 is an end view of the extension housing taken along line DD in FIG. 2;

FIG. 5 is an explanatory longitudinal sectional view showing an enlarged main part around a shift gate chamber of the gear type transmission.

6 is an explanatory longitudinal sectional view of the shift gate chamber taken along line FF in FIG. 5;

FIG. 7 is an enlarged longitudinal sectional view showing a breather mechanism of the gear transmission.

[Explanation of symbols]

 1G to 6G: transmission gear pair 19: shift gate chamber 27 ... oil introduction passage 29 ... oil discharge passage 33h ... breather hole Sc: counter shaft Si: input shaft So: output shaft TM: gear type transmission

Claims (3)

[Claims] 1. A gear type transmission comprising: a gear chamber accommodating a plurality of transmission gear pairs and a shaft member supporting each transmission gear; and a gear operation chamber accommodating a gear operation unit, A gear-type transmission structure having an oil introduction passage for guiding oil to the shift operation chamber and an oil discharge passage for discharging oil from the shift operation chamber, between the chamber and the shift operation chamber. . 2. The method according to claim 1, wherein the speed change operation chamber is disposed above an output shaft, and the oil introduction passage is provided on a transmission gear pair side, while the oil discharge passage is provided on the output shaft side. The gear type transmission structure according to claim 1, wherein: 3. The gear type transmission structure according to claim 1, wherein an air release mechanism is provided above the speed change operation chamber.