JP2011064211A - Transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission, capable of reducing agitation resistance in addition to improvement in lubricity. <P>SOLUTION: The transmission 1 includes a supply receiver 92 for supplying lubricating oil scraped upwardly by rotation of a ring gear 80 to lubricating points of a plurality of gears; input shafts 21, 22 which rotatably support drive-side gears 51-57 of the plurality of gears; and a normally-opened clutch 40 for transmitting rotational driving force of a prime motor to the input shafts 21, 22, which puts the prime motor and the input shafts 21, 22 into a connected state when operating force is added to the clutch 40, and puts the prime motor and the input shafts 21, 22 into a released state when no operating force is added to the clutch 40. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a transmission that performs lubrication by scooping up lubricating oil with a transmission gear.

2. Description of the Related Art Some vehicle transmissions that change the driving force of an internal combustion engine or the like perform lubrication by scooping up lubricating oil using a transmission gear. For example, Japanese Patent Laid-Open No. 2001-254811 (Patent Document 1) discloses a lubricating mechanism for a transmission having an oil receiver. This lubrication mechanism receives the lubricating oil scraped up by the transmission gear with an oil receiver, and supplies the lubricating oil to the tooth surfaces of the other transmission gears and the inside of each shaft.

JP 2001-254811 A

In such a lubrication mechanism of the transmission, the transmission gear scoops up the lubricating oil stored in the case, so that a stirring resistance is generated in the transmission gear. This increase in stirring resistance results in power loss of the transmission, which may greatly affect vehicle driving and fuel consumption.

The present invention has been made in view of the above problems, and an object thereof is to provide a transmission capable of reducing the stirring resistance.

In order to solve the above problems, the features of the invention according to claim 1 are:
Case and
A plurality of gears rotatably supported in the case and including a differential ring gear;
A lubricating oil storage area formed in the case, storing the lubricating oil stored in the case, and capable of scooping the stored lubricating oil upward of the ring gear by rotation of the ring gear;
A supply receiver for supplying the lubricating oil scraped upward by rotation of the ring gear to a plurality of lubrication points of the gear;
An input shaft that rotatably supports a driving gear among the plurality of gears;
A clutch that transmits the rotational driving force of a prime mover to the input shaft, and when the operating force is applied to the clutch, the prime mover and the input shaft are connected, and no operating force is applied to the clutch. The normally open clutch that opens the prime mover and the input shaft,
It is to provide.

The feature of the invention according to claim 2 is that in claim 1,
The ring gear is formed so as to surround the periphery of the ring gear from the lubricating oil storage region to the outside of the lubricating oil storage region, and is scraped up by rotation of the ring gear outside the lubricating oil storage region. A lubricating oil holding portion for holding the lubricating oil between the ring gear and allowing the ring gear to scatter the lubricating oil held outside the lubricating oil storage area toward the supply receiver. It is to prepare further.

The invention according to claim 3 is characterized in that in claim 2,
The lubricating oil holding part is composed of two side pieces respectively fixed to a first case part and a second case part constituting the case, and the second case part is fastened to the first case part. And the two side pieces surround the peripheral surface and both side surfaces of the peripheral edge of the ring gear.

A feature of the invention according to claim 4 is that in any one of claims 1 to 3,
It is further provided with a return receiver that collects the lubricating oil scattered by the rotation of the plurality of gears and returns the collected lubricating oil to the vicinity of the ring gear.

The feature of the invention according to claim 5 is that in claim 4,
The return receiver is integrated so that the bottom wall portion of the return receiver protrudes from the inner wall surface of the case so that the collected lubricating oil is returned to the vicinity of the ring gear along the inner wall surface of the case. Is formed.

The invention according to claim 6 is characterized in that in claim 4 or 5,
The return receiver is arranged such that the bottom surface of the return receiver collides with the lubricating oil scattered above the case by the rotation of the gear and drops the lubricant below the case.

A feature of the invention according to claim 7 is that in any one of claims 1 to 6,
The input shaft has a first input shaft that rotatably supports a drive-side gear among the plurality of gears, and a second input shaft disposed concentrically with the first input shaft,
A first output shaft and a second output shaft that rotatably support a driven gear among the plurality of gears are arranged in parallel with the input shaft,
The clutch is a dual clutch having a first clutch that transmits a rotational driving force of a prime mover to the first input shaft and a second clutch that transmits the rotational driving force to the second input shaft;
The ring gear of the differential is always rotationally connected to the first output shaft and the second output shaft.

According to the first aspect of the present invention, in a transmission including a normally open type clutch (also referred to as a “normally open type clutch”), the lubricating oil is scraped up by a differential ring gear housed in the case. . Thereby, the ring gear can scoop up the lubricating oil from the lubricating oil storage area, and can scoop up to a position where the supply receiver can collect the lubricating oil. Here, the “normally open type clutch” is a clutch that opens a prime mover such as an engine and an input shaft in a state where no operating force is applied. For example, when the vehicle is traveling at a constant speed, an operating force is always applied to the normally open clutch so that the prime mover and the input shaft are connected. Unlike a normally closed type transmission, the plurality of gears of a transmission having such a normally open clutch do not rotate because no operating force is applied to the clutch when the vehicle is stopped. That is, when the prime mover and the input shaft are in an open state, it is not necessary to supply lubricating oil to the lubrication points of the plurality of gears.

Therefore, in the present invention, the lubricating oil is scraped up by a differential ring gear that is always rotating when the vehicle is running. This makes it possible to scoop up the lubricating oil only when lubrication is necessary. Further, the ring gear in the transmission generally has a large diameter among the plurality of gears accommodated in the case and is often located at the lowest position. Thereby, lubricating oil can be scraped up more efficiently from the lubricating oil storage area | region formed in the bottom part of a case. Also,
The ring gear is configured as a final gear in the transmission. Therefore, the stirring resistance applied to the ring gear is transmitted to the prime mover that is the drive source via a plurality of gears having a reduction ratio corresponding to the shift position. Therefore, the power resistance acting on the prime mover can be reduced by the stirring resistance applied to the ring gear.

Further, with such a configuration, it is possible to efficiently scoop up the lubricating oil and improve the circulation of the lubricating oil in the case. Therefore, the amount of lubricating oil contained in the case is, for example,
You may set so that only the lower part of a ring gear may immerse at the time of vehicle travel. Thereby, since stirring of the lubricating oil by gears other than the ring gear is eliminated, the stirring resistance of the plurality of gears as a whole can be reduced. Therefore, power loss due to agitation resistance can be reduced, and lubricating oil can be sufficiently supplied to the lubrication points of the plurality of gears. Therefore, power transmission efficiency can be improved as a transmission.

According to the second aspect of the present invention, the lubricating oil holding portion is formed so as to surround the peripheral portion of the ring gear rotatably supported in the case, and at least a part of the lower end portion of the lubricating oil holding portion is ,
It is immersed in the lubricating oil stored in the lubricating oil storage area. Therefore, the lubricating oil holding part can scrape more lubricating oil up to a position where the lubricating oil is scattered on the supply receiver in the upper part of the ring gear. Furthermore, by dividing the lubricating oil stored in the lubricating oil storage area by the lubricating oil holding portion, an appropriate amount of lubricating oil can be stored near the periphery of the ring gear.

An interval is provided between the ring gear and the lubricating oil retaining portion for retaining the lubricating oil scooped up from the lubricating oil storage area by the rotation of the ring gear. Furthermore, the lubricating oil holding part enables the ring gear to scatter the lubricating oil held outside the lubricating oil storage area toward the supply receiver. For example, one end of the lubricating oil holding portion is formed so as not to block the lubricating oil scattered from the ring gear to the supply receiver and to surround the vicinity of the peripheral portion of the ring gear from which the lubricating oil is scattered.

By setting it as such a structure, the ring gear can scrape up the lubricating oil of a lubricating oil storage area | region efficiently. As a result, the supply receiver can collect the lubricating oil as the ring gear scatters more lubricating oil, and can efficiently supply the lubricating oil to the lubricating portion. Therefore, the lubricity of the transmission can be improved. Further, in the lubricating oil storage region, the lubricating oil stirred by the ring gear is mainly the lubricating oil that exists between the ring gear and the lubricating oil holding portion. That is, the amount of lubricating oil stirred by the ring gear can be reduced as compared with the conventional case. Thereby, the stirring resistance by a ring gear can be reduced. Therefore, the power loss of the transmission can be reduced. Furthermore, since the lubricating oil can be circulated efficiently in the case, the amount of lubricating oil accommodated in the case can be reduced.

According to the invention which concerns on Claim 3, the lubricating oil holding | maintenance part adapted to the shape of the ring gear which scoops up lubricating oil can be set easily. Here, the case of the transmission may be configured by a first case portion and a second case portion that are fastened at a portion that accommodates the ring gear. Therefore, it is assumed that the lubricating oil holding portion is composed of two side pieces that respectively fix the first case portion and the second case portion. When the second case portion is fastened to the first case portion, the two side pieces surround the peripheral portion and both side surfaces of the ring gear, and constitute a lubricating oil holding portion. For example, the transmission may contain various gears in the same case by changing the gear ratio in practice. In such a case, the configuration as described above can be applied to various types of exchanged gears including ring gears. Further, the shape of the lubricating oil holding portion can be set in accordance with the amount and type of lubricating oil stored in the case.

According to the fourth aspect of the invention, the transmission further includes a return receiver that returns the lubricating oil to the vicinity of the ring gear. A transmission including a supply receiver supplies lubricating oil scraped up above a ring gear to lubrication points of a plurality of gears. Here, in order to reliably supply the lubricating oil accommodated in the case from the lubricating portion, it is preferable to efficiently circulate the lubricating oil in the case. However, the lubricating oil supplied to the lubrication point
For example, after passing through the meshing surface of the gear, it may be scattered in the case by the rotation of the gear. In such a case, the scattered lubricating oil flows along the inner wall surface or bottom portion of the case before returning to the region located in the vicinity of the ring gear in the lubricating oil storage region, and the ring gear that can be scraped up is flown. It takes time to reach the bottom.

In view of this, the splashed lubricating oil is collected and returned to the vicinity of the ring gear by a return receiver further provided in the transmission. As a result, the lubricating oil after passing through the meshing surface of the gear quickly reaches the lower part of the ring gear and is scraped up again by the ring gear. In other words, the return receiver promotes the circulation of the lubricating oil in the case and enables efficient circulation.

According to the invention which concerns on Claim 5, the bottom wall part of a return receiver becomes a structure integrally formed so that it may protrude from the inner wall face of a case. As described above, the lubricating oil that has been supplied to the lubrication point may scatter in the case due to the rotation of the gear and flow along the inner wall surface of the case. Therefore, the return receiver is formed so as to return the collected lubricating oil to the vicinity of the ring gear along the inner wall surface of the case. Thereby, the return receiver can further collect the lubricating oil flowing along the inner wall surface of the case to the bottom of the case. Since this return receiver should just be formed so that the bottom wall part may protrude from the inner wall surface of a case, for example,
The cross section may be L-shaped or U-shaped. With such a configuration, the space between the plurality of gears and the inner wall surface of the case can be effectively used, and the lubricating oil can be quickly returned to the vicinity of the ring gear. Therefore, the return receiver can circulate the lubricating oil more efficiently in the case.

According to the sixth aspect of the present invention, the return receiver is arranged so that the bottom surface of the return receiver collides with the lubricating oil scattered above the case and drops it below the case. As described above, the lubricating oil after being supplied to the lubrication point may be scattered in the case by the rotation of the gear. Here, the lubricating oil may scatter from the lower part of the gear located below the return receiver. Further, in order to quickly return the lubricating oil to the vicinity of the ring gear, it is preferable to shorten the route of the lubricating oil until returning. For example, the lubricating oil splashed from the lower part of the gear can be shortened by preventing the oil from splashing upward above the case and being scattered above the return receiver, rather than being scattered by the return receiver. . Therefore, by causing the lubricating oil scattered from the lower part of the gear to collide with the bottom surface of the return receiver, it is possible to exclude a path for the lubricating oil to be scattered above the case. By arranging the return receiver at such a position, the lubricating oil can be circulated more efficiently in the case.

According to the seventh aspect of the present invention, the transmission is a dual clutch type automatic transmission. The dual clutch type automatic transmission has a first input shaft and a second input shaft.
This mechanism enables high-speed shift change by switching the connection with the prime mover by two clutches. That is, the dual clutch automatic transmission is a transmission that includes a normally open clutch. In this transmission, when one input / output shaft is connected to the prime mover by a clutch during vehicle travel, the other input / output shaft may not be driven to rotate. In such a dual clutch type automatic transmission, the lubricating oil is scraped up by a ring gear that is always rotationally connected to the first output shaft and the second output shaft. As a result, the lubricating oil is always scooped up when the vehicle is traveling, and the lubricity of the transmission can be improved.

1st embodiment: It is a block diagram which shows a part of gear seen from the axial direction of the transmission 1. FIG. FIG. 2 is a schematic cross-sectional view seen from the direction A in FIG. 1, and is a diagram schematically showing a sliding portion and lubricating oil housed in the case 10 with the transmission case 11 and the clutch housing 12 of the case 10 as cross sections. It is the cross-sectional schematic diagram seen from the B direction in FIG. 1 is a skeleton diagram showing an overall structure of a transmission 1. FIG. It is an enlarged view of the CC cross section in FIG. 2nd embodiment: It is a block diagram which shows a one part gear seen from the axial direction of the transmission 101. FIG. It is the cross-sectional schematic diagram seen from the D direction in FIG.

Hereinafter, an embodiment embodying a transmission of the present invention will be described with reference to FIGS. 2, 3, and 6 are views schematically showing a sliding portion and lubricating oil housed in the case 10, with the transmission case 11 and the clutch housing 12 of the case 10 as cross sections.
<First embodiment>
(Configuration of transmission 1)
As shown in FIGS. 1 to 5, the transmission 1 according to the present embodiment is a dual clutch automatic transmission, and includes a first input shaft 21, a second input shaft 22, a first output shaft 31 in a case 10. , The second output shaft 32, the dual clutch 40, the drive gears 51 to 57 (corresponding to the “drive-side gear” of the present invention), the final reduction drive gears 58 and 68, and the driven gear 61 of each gear. -67, reverse gear 70, ring gear 80, and lubrication mechanism 90 are provided. Final reduction drive gear 58,
68, the driven gears 61 to 67, and the reverse gear 70 correspond to the “driven gear” of the present invention.

As shown in FIGS. 2 and 3, the case 10 includes a transmission case 11 (corresponding to the “first case portion” of the present invention) and a clutch housing 12 (corresponding to the “second case portion” of the present invention).
Have The mission case 11 supports each shaft by a plurality of bearings, and contains lubricating oil for lubricating a lubricating portion including sliding portions such as the plurality of gears and sleeves. The clutch housing 12 has an end surface facing the end surface of the transmission case 11 and is fixed by bolt fastening. The clutch housing 12 supports each shaft by a plurality of bearings and accommodates a dual clutch 40 therein.

The first input shaft 21 is formed in a hollow shaft shape and is rotatably supported with respect to the transmission case 11 by a bearing. Further, on the outer peripheral surface of the first input shaft 21, a portion that supports the bearing and a plurality of external tooth splines are formed. The first input shaft 21 is directly formed with a first-speed drive gear 51 and a large-diameter third-speed drive gear 53. The fifth speed drive gear 55 and the seventh speed drive gear 57 are press-fitted by spline fitting into external splines formed on the outer peripheral surface of the first input shaft 21. Further, the first input shaft 21 is formed with a connecting portion that is connected to the first clutch 41 of the dual clutch 40.

The second input shaft 22 is formed in a hollow shaft shape, is rotatably supported on a part of the outer periphery of the first input shaft 21 via a plurality of bearings, and is rotated with respect to the clutch housing 12 by the bearings. It is supported as possible. That is, the second input shaft 22 is disposed so as to be rotatable relative to the first input shaft 21 concentrically. Similarly to the first input shaft 21, a portion for supporting the bearing and a plurality of external gears are formed on the outer peripheral surface of the second input shaft 22. The second input shaft 22 includes
A 2-speed drive gear 52, a large-diameter 4-speed drive gear 54, and a 6-speed drive gear 56 are formed. Further, the second input shaft 22 is formed with a connecting portion that is connected to the second clutch 42 of the dual clutch 40.

The first output shaft 31 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in parallel to the first input shaft 21 in the transmission case 11. In addition, a final reduction drive gear 58 is formed on the outer peripheral surface of the first output shaft 31, and a portion that supports the bearing and a plurality of external splines are formed. The hubs 201 of the gear shift clutches 101 and 103 are press-fitted into the external splines of the first output shaft 31 by spline fitting. The final reduction drive gear 58 is differential (differential mechanism).
Is engaged with the ring gear 80. Further, the first output shaft 31 is formed with a support portion that supports the first-speed driven gear 61, the third-speed driven gear 63, the fourth-speed driven gear 64, and the reverse gear 70 so as to be freely rotatable.

The second output shaft 32 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in parallel to the first input shaft 21 in the transmission case 11. Further, as with the first output shaft 31, a final reduction drive gear 68 is formed on the outer peripheral surface of the second output shaft 32, and a portion for supporting the bearing and a plurality of external splines are formed. The external gear spline of the second output shaft 32 includes gear shift clutches 102 and 10.
Each hub 201 is press-fitted by spline fitting. The final reduction drive gear 68 meshes with a differential ring gear 80. Further, the second output shaft 32 is formed with a support portion that supports the second-speed driven gear 62, the fifth-speed driven gear 65, the sixth-speed driven gear 66, and the seventh-speed driven gear 67 so as to be freely rotatable.

Here, as shown in FIG. 4, the dual clutch 40 includes a first clutch 41 that transmits the rotational driving force of the internal combustion engine E / G (corresponding to the “motor” of the present invention) to the first input shaft 21, And a second clutch 42 that transmits the driving force of the internal combustion engine E / G to the second input shaft 22. The dual clutch 40 is accommodated in the clutch housing 12 on the right side in FIG. 2 and is provided concentrically with the first input shaft 21 and the second input shaft 22. The first clutch 41 is the first
Connected to the connecting shaft portion of the input shaft 21, the second clutch 42 is connected to the connecting shaft portion of the second input shaft 22. The first and second input shafts 21 and 22 are switched to the internal combustion engine E / G by the first and second clutches 41 and 42 based on a control command input from the vehicle control device. , Enabling fast shift changes.

Further, the dual clutch 40 is in a state where one of the first input shaft 21 and the second input shaft 22 is connected to the internal combustion engine E / G when an operating force is applied based on a control command. To do. Then, the dual clutch 40 opens both the first input shaft 21 and the second input shaft 22 with respect to the internal combustion engine E / G when no operating force is applied based on the control command. At this time, the gear shift clutches 101 to 104 are in a neutral position, and any gear including the ring gear 80 does not rotate. As described above, the dual clutch 40 is a normally open type clutch that does not receive an operating force and opens the clutches 41 and 42 when the transmission 1 is in an inoperative state such as when the vehicle is stopped.

The reverse gear 70 is provided on the support portion of the reverse gear formed on the first output shaft 31 so as to be free-wheeling. In the present embodiment, the reverse gear 70 is always meshed with a small-diameter gear 62 a formed integrally with the second-speed driven gear 62.

Each of the gear shift clutches 101 to 104 includes a hub 201 and a sleeve 202. The hub 201 has a hollow disk shape formed with internal splines and external splines, and is press-fitted into the external splines of the first output shaft 31 or the second output shaft 32 by spline fitting. The sleeve 202 meshes with an external spline of the hub 201 so as to be slidable in the axial direction with respect to the hub 201, and when the sleeve 202 is slid, the driven gears 61 to 6 of the shift stage.
7 or the synchro gear portion of the reverse gear 70 can be engaged. That is, the sleeve 202 is
By sliding in the axial direction, switching between a meshing state and a non-meshing state with a synchro gear (not shown) provided in the driven gears 61 to 67 of the shift stage or the reverse gear 70,
It has a role of selectively connecting the driven gears 61 to 67 or the reverse gear 70 to the first output shaft 31 and the second output shaft 32.

As shown in FIG. 1, the ring gear 80 meshes with the final reduction drive gear 58 and the final reduction drive gear 68, and is always rotationally connected to the first output shaft 31 and the second output shaft 32.
The ring gear 80 has a larger diameter and a larger number of teeth than the final reduction drive gears 58 and 68.
The ring gear 80 is connected to a drive wheel via a rotary shaft 80a as a shaft body supported by the case 10 and a differential mechanism (not shown). That is, the differential ring gear 80 is configured as a final gear in the transmission, and is a gear that always rotates when the vehicle travels. Further, the ring gear 80 is located below the other gears. At least a part of the ring gear 80 is immersed in the lubricating oil stored at the bottom of the mission case 11 so that the lubricating oil can be scraped up.

The lubricating mechanism 90 includes a lubricating oil storage area 91, a supply receiver 92, a separator 93 (corresponding to the “lubricating oil holding portion” of the present invention), and a return receiver 94. The lubricating oil storage area 91 is an area for storing lubricating oil at the bottom of the mission case 11 as shown in FIGS. Further, a part of the lubricating oil storage area 91 is partitioned by a lower portion by a separator 93. The lubricating oil storage area 91 can scrape up the stored lubricating oil upward of the ring gear 80 by the rotation of the ring gear 80. The lubricating oil scraped up by the ring gear 80 scatters at the top of the ring gear 80 and is collected by the supply receiver 92. In the present embodiment, the amount of lubricating oil stored in the mission case 11 is set so that only the lower part of the ring gear 80 is immersed when the vehicle travels when the oil level of the lubricating oil storage area 91 is lowered. Has been.

The supply receiver 92 is fixed to the upper part of the case 10 by bolt fastening and is a separate member from the transmission case 11. The supply receiver 92 includes a ring gear 8 as shown in FIG.
At one end of the supply receiver 92 located in the zero-axis orthogonal direction, a collecting portion 92a that receives the lubricating oil is formed. Further, the supply receiver 92 is formed with a bowl-shaped flow path 92 b extending in the axial direction of the transmission 1 so that the collected lubricating oil flows to the lubrication location of the transmission 1. In this flow path 92b, a plurality of downflows are provided above the lubrication points so that an appropriate amount of lubricating oil flows down or drops onto the lubrication points including the tooth surfaces of the gears and sliding portions such as the gear shift clutches 101 to 104. A mouth (not shown) is provided.

The supply receiver 92 has a supply port 92 c at the other end of the supply receiver 92. Here, each shaft such as the first output shaft 31 and the second output shaft 32 is formed with a through-hole through which lubricating oil flows. The transmission case 11 is an inflow groove 1 that is an oil passage through which lubricating oil flows into the through holes of the respective shafts in a cover formed integrally with the end of the transmission case 11.
1a is provided. The supply port 92c of the supply receiver 92 is inserted into a horizontal hole that communicates with the inflow groove 11a. The supply receiver 92 causes the lubricating oil to flow from the supply port 92c to the lateral hole of the inflow groove 11a, thereby causing the first output shaft 31 and the second output to pass through the inflow groove 11a.
Lubricating oil is supplied to the through hole of the output shaft 32.

As shown in FIG. 1, the separator 93 is arcuate when viewed from the axial direction of the transmission 1.
The ring gear 80 is formed so as to surround the peripheral edge of the ring gear 80 from the lubricating oil storage area 91 to the outside of the lubricating oil storage area 91 in the peripheral edge of the ring gear 80. The separator 93 is formed in a U shape so as to follow the shape of the axial cross section of the peripheral edge of the ring gear 80. Specifically, the separator 93 is formed in a shape surrounding the peripheral surface and both side surfaces of the ring gear 80 in the peripheral portion of the ring gear 80. That is, the peripheral edge of the ring gear 80 and the separator 93
The distance between and can be maintained at a predetermined distance. The upper end of the separator 93 is formed so as not to block the lubricating oil scattered from the ring gear 80 to the supply receiver 92 and to surround the periphery of the ring gear 80 from which the lubricating oil is scattered.

Further, in this embodiment, the separator 93 is formed in a U-shaped cross section by overlapping the bottom portions of two side pieces 93L, 93R having a L-shaped cross section that can be separated on the left and right sides. As shown in FIG. 2, the left side piece 93 </ b> L and the right side piece 93 </ b> R of the separator 93 have four concave portions 93 on the side part.
a is provided. Further, as shown in FIG. 5, the left-side piece 93L includes four concave portions 9
3a is fastened by bolts 13 in a state of being inserted into four mounting holes 11b formed in the mission case 11, respectively. Similarly, the right piece 93 </ b> R of the separator 93 is fastened by the bolt 13 in a state where the four recesses 93 a are respectively inserted into the four attachment holes 12 b formed in the clutch housing 12.

Then, when the clutch housing 12 is brought into contact with the transmission case 11 and is fixed by bolt fastening, the separator 93 is arranged so that the two side pieces 93L and 93R sandwich the both side surfaces of the ring gear 80 from the left and right sides and face the outer peripheral surface. Assembled into. Thereby, the separator 93 can be easily fixed to the case 10 so as to surround the peripheral surface and both side surfaces of the peripheral portion of the ring gear 80. And since the two side pieces 93L and 93R of the separator 93 are fastened by the bolt 13 in a state in which the concave portion 93a is put in the mounting holes 11b and 12b,
The inner surface of the separator 93 is flat, and the lubricating oil scraped up by the ring gear 80 can flow smoothly.

Further, the lower end of the separator 93 is provided in the lubricating oil storage area 91. That is, the lower part of the separator 93 partitions the lubricating oil stored in the mission case 11 and the lubricating oil stored near the periphery of the ring gear 80 as described above. Thereby, the amount of lubricating oil stirred by the rotating ring gear 80 is set.

The return receiver 94 is a member separate from the mission case 11 that is arranged from the middle to the lower part of the mission case 11 and is fixed by bolt fastening. As shown in FIG. 1, the return receiver 94 is formed in a bowl shape having a U-shaped cross section, and the vertical wall on one side of the U-shape is in contact with the inner wall surface of the mission case 11. It is fixed with. That is, the return receiver 94 is integrally fixed so that the bottom wall portion protrudes from the inner wall surface of the mission case 11.

Further, as shown in FIG. 3, the return receiver 94 has a collecting portion 94 a that receives the lubricating oil at one end of the return receiver 94 that is positioned in the direction orthogonal to the axis of the first-speed driven gear 61. This collection part 94a is supplied to the tooth surfaces of the first-speed drive gear 51 and the first-speed driven gear 61, and collects the lubricating oil scattered from the tooth surfaces of the gears after meshing. Here, the first output shaft 3
The lubricating oil supplied to the through holes provided in the respective shafts such as the first output shaft and the second output shaft flows through the respective shafts and then is supplied to the gear shift clutches 101 to 104 and the like. The supplied lubricating oil lubricates the gear shift clutches 101 to 104 and then the gear shift clutches 101 to 1.
04 will scatter from the peripheral edge. Therefore, the collecting portion 94a of the return receiver 94 collects the lubricating oil scattered from the periphery of the gear shift clutches 101 and 104 disposed adjacent to the first speed driving gear 51 and the first speed driven gear 61 among the gear shift clutches 101 to 104. is doing.

Further, the return receiver 94 is formed with a flow path 94b extending in the axial direction of the transmission 1 so that the collected lubricating oil flows in the vicinity of the ring gear 80. The flow path 94b is fixed in a state where the vertical wall on one side of the U-shape is in contact with the inner wall surface of the mission case 11 so that the collected lubricating oil flows along the inner wall surface of the mission case 11. Has been. Thus, the flow path 94b is configured to further collect the lubricating oil that flows along the inner wall surface of the mission case 11 to the bottom of the mission case 11. The return receiver 94 is
A return port 94 c is formed at the other end of the return receiver 94. The return port 94c is connected to the flow path 9
The lubricating oil flowing through 4b is returned to the region located in the vicinity of the ring gear 80 in the lubricating oil storage region 91.

Here, the collection part 94 a and the return port 94 c of the return receiver 94 are arranged separately from the middle part to the lower part of the transmission 1. Thereby, the flow path 94b of the return receiver 94 that couples each has an inclination angle larger than that of the bottom of the transmission case 11 for the collected lubricating oil. That is, the return receiver 94 collects the lubricating oil splashing from the gear surfaces of the gears or the gear shift clutches 101 and 104 and the lubricating oil flowing down along the inner wall surface of the transmission case 11 and flows the lubricating oil to the vicinity of the ring gear 80. Let me return. In the return receiver 94, the bottom surface, which is the lower surface of the bottom wall portion, has a transmission case 1 that is rotated by the rotation of each gear.
1 is arranged so as to collide with the lubricating oil scattered above 1 and drop it below the mission case 11.

In the return receiver 94, the width of the bottom wall portion protruding from the inner wall surface of the transmission case 11 is appropriately set so that the U-shaped vertical wall on the other side is close to the tooth surface of each gear. As a result, the bottom surface of the return receiver 94 collides with the lubricating oil scattered upward of the transmission case 11 by the rotation of each gear, and prevents the lubricating oil from scattering upward from the return receiver 94. Thus, the return receiver 94 removes the lubricating oil that collided with the bottom surface of the transmission case 1.
1 is dropped below 1 and returned to the lubricating oil storage area 91 at the bottom.

(Operation of transmission 1)
Next, the operation of the transmission 1 according to this embodiment will be described. The vehicle control device outputs a control command to the transmission 1 according to the operation state of the vehicle such as the accelerator opening, the engine rotation speed, and the vehicle speed. The dual clutch 40 receives operation force from the transmission 1 based on a control command, and operates the first clutch 41 and the second clutch of the dual clutch 40 and the gear shift clutches 101 to 104. Further, as described above, when the transmission 1 is in an inoperative state such as when the vehicle is stopped, the first clutch and the second clutch 42 of the dual clutch 40.
Are opened, and each gear shift clutch 101-104 is in a neutral position. That is, no operating force is applied to the dual clutch 40, and no rotational driving force is transmitted to any gear including the ring gear 80. In such a state, it is not necessary to supply lubricating oil to the lubricating part of the transmission 1.

Next, when the internal combustion engine E / G is started when the vehicle is stopped and the shift lever of the transmission is switched to the forward movement position, the vehicle control device detects the sleeve 2 that the gear shift clutch 101 has.
02 is slid to engage the sleeve 202 and the synchro gear portion of the first-speed driven gear 61. At this time, the transmission 1 is operated so that the other gear shift clutches are in the neutral position.
Form a fast stage. Then, when the accelerator opening increases and the internal combustion engine E / G exceeds a predetermined low rotational speed, the control device sets the first clutch 41 of the dual clutch 40 in accordance with the accelerator opening.
Gradually increase the engagement force.

As a result, the driving torque (rotational driving force) is changed from the first clutch 41 to the first input shaft 21, the first speed drive gear 51, the first speed driven gear 61, the gear shift clutch 101, the first output shaft 31, and the final reduction drive gear 58. To the differential ring gear 80 and the vehicle starts to travel at the first speed. Thus, in order to increase the engagement force of the first clutch 41, an operating force is applied to the dual clutch 40, and the internal combustion engine E / G and the first input shaft 21 are connected. In such a state, it is necessary to supply the lubricating oil to the lubrication location of the transmission 1 related to the drive torque transmission path described above.

The vehicle control device first slides the sleeve 202 included in the gear shift clutch 102 when the operation state of the vehicle becomes suitable for the second speed traveling, for example, when the accelerator opening is increased, so that the sleeve 202 and the second speed are shifted. The synchro gear portion of the driven gear 62 is engaged. As described above, the transmission 1 switches the dual clutch 40 from the first clutch 41 to the second clutch 42 and switches to the second speed traveling after the second speed is established. Next, the sleeve 202 of the gear shift clutch 101 is released.

As a result, the drive torque from the second clutch 42 to the second input shaft 22, the second speed drive gear 52,
2-speed driven gear 62, gear shift clutch 102, second output shaft 32, final reduction drive gear 68
Is transmitted to the differential ring gear 80, and the vehicle travels at the second speed.
Thus, in order to increase the engaging force of the second clutch 42, an operating force is applied to the dual clutch 40, and the internal combustion engine E / G and the second input shaft 22 are connected. In such a state, it is necessary to supply the lubricating oil to the lubrication location of the transmission 1 related to the drive torque transmission path described above.

When the second speed is switched, the gear shift clutch 101 is in a neutral state, the first clutch 41 is in an open state, and the rotational speed of the first input shaft 21 is gradually reduced. On the other hand, the first output shaft 31 that supports the first-speed driven gear 61 is always rotated with the rotation of the final reduction drive gear 58 that is always rotationally connected to the ring gear 80. As a result, the support portion of the first speed driven gear 61 is rotated, and the first speed driven gear 61 supported by the support portion is rotated by the frictional force with the support portion. Similarly, in the shift from the third gear to the seventh gear, the vehicle control device sequentially selects the gear according to the operating state of the vehicle and alternately switches the first clutch 41 and the second clutch 42. The vehicle is selected and traveled at a gear position suitable for the state.

And the 3rd speed stage in which the 1st input shaft 21 is connected to the 1st clutch 41, and a gear stage is formed,
At the fifth speed and the seventh speed, the first-speed driven gear 61 is always rotated because it is rotationally connected to the first-speed drive gear 51 formed on the first input shaft 21. Further, in the fourth and sixth speeds where the second input shaft 22 is connected to the second clutch 42 to form a gear stage, the first-speed driven gear 61 is always rotated as in the second speed stage. The final reduction drive gear 58 is rotated by a support portion provided on the first output shaft 31 that rotates. As a result, the first-speed driven gear 61 and the ring gear 80 are always rotating while the vehicle is running.

In addition, the vehicle control device starts the internal combustion engine E / G when the vehicle is stopped, and when the shift lever of the transmission is switched to the reverse position, the sleeve 2 included in the gear shift clutch 103.
02 is slid to engage the sleeve 202 and the synchro gear portion of the reverse gear 70. At this time, the transmission 1 forms a reverse gear so that the other gear shift clutches are in the neutral position. Further, the reverse gear 70 is always meshed with a small diameter gear 62 a formed integrally with the driven gear 62.

As a result, the drive torque from the second clutch 42 to the second input shaft 22, the second speed drive gear 52,
The second speed driven gear 62, the small diameter gear 62a, the reverse gear 70, the gear shift clutch 103, the first output shaft 31, and the final reduction drive gear 58 are transmitted to the differential ring gear 80, and the vehicle starts to reverse. Thus, in order to increase the engaging force of the second clutch 42, an operating force is applied to the dual clutch 40, and the internal combustion engine E / G and the second input shaft 22 are connected. In such a state, the transmission 1 related to the above-described drive torque transmission path.
It is necessary to supply lubricating oil to the lubrication point.

(Effects of transmission 1)
The transmission 1 configured as described above has the following effects.
The lubrication mechanism 90 of the transmission 1 scoops up the lubricating oil by a differential ring gear 80 that is always rotating when the vehicle is traveling. This makes it possible to scoop up the lubricating oil only when lubrication is necessary. Further, the ring gear 80 in the transmission 1 generally has a large diameter among the plurality of gears accommodated in the transmission case 11 and is often located at the lowest position. Thereby, lubricating oil can be scraped up more efficiently from the lubricating oil storage area 91 formed at the bottom of the mission case 11.

The ring gear 80 is configured as a final gear in the transmission 1. Therefore, the stirring resistance applied to the ring gear 80 is transmitted to the prime mover that is the drive source via a plurality of gears having a reduction ratio corresponding to the shift position. Therefore, the power resistance acting on the prime mover can be reduced by the stirring resistance applied to the ring gear 80.

Further, with such a configuration, it is possible to efficiently lift up the lubricating oil and improve the circulation of the lubricating oil in the mission case 11. The amount of lubricant contained in the mission case 11 is set so that only the lower part of the ring gear 80 is immersed when the vehicle is traveling. Thereby, since stirring of the lubricating oil by each gear other than the ring gear 80 is eliminated, the stirring resistance of the transmission 1 as a whole can be reduced. Therefore, power loss due to agitation resistance can be reduced, and lubricating oil can be sufficiently supplied to the lubrication points of each gear. Accordingly, the transmission efficiency of the transmission 1 can be improved.

The separator 93 is formed so as to surround a peripheral portion of the ring gear 80 that is rotatably supported in the mission case 11, and at least a part of the lower end portion of the separator 93 is lubricated in the lubricating oil storage region 91. Soaked in oil. Therefore, the separator 93 can scrape more lubricating oil up to a position where the lubricating oil is scattered on the supply receiver 92 in the upper part of the ring gear 80. Furthermore, the lubricating oil stored in the lubricating oil storage area 91 is separated from the separator 93.
By dividing by the above, an appropriate amount of lubricating oil can be stored in the vicinity of the periphery of the ring gear 80.

An interval is provided between the ring gear 80 and the separator 93 to hold the lubricating oil scooped up from the lubricating oil storage area 91 by the rotation of the ring gear 80. further,
The separator 93 allows the ring gear 80 to scatter the lubricant held outside the lubricant storage region 91 toward the supply receiver 92. For example, one end of the separator 93 is formed so as not to block the lubricating oil scattered from the ring gear 80 to the supply receiver 92 and to surround the periphery of the ring gear 80 that scatters the lubricating oil.

By setting it as such a structure, the ring gear 80 can scoop up the lubricating oil of the lubricating oil storage area | region 91 efficiently. Thereby, the supply receiver 92 can collect lubricating oil by the ring gear 80 splashing more lubricating oil, and can supply lubricating oil efficiently to a lubrication location. Therefore, the lubricity of the transmission 1 can be improved. Further, in the lubricating oil storage area 91, the lubricating oil stirred by the ring gear 80 is mainly the lubricating oil that exists between the ring gear 80 and the separator 93. That is, the amount of lubricating oil stirred by the ring gear 80 can be reduced as compared with the conventional case. Thereby, the stirring resistance by the ring gear 80 can be reduced. Therefore, the power loss of the transmission 1 can be reduced. further,
Since the lubricating oil can be efficiently circulated in the mission case 11, the amount of lubricating oil accommodated in the mission case 11 can be reduced.

Here, the case 10 of the transmission 1 includes a transmission case 11 and a clutch housing 12 that are fastened at a portion where the ring gear 80 is accommodated. The separator 93 has two side pieces 9 fixed to the transmission case 11 and the clutch housing 12 respectively.
It is assumed to be composed of 3L and 93R. When the clutch housing 12 is fastened to the transmission case 11, the two side pieces 93 </ b> L and 93 </ b> R surround the peripheral edge portion and both side surfaces of the ring gear 80 and constitute a separator 93. For example, the transmission 1 may exchange and accommodate various gears in the same mission case 11 due to a change in gear ratio in practice.
In such a case, the configuration as described above can be applied to various types of exchanged gears including the ring gear 80. Further, the shape of the separator 93 can be set in accordance with the amount and type of lubricating oil stored in the mission case 11.

The transmission 1 further includes a return receiver 94 that returns the lubricating oil to the vicinity of the ring gear 80. The transmission 1 including the supply receiver 92 supplies the lubricating oil scooped up above the ring gear 80 to the lubrication points of each of the plurality of gears. Here, in order to reliably supply the lubricating oil accommodated in the mission case 11 from the lubrication location, it is preferable to efficiently circulate the lubricating oil in the mission case 11. However, the lubricating oil supplied to the lubrication location may scatter in the mission case 11 due to the rotation of the gear after passing through the meshing surface of each gear, for example.

In such a case, the scattered lubricating oil flows along the inner wall surface or the bottom of the mission case 11 before returning to the region located in the vicinity of the ring gear 80 in the lubricating oil storage region 91 and can be scraped up. It takes time to reach below the ring gear 80.
Accordingly, the returned receiver 94 collects the scattered lubricating oil, and the ring gear 80.
Return to the vicinity. As a result, the lubricating oil after passing through the meshing surfaces of the respective gears quickly reaches below the ring gear 80 and is scraped up again by the ring gear 80. That is, the return receiver 94 promotes the circulation of the lubricating oil in the mission case 11 and enables efficient circulation.

Further, the bottom wall portion of the return receiver 94 is configured to be integrally formed so as to protrude from the inner wall surface of the mission case 11. As described above, the lubricating oil after being supplied to the lubrication location may scatter in the mission case 11 due to the rotation of the gear and flow along the inner wall surface of the mission case 11. Therefore, the return receiver 94 is configured to return the collected lubricating oil to the vicinity of the ring gear 80 along the inner wall surface of the mission case 11. Thereby, the return receiver 94 can further collect the lubricating oil flowing along the inner wall surface of the mission case 11 to the bottom of the mission case 11.

Since the return receiver 94 only needs to be formed so that the bottom wall portion protrudes from the inner wall surface of the mission case 11, the return receiver 94 may have, for example, an L-shaped cross-section or a U-shape. With such a configuration, the space between the plurality of gears and the inner wall surface of the transmission case 11 can be used effectively, and the lubricating oil can be quickly returned to the vicinity of the ring gear 80. Therefore, the return receiver 94 can circulate the lubricating oil in the mission case 11 more efficiently.

The return receiver 94 is arranged such that the bottom surface of the return receiver 94 collides with the lubricating oil scattered upward of the mission case 11 and falls below the mission case 11. As described above, the lubricating oil that has been supplied to the lubrication location may scatter in the mission case 11 due to the rotation of the gear. Here, the lubricating oil may scatter from the lower part of the gear located below the return receiver 94. In order to quickly return the lubricating oil to the vicinity of the ring gear 80, it is preferable to shorten the route of the lubricating oil until it returns.

For example, the lubricating oil scattered from the lower part of the gear is shortened by preventing the oil from splashing upward from the return receiver 94 rather than from above the mission case 11 and collected by the return receiver 94. can do. Therefore, by causing the lubricating oil scattered from the lower part of the gear to collide with the bottom surface of the return receiver 94, it is possible to exclude a path through which the lubricating oil scatters above the mission case 11. By arranging the return receiver 94 at such a position, the lubricating oil can be circulated more efficiently in the mission case 11.

Further, the transmission 1 has a first input / output shaft 21, 31 and a second input / output shaft 22, 32,
The transmission includes a normally open type dual clutch 40 that switches the connection with the internal combustion engine E / G by two clutches 41 and 42, respectively. A differential ring gear 80 was used as a member for scooping up the lubricating oil in the lubricating oil storage area 91. The ring gear 80 is a gear that always rotates when the vehicle travels, and can always scrape up the lubricating oil during vehicle travel that requires lubrication inside the transmission 1.

Thereby, since the lubricant oil can be stably supplied to the receiver 92, the lubricant oil can be efficiently circulated inside the transmission 1. On the other hand, when the transmission 1 is in an inoperative state such as when the vehicle is stopped, no operating force is applied to the dual clutch 40, and both clutches 41 and 42 are in a released state. That is, the rotation of the ring gear 80 is also stopped. As described above, when the lubrication is unnecessary, the ring gear 80 does not rotate, so that it is possible to prevent unnecessary lubrication of the lubricating oil. Therefore, the stirring resistance by the ring gear 80 is reduced, and the transmission 1
The power loss can be reduced.

<Second embodiment>
A transmission according to a second embodiment will be described with reference to FIGS. Here, the configuration of the second embodiment is mainly different from the transmission 1 of the first embodiment in that it is a dual-clutch automatic transmission, but a mechanical automatic transmission. Along with this, the configuration of sliding parts such as gears in the transmission 101 is different. Since other configurations are the same as those in the first embodiment, detailed description thereof is omitted. Only the differences will be described below.

(Configuration of transmission 101)
As shown in FIGS. 6 and 7, a transmission 101 that is a mechanical automatic transmission is provided in a case 10.
Input shaft 123, output shaft 133, automatic clutch mechanism 143, drive gears 151-1 for each gear stage
56, driven gears 161 to 166 for each shift stage, final reduction drive gear 168, reverse gear 170,
A ring gear 180 and a lubrication mechanism 190 are provided.

The input shaft 123 is formed in a shaft shape and is supported by a bearing so as to be rotatable with respect to the transmission case 11. A small-diameter gear 1 meshed with the outer peripheral surface of the input shaft 123 via a counter gear (not shown) and the first-speed drive gear 151, the second-speed drive gear 152, and the reverse gear 170.
57 is formed directly. Further, on the outer peripheral surface of the input shaft 123, a support portion that supports each gear so as to be freely rotatable and a plurality of external splines are formed. A hub of a gear shift clutch is press-fitted to the external spline of the input shaft 123 by spline fitting, and the third speed drive gear 153 to the sixth speed drive gear 156 are supported on the support portion so as to be freely rotatable.

The input shaft 123 is connected to a crankshaft of an internal combustion engine E / G (not shown) via a clutch, and inputs driving force to the transmission 101. That is, the input shaft 123 is the first of the first embodiment.
It corresponds to the input shaft 21 and the second input shaft 22. A through hole is formed in the input shaft 123 through which lubricating oil for lubricating the support portions of the gears 153 to 156 serving as lubrication points flows.

The output shaft 133 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in the transmission case 11 in parallel with the input shaft 123. Further, on the outer peripheral surface of the output shaft 133, a third speed driven gear 163 to a sixth speed driven gear 166 are provided.
The final reduction drive gear 168 is directly formed. Further, on the outer peripheral surface of the output shaft 133, a support portion that supports the gears 161, 162, and 170 so as to be freely rotatable and a plurality of external splines are formed.

Then, a gear shift clutch hub is press-fitted into the external spline of the output shaft 133 by spline fitting, and the first-speed driven gear 161, the second-speed driven gear 162, and the reverse gear 170 are supported in a freely rotatable manner in the support portion. Has been. The first speed driven gear 161 is disposed on the side opposite to the internal combustion engine E / G side in the axial direction of the output shaft 133. The first-speed driven gear 161 meshes with a first-speed drive gear 151 formed on the input shaft 123 and is always rotationally connected to the input shaft 123.

The output shaft 133 is connected to one of the driven gears supported by the output shaft 133 and one of the drive gears supported by the input shaft 123 to rotate the final reduction drive gear 168 formed on the output shaft 133. And the differential ring gear 180 is rotated to output a driving force from the transmission 101. The output shaft 133 corresponds to the first output shaft 31 and the second output shaft 32 of the first embodiment. Further, a through hole through which the lubricating oil flows is formed inside the output shaft 133.
Then, as in the first embodiment, lubricating oil is allowed to flow through the inflow groove 11a formed in the cover that closes the opening on the side opposite to the internal combustion engine E / G side in the axial direction of the mission case 11. Lubricating oil is supplied to the through holes of the input shaft 123 and the output shaft 133. And the gears 153 to 15 as lubrication points are provided through the through holes of the input shaft 123 and the output shaft 133.
The support portions of 6, 161, 162, and 170 are lubricated.

The automatic clutch mechanism 143 has a clutch that transmits the rotational driving force of the internal combustion engine E / G to the input shaft 123. The automatic clutch mechanism 143 is accommodated in the clutch housing 12 on the left side in FIG. 7 and is provided concentrically with the input shaft 123. Automatic clutch mechanism 14
The clutch 3 is connected to the connecting shaft portion of the input shaft 123, and by switching the connection state between the internal combustion engine E / G and the input shaft 123 based on a control command input from the vehicle control device,
The shift change of each gear stage is enabled. That is, the clutch of the automatic clutch mechanism 143 corresponds to the first clutch 41 and the second clutch 42 of the first embodiment.

Further, the automatic clutch mechanism 143 brings the input shaft 123 into a connected state with respect to the internal combustion engine E / G when an operating force is applied based on the control command. The automatic clutch mechanism 114 opens the input shaft 123 with respect to the internal combustion engine E / G when no operating force is applied based on the control command. At this time, each gear shift clutch is in a neutral position, and any gear including the ring gear 180 does not rotate. Thus, the automatic clutch mechanism 143 is
When the transmission 101 is in an inoperative state such as when the vehicle is stopped, it is a normally open type clutch in which the operating force is not applied and the clutch of the automatic clutch mechanism 143 is opened.

The ring gear 180 is always rotationally connected to the output shaft 133 by meshing with the final reduction drive gear 168. The ring gear 180 is larger in diameter than the final reduction drive gear 168,
And there are many teeth. That is, the differential ring gear 180 is a gear that is disposed on the internal combustion engine E / G side in the axial direction of the output shaft 133 and that always rotates as a final gear in the transmission 101 when the vehicle is traveling. Moreover, the ring gear 180 is located below the other gears. And the lower part of the ring gear 180 is immersed in the lubricating oil stored in the bottom part of the mission case 11, and the lubricating oil can be scraped up. In this way, the ring gear 180 is immersed in the lubricating oil in the lubricating oil storage area 91.

The lubricating mechanism 190 includes a lubricating oil storage area 91, a supply receiver 92, a separator 93,
It has a return receiver 194. Since the lubricating oil storage area 91, the supply receiver 92, and the separator 93 are the same as those in the first embodiment, detailed description thereof is omitted.

The return receiver 194 is a member separate from the mission case 11 that is disposed from the middle stage to the lower stage of the mission case 11 and fixed by bolt fastening. This return receiver 19
As shown in FIG. 6, 4 is formed in a bowl shape having a U-shaped cross section, and is fixed in a state where the vertical wall on one side of the U-shape is in contact with the inner wall surface of the mission case 11. The That is, the return receiver 194 is integrally fixed so that the bottom wall portion protrudes from the inner wall surface of the mission case 11.

Further, as shown in FIG. 7, the return receiver 194 has a collecting portion 194 a that receives the lubricating oil at one end of the return receiver 194 that is positioned in the direction orthogonal to the axis of the sixth speed driven gear 166. The collection unit 194a collects lubricating oil that is supplied to the tooth surfaces of the 6-speed drive gear 156 and the 6-speed driven gear 166 and scatters from the tooth surfaces of the gears after meshing. Here, the lubricating oil supplied to the through holes provided in the respective shafts such as the input shaft 123 and the output shaft 133 flows through the respective shafts, and is then supplied to a gear shift clutch or the like. The supplied lubricating oil scatters from the peripheral portion of the gear shift clutch after lubricating the gear shift clutch. Therefore, the collection unit 194a of the return receiver 194 is configured to include 6 of the gear shift clutches.
Lubricating oil scattered from the periphery of the gear shift clutch disposed adjacent to the high-speed drive gear 151 and the sixth-speed driven gear 166 is collected.

Further, the return receiver 194 has a flow path 194 b extending in the axial direction of the transmission 101 so that the collected lubricating oil flows in the vicinity of the ring gear 180. This flow path 194
b is fixed in a state where the vertical wall on one side of the U-shape is in contact with the inner wall surface of the mission case 11 so that the collected lubricating oil flows along the inner wall surface of the mission case 11. . As a result, the flow path 194b travels along the inner wall surface of the mission case 11 in the mission case 1.
The lubricating oil that flows to the bottom of 1 can be further collected. The return receiver 194 has a return port 194 c at the other end of the return receiver 194. The return port 194c returns the lubricating oil flowing in the flow path 194b to a region located in the vicinity of the ring gear 180 in the lubricating oil storage region 91.

Here, the collection unit 194 a and the return port 194 c of the return receiver 194 are arranged separately from the middle stage to the lower stage of the transmission 101. As a result, the flow path 194 b of the return receiver 194 that connects them has a greater inclination angle than the bottom of the mission case 11 for the collected lubricating oil. That is, the return receiver 194 collects the lubricating oil scattered from the tooth surfaces of the gears or the gear shift clutch and the lubricating oil flowing down along the inner wall surface of the transmission case 11 and flows the lubricating oil to the vicinity of the ring gear 180 and returns it. ing. Further, the return receiver 194 is arranged such that the bottom surface, which is the lower surface of the bottom wall portion, collides with the lubricating oil scattered upward of the transmission case 11 due to the rotation of each gear and falls below the transmission case 11. .

In the return receiver 194, the width of the bottom wall portion protruding from the inner wall surface of the transmission case 11 is appropriately set so that the U-shaped vertical wall on the other side is close to the tooth surface of each gear. As a result, the bottom surface of the return receiver 194 collides with the lubricating oil scattered upward of the transmission case 11 by the rotation of each gear, and prevents the lubricating oil from scattering upward from the return receiver 194. Thus, the return receiver 194 is configured to drop the lubricating oil that has collided with the bottom surface thereof below the mission case 11 and return it to the lubricating oil storage area 91 at the bottom.

(Effects of transmission 101)
As described above, the present invention can be applied to a normally open transmission. Thus, when the lubrication mechanism 190 is applied to the transmission 101 that is an automatic mechanical transmission,
The same effects as those of the first embodiment are achieved. Further, the lubricating mechanism 190 of the present invention is provided for the member that is scooping up the lubricating oil inside the automatic mechanical transmission. Thereby, the power resistance acting on the internal combustion engine E / G can be reduced by the stirring resistance applied to the ring gear 180. Furthermore, with such a configuration, the lubricating oil can be efficiently scraped and the circulation of the lubricating oil in the mission case 11 can be improved. Therefore, the amount of lubricating oil stored in the mission case 11 can be reduced as compared with the conventional case. Therefore, the stirring resistance of the lubricating oil by each gear can be reduced, and the power loss due to this can be reduced. Therefore, power transmission efficiency can be improved as the transmission 101.

<Modification of the first and second embodiments>
In the first embodiment, the amount of lubricating oil stored in the transmission case 11 is set so that only the lower part of the ring gear 80 is immersed when the vehicle travels when the oil level of the lubricating oil storage area 91 is lowered. It was supposed to be. On the other hand, when the vehicle travels, the ring gear 8
The amount of oil may be adjusted so that gears other than 0 are also immersed in the lubricating oil storage area 91. For example, in the second embodiment, the lubricating oil accommodated in the transmission case 11 is not limited to the lower part of the ring gear 180 and the first speed driven gear 161 and the second speed driven gear 1 when the vehicle is traveling.
The amount of oil is set so that the lower part of 62 is immersed. Increasing the amount of lubricating oil stored in the mission case 11 can improve the lubricity in the mission case 11, but the stirring resistance may increase. For this reason, it is preferable to apply the present invention to a transmission and to set an appropriate amount of oil after ensuring efficient circulation of lubricating oil in the transmission case 11.

DESCRIPTION OF SYMBOLS 1,101: Transmission 10: Case, 11: Mission case (first case part), 11a: Inflow groove 12: Clutch housing (second case part), 11b, 12b: Mounting hole 13: Bolt 21: First input Axis (first input axis), 22: second input axis (second input axis)
123: Input shaft 31: First output shaft (first output shaft) 32: Second output shaft (second output shaft)
133: Output shaft 40: Dual clutch, 41: First clutch, 42: Second clutch 143: Automatic clutch mechanism 51-57, 151-156: Drive gear of gear stage, 58: Final reduction drive gear 61-67, 161 166: driven gear of gear stage, 62a: small diameter gear 68, 168: final reduction drive gear 70, 170: reverse gear 80, 180: ring gear, 80a, 180a: rotating shaft 90, 190: lubrication mechanism, 91: lubricating oil Storage area 92: Supply receiver, 92a: Collection part, 92b: Flow path, 92c: Supply port 93: Separator (lubricating oil holding part), 93a: Recess, 93L, 93R: Side piece 94, 194: Return receiver, 94a , 194a: Collection part 94b, 194b: Flow path, 94c, 194c: Return port 101-104: Gear shift clutch 201 Hub, 202: sleeve E / G: internal combustion engine (prime mover)

Claims (7)

Case and
A plurality of gears rotatably supported in the case and including a differential ring gear;
A lubricating oil storage area formed in the case, storing the lubricating oil stored in the case, and capable of scooping the stored lubricating oil upward of the ring gear by rotation of the ring gear;
A supply receiver for supplying the lubricating oil scraped upward by rotation of the ring gear to a plurality of lubrication points of the gear;
An input shaft that rotatably supports a driving gear among the plurality of gears;
A clutch that transmits the rotational driving force of a prime mover to the input shaft, and when the operating force is applied to the clutch, the prime mover and the input shaft are connected, and no operating force is applied to the clutch. The normally open clutch that opens the prime mover and the input shaft,
A transmission comprising: In claim 1,
The ring gear is formed so as to surround the periphery of the ring gear from the lubricating oil storage region to the outside of the lubricating oil storage region, and is scraped up by rotation of the ring gear outside the lubricating oil storage region. A lubricating oil holding portion for holding the lubricating oil between the ring gear and allowing the ring gear to scatter the lubricating oil held outside the lubricating oil storage area toward the supply receiver. A transmission further comprising: In claim 2,
The lubricating oil holding part is composed of two side pieces respectively fixed to a first case part and a second case part constituting the case, and the second case part is fastened to the first case part. And the two side pieces surround a peripheral surface and both side surfaces of the peripheral portion of the ring gear. In any one of Claims 1-3,
A transmission further comprising a return receiver that collects the lubricating oil scattered by the rotation of the plurality of gears and returns the collected lubricating oil to the vicinity of the ring gear. In claim 4,
The return receiver is integrated so that the bottom wall portion of the return receiver protrudes from the inner wall surface of the case so that the collected lubricating oil is returned to the vicinity of the ring gear along the inner wall surface of the case. A transmission characterized in that it is formed. In claim 4 or 5,
The transmission is characterized in that the return receiver is arranged so that the bottom surface of the return receiver collides with the lubricating oil scattered upward of the case by the rotation of the gear and drops it below the case. In any one of Claims 1-6,
The input shaft has a first input shaft that rotatably supports a drive-side gear among the plurality of gears, and a second input shaft disposed concentrically with the first input shaft,
A first output shaft and a second output shaft that rotatably support a driven gear among the plurality of gears are arranged in parallel with the input shaft,
The clutch is a dual clutch having a first clutch that transmits a rotational driving force of a prime mover to the first input shaft and a second clutch that transmits the rotational driving force to the second input shaft;
The transmission is characterized in that the differential ring gear is always rotationally connected to the first output shaft and the second output shaft.

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