JP2012013107A - Transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission which needs only a small amount of a lubricating oil to supply it to a fitting part by supplying the lubricating oil to the fitting part only during continuous running, that is, when the gear to be driven of a transmission gear train is fitted in the sleeve of a clutch mechanism.SOLUTION: The transmission 10 is configured to comprise at least an input shaft 11 to which the power from a power source is input, an output shaft 12 from which the power from the power source is output, a plurality of transmission gear trains which is provided to the input shaft 11 and the output shaft 12 to enable the power from the power source to be transmitted from the input shaft 11 to the output shaft 12, a clutch mechanism which can switch one transmission gear train of a plurality of transmission gear trains between a power transmission state and a power interception state, and a lubricating oil supply means provided to a gear to be synchronized, which constitutes the transmission gear train, and can be switched between a first state in which lubricating oil supply to the fitting part between the gear to be synchronized and a clutch mechanism is stopped in the interception state and a second state in which the lubricating oil is supplied to the fitting part in the power transmission state.

Description

  The present invention relates to a transmission mounted on a vehicle such as an automobile.

  2. Description of the Related Art Conventionally, a transmission mounted on a vehicle such as an automobile is disposed in a state where a driving gear and a driven gear constituting a transmission gear train are always meshed with an input shaft and an output shaft. As a transmission, a synchronous mesh type transmission is generally known in which each shift gear train is switched between a power transmission state and a cutoff state by a clutch mechanism to enable a shift operation.

  The transmission supplies the lubricating oil from the input shaft and the output shaft to the side surface of the driven gear constituting each transmission gear train, the baux ring side constituting the clutch mechanism, and the like. Smooth shifting to the row is possible.

  By the way, the transmission enables the shift operation by switching each transmission gear train between the power transmission state and the cutoff state by fitting the sleeve constituting the clutch mechanism and the driven gear constituting the transmission gear train. However, as illustrated in FIG. 6, as illustrated in FIG. 6, the lubricating oil is supplied to a portion where the driven gear and the sleeve are fitted (fitting portion 138 in FIG. 6) in the power transmission state. There was a reality that it was difficult.

  In such a situation, for example, in a diesel vehicle that can travel from a low speed region while being in a high speed gear train, among the transmission gear trains, since the travel time in the high speed gear train is long, the high speed gear train and the sleeve The state in which the lubricating oil is difficult to be supplied to the fitting portion of this is continued for a long time. As a result, the high-speed gear train and the sleeve are easily damaged and worn.

  In view of this, for example, Patent Document 1 discloses a manual transmission that enables the supply of lubricating oil to the entire synchronization mechanism as a means for supplying lubricating oil to a fitting portion between a driven gear and a sleeve of each transmission gear train. A lubricating structure is disclosed.

  Further, Patent Document 2 discloses a taper formed in a plurality of a through-hole penetrating the transmission gear in a radial direction from an inner peripheral surface of the transmission gear and a spline groove formed in the inner peripheral surface of the gear piece. There is provided a lubricating device for a manual transmission that is capable of supplying lubricating oil between synchronous contact surfaces by providing a lubricating oil passage composed of a groove and generating a forced flow in the outer diameter direction. It is disclosed.

JP-A-8-312761 Japanese Patent Laid-Open No. 10-153221

  However, Patent Documents 1 and 2 have a structure in which lubricating oil always flows in a fitting portion where a driven gear and a sleeve of a transmission gear train are fitted. That is, in the above-mentioned Patent Documents 1 and 2, since the lubricating oil always flows through the fitting portion together with the side surface side and the bokeling side of the driven gear, the amount of the lubricating oil must be increased more than necessary. There is a technical problem that must be done.

  An object of the present invention is to supply lubricating oil to the fitting portion in continuous running, that is, only when the driven gear of the transmission gear train and the sleeve of the clutch mechanism are fitted in view of the above-described conventional situation. Then, it is providing the transmission which can supply lubricating oil to a fitting part with a small amount of oil.

  In order to solve such problems, a transmission according to the present invention is provided on an input shaft to which power of a drive source is input, an output shaft that outputs power of the drive source, the input shaft, and the output shaft. A plurality of transmission gear trains that enable power transmission of the drive source from the input shaft to the output shaft, and among the plurality of transmission gear trains, one of the transmission gear trains is in a power transmission state and a cutoff state. And a clutch mechanism that can be switched to each other, provided in a synchronized gear constituting the transmission gear train, and supplying lubricating oil to a fitting portion between the synchronized gear and the clutch mechanism in the disconnected state. Lubricating supply means that can be switched between a first state of stopping and a second state of supplying lubricating oil to the fitting portion in the power transmission state is provided.

  Further, the lubricating oil supply means of the transmission according to the present invention is provided in a lubricating oil supply passage for supplying the lubricating oil to the fitting portion, and in the lubricating oil supply passage, and operates in the operation of the clutch mechanism. Accordingly, a lubricating oil supply valve that opens and closes the lubricating oil supply passage is provided.

  Further, the lubricating oil supply valve of the transmission according to the present invention includes a main body that can open and close the lubricating oil supply passage due to the operation of the clutch mechanism, and the synchronized member that constitutes a part of the main body. A projecting portion projecting from the outer peripheral surface of the gear, and the main body portion opens and closes the lubricating oil supply passage when the projecting portion is pushed inside the synchronized gear due to the clutch operation. Is configured to do.

  Further, the lubricating oil supply passage of the transmission according to the present invention has a step portion at the boundary between the first and second passages formed with different inner diameters, and the above-described clutch operation causes the above-mentioned The protruding portion of the lubricating oil supply valve is pushed and pushed inside the synchronized gear, and the lubricating oil supply passage is opened and closed by the main body portion being separated from the stepped portion.

  Further, the clutch mechanism of the transmission according to the present invention is formed with a notch portion that engages with the protruding portion of the lubricating oil supply valve in the power transmission state.

  The lubricating oil supply means of the transmission according to the present invention further includes a biasing member that biases the lubricating oil supply valve toward the outer peripheral surface of the synchronized gear.

  In addition, the input shaft and the output shaft of the transmission according to the present invention have an oil passage that feeds lubricating oil into the transmission gear train, the clutch mechanism, and the lubricating oil supply passage, and are caused by the operation of the clutch mechanism. When the lubricating oil supply valve is in the first state, the lubricating oil is supplied to the transmission gear train and the clutch mechanism, and in the second state, the lubricating oil is added to the transmission gear train and the clutch mechanism. The lubricating oil is supplied to the supply passage.

  According to the present invention, the lubricating oil is supplied to the fitting portion during continuous running, that is, only when the transmission gear train and the clutch mechanism are fitted, so that the lubricating oil is supplied to the fitting portion with a small amount of oil. Can be provided.

It is a side view which shows typically the structure of the transmission which concerns on one embodiment of this invention. It is sectional drawing which shows typically the structure of the transmission which concerns on one embodiment of this invention. It is an expanded sectional view showing typically the 1st state of the composition of the transmission concerning one embodiment of the present invention. It is an expanded sectional view showing typically the 2nd state of the composition of the transmission concerning one embodiment of the present invention. It is sectional drawing which shows line II 'in FIG. 3A typically. It is sectional drawing which shows line II-II 'in FIG. 3B typically. It is sectional drawing which shows typically line II-II 'in FIG. 3B about the structure of the transmission which concerns on other embodiment of this invention. It is sectional drawing which shows the structure of the conventional transmission typically.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. First, the structure of the transmission 10 of this Embodiment is demonstrated using FIG.1 and FIG.2. FIG. 1 is a side view schematically showing an internal configuration of a transmission 10 according to an embodiment of the present invention, and FIG. 2 schematically shows an internal configuration of the transmission 10 according to an embodiment of the present invention. FIG.

  As illustrated in FIGS. 1 and 2, the transmission 10 of the present embodiment is housed in a transmission case 9, and an input shaft 11 and an output shaft 12 that are arranged in parallel with each other can rotate to the transmission case 9. Is pivotally supported.

  The input shaft 11 is connected to a crankshaft of an engine (power source) (not shown) so that the engine power can be input via the crankshaft. Further, as described above, the output shaft 12 is arranged in parallel to the input shaft 11 and receives engine power from the input shaft 11 to output engine power.

  The input shaft 11 and the output shaft 12 of the present embodiment are provided with a plurality of transmission gear trains that enable transmission of engine power from the input shaft 11 to the output shaft 12. This transmission gear train is configured to have two gears, and these two gears are arranged so as to mesh with each other, and either one is provided to be rotatable relative to either the input shaft 11 or the output shaft 12. ing. The other is provided integrally with either the input shaft 11 or the output shaft 12.

  Specifically, a first speed drive gear 14 and a second speed drive gear 15 are integrally provided on the input shaft 11 so as not to be relatively rotatable. The input shaft 11 is provided with a third-speed driven gear 16 (synchronized gear) and a fifth-speed driven gear 18 (synchronized gear) so as to be relatively rotatable.

  The input shaft 11 is provided with an intermediate shaft 13 disposed concentrically with the input shaft 11 so as to be relatively rotatable. The intermediate shaft 13 is provided with a fourth speed driven gear 17 (synchronized gear) so as to be relatively rotatable.

  On the other hand, the output shaft 12 is engaged with the first-speed driving gear 14 and the second-speed driving gear 15 at all times, so that the first-speed driven gear wheel constituting the first-speed and second-speed gear trains is always engaged. A driving gear 24 (synchronized gear) and a second speed driven gear 25 (synchronized gear) are provided so as to be relatively rotatable.

  Further, the output shaft 12 is always in mesh with the third driven gear 16 and the fifth driven gear 18, respectively, so as to constitute a third gear and a fifth gear train. The drive gear 26 and the fifth speed drive gear 28 are integrally provided.

  The output shaft 12 is integrally provided with a fourth-speed drive gear 27 that is always meshed with the fourth-speed driven gear 17 to form a fourth-speed transmission gear train.

  The input shaft 11 and the output shaft 12 are provided with meshing clutches (clutch mechanisms) that can switch one of the transmission gear trains between a power transmission state and a cutoff state. In the present embodiment, two meshing clutches are provided on the input shaft 11, and one meshing clutch is provided on the output shaft 12.

  The second meshing clutch 32 provided on the input shaft 11 is for switching the fifth-speed transmission gear train between a power transmission state and a cutoff state. Further, the third meshing clutch 33 provided on the input shaft 11 is for switching between the power transmission state and the cutoff state for either the third speed gear train or the fourth speed gear train.

  The second meshing clutch 32 is disposed between the third speed driven gear 16 and the fifth speed driven gear 18 and is provided on the input shaft 11. That is, when the second meshing clutch 32 is actuated to the fifth speed transmission gear train side, the fifth speed driven gear 18 is rotated due to the drive of the input shaft 11. The fifth-speed drive gear 28 rotates in conjunction with the rotation of the fifth-speed driven gear 18 to enable power transmission from the input shaft 11 to the output shaft 12.

  The third meshing clutch 33 of the present embodiment is disposed between the third speed driven gear 16 and the fourth speed driven gear 17 and is provided on the input shaft 11. That is, when the third meshing clutch 33 is operated to the third speed transmission gear train side, the third speed driven gear 16 is rotated due to the drive of the input shaft 11. The third-speed drive gear 26 rotates in conjunction with the rotation of the third-speed driven gear 16 to enable power transmission from the input shaft 11 to the output shaft 12.

  Further, when the third meshing clutch 33 is operated to the fourth speed transmission gear train side, the fourth speed driven gear 17 is interlocked and driven from the input shaft 11 to the output shaft due to the drive of the input shaft 11. Power transmission is possible.

  On the other hand, the first meshing clutch 31 provided on the output shaft 12 is for switching between a power transmission state and a shut-off state for either the first speed gear train or the second speed gear train. The first meshing clutch 31 is disposed between the first speed driven gear 24 and the second speed driven gear 25 and is provided on the output shaft 12.

  That is, when the first meshing clutch 31 is operated toward the first speed transmission gear train, the first speed driving gear 14 is rotated due to the drive of the input shaft 11. Then, the first-speed driven gear 24 rotates in conjunction with the rotation of the first-speed driving gear 14 to enable power transmission from the input shaft 11 to the output shaft 12.

  When the first meshing clutch 31 is operated toward the second speed driven gear 25, the second speed driving gear 15 is rotated due to the drive of the input shaft 11. Then, the second-speed driven gear 25 rotates in conjunction with the rotation of the second-speed driving gear 15 to enable power transmission from the input shaft 11 to the output shaft 12.

  As described above, the switching operation between the power transmission state and the cutoff state to each transmission gear train is performed by the first mesh clutch 31, the second mesh clutch 32, and the third mesh clutch 33.

  In the present embodiment, the first meshing clutch 31, the second meshing clutch 32, and the third meshing clutch 33 are constituted by a synchromesh mechanism. Hereinafter, the configuration of the synchromesh mechanism will be described with reference to FIGS. 3A and 3B. FIG. 3A is an enlarged cross-sectional view schematically showing a first state of the configuration of the transmission 10 according to the embodiment of the present invention, and FIG. 3B is a transmission 10 according to the embodiment of the present invention. It is an expanded sectional view showing typically the 2nd state of composition.

  Note that the first meshing clutch 31, the second meshing clutch 32, and the third meshing clutch 33 are all configured by a synchromesh mechanism as described above, and the configuration is the same or equivalent. is there. Therefore, in FIG. 3A and FIG. 3B, it demonstrates based on the 3rd meshing clutch 33, and the description about the 1st meshing clutch 31 and the 2nd meshing clutch 32 is abbreviate | omitted.

  As illustrated in FIG. 3A, the third-speed driven gear 16 is provided on the input shaft 11 so as to be relatively rotatable as described above. Specifically, the third speed driven gear 16 is provided on the input shaft 11 via a needle bearing 37.

  As described above, since the third speed driven gear 16 is provided on the input shaft 11 via the needle bearing 37, the third speed driven gear 16 is rotated relative to the input shaft 11 as described above. It is provided as possible.

  And the 3rd meshing clutch 33 is comprised by the synchromesh mechanism as mentioned above. Specifically, the third meshing clutch 33 includes a clutch hub 34 attached to the input shaft 11 and a sleeve 36 provided on the clutch hub 34 so as to be slidable in the axial direction. Yes.

  As described above, the clutch hub 34 is attached to the input shaft 11 and is splined to the outer peripheral surface of the input shaft 11 so as to rotate together with the input shaft 11. Note that the method of fixing the clutch hub 34 is not limited to spline fitting. For example, the clutch hub 34 may be fixed to the outer peripheral surface of the input shaft 11 using a groove having a two-surface width.

  A gear piece 16a is spline-fitted to the third speed driven gear 16, and the gear piece 16a and the third speed driven gear 16 are provided so as to be integrated. On the other hand, since the gear piece 16 a is not fitted to the clutch hub 34, the gear piece 16 a can be rotated relative to the clutch hub 34.

  Further, the gear piece 16 a includes a cone portion having a tapered surface inclined with respect to the axis of the input shaft 11 as an outer peripheral surface. A baux ring 35 is fitted on the outer peripheral side of the cone portion.

  The bake ring 35 is for synchronizing the rotation of the gear piece 16a and the clutch hub 34, and has a cone portion having a tapered surface facing the cone portion of the gear piece 16a as an inner peripheral surface. In other words, the cone portion of the baux ring 35 and the cone portion of the gear piece 16a come into contact with each other, so that the boke ring 35 and the gear piece 16a can be rotated synchronously.

  Further, as described above, the sleeve 36 is spline-fitted to the outer peripheral surface of the clutch hub 34. The sleeve 36 is rotatably integrated with the input shaft 11 via the clutch hub 34 and is slidable in a direction along the axis of the input shaft 11. That is, the clutch hub 34 holds the sleeve 36 so as to be slidable in the direction along the axis of the input shaft 11.

  In the present embodiment, the third speed driven gear 16 is provided with lubricating oil supply means for supplying lubricating oil to the fitting portion 38 between the third speed driven gear 16 and the sleeve 36. The lubricating oil supply means is formed inside the third-speed driven gear 16 and reciprocates inside and outside the lubricating oil supply passage 43 for supplying the fitting portion 38 with the lubricating oil. A lubricating oil supply valve 41 that is provided so as to be movable and opens the lubricating oil supply passage due to the operation of the third meshing clutch 33 is provided.

  Hereinafter, the lubricating oil supply means of the present embodiment will be described with reference to FIGS. 3A, 3B, 4A, and 4B. 4A is a cross-sectional view schematically showing a line II ′ in FIG. 3A, and FIG. 4B is a cross-sectional view schematically showing a line II-II ′ in FIG. 3B.

  As illustrated in FIGS. 3A, 3B, 4A, and 4B, the third-speed driven gear 16 is lubricated by the fitting portion 38 with the lubricating oil fed from the output shaft 11 as described above. A lubricating oil supply passage 43 is formed.

  The lubricating oil supply passage 43 is formed with mutually different inner diameters, and includes a first lubricating oil supply passage 43b (first passage) and a second lubricating oil supply that accommodate the lubricating oil supply valve 41 in a reciprocable manner. It has a passage 43a (second passage).

  The lubricating oil supply passage 43 is disposed at the boundary between the first lubricating oil supply passage 43b and the second lubricating oil supply passage 43a, and a third meshing clutch 33 is connected to a spherical body portion 41a of the lubricating oil supply valve 41 described later. The step portion 43c is engaged so as to be separable due to the above operation.

  As described above, the lubricating oil supply valve 41 is disposed inside the lubricating oil supply passage 43. The lubricating oil supply valve 41 includes a protruding portion 41 c protruding from the outer peripheral surface of the third speed driven gear 16 and a spherical portion 41 a that opens the lubricating oil supply passage 43 due to the operation of the third meshing clutch 33. And is configured.

  The lubricating oil supply valve 41 is disposed between the protruding portion 41 c and the spherical portion 41 a and has a cylindrical portion 41 b that reciprocates in the lubricating oil supply passage 43 due to the operation of the third meshing clutch 33. Configured.

  Thus, since the lubricating oil supply valve 41 of this Embodiment has the cylindrical part 41b which connects the protrusion part 41c and the spherical body part 41a, the axis | shaft and lubricating oil supply of the lubricating oil supply valve 41 are comprised. It becomes possible to arrange | position with the axis | shaft of the channel | path 43 substantially coaxially. Therefore, the spherical portion 41 a of the lubricating oil supply valve 41 can be reciprocated on the axis of the lubricating oil supply passage 43.

  In the present embodiment, the lubricating oil supply means includes an urging member 42 that urges the lubricating oil supply valve 41 toward the outer peripheral surface of the third speed driven gear 16. The biasing member 42 of the present embodiment is configured using a spring.

  Usually, the lubricating oil supply valve 41 is urged toward the outer peripheral surface side of the third speed driven gear 16 by a centrifugal force generated by the rotation operation of the third speed driven gear 16. In the present embodiment, the lubricating oil supply passage 43 is more reliably sealed by being urged by the urging member 42 in addition to the centrifugal force generated by the rotation operation of the third speed driven gear 16. be able to.

  Further, since the lubricating oil supply valve 41 is urged toward the outer peripheral surface side of the third speed driven gear 16 by the centrifugal force generated by the rotating operation of the third speed driven gear 16, the lubricating oil supply valve The protrusion 41c of 41 is maintaining the position which protruded outside from the outer peripheral surface of the driven gear 16 of the 3rd speed.

  That is, as illustrated in FIG. 4B, when the sleeve 33 is fitted to the third speed driven gear 16, the hemispherical portion 41 c of the main body portion 41 is pushed inward by the sleeve 33. As described above, the hemispherical portion 41c is pushed inside and the spherical portion 41a of the main body portion 41 is separated from the stepped portion 43c, thereby bringing the lubricating oil supply passage 43 into a communication state. Since the third speed driven gear 16 is rotating, the lubricating oil is sent to the outside by centrifugal force, and the lubricating oil is supplied to the fitting portion 38.

  Therefore, according to the present embodiment, it is possible to supply the lubricating oil to the fitting portion 38 only when the sleeve 36 and the third-speed driven gear 16 are fitted, so that the consumption of the lubricating oil is increased. The amount can be reduced. Further, when the sleeve 36 and the third speed driven gear 16 are not fitted, the lubricating oil supply passage 43 is blocked, so that the side surface side of the third speed driven gear 16 that is the lubricating oil passage is provided. Therefore, it is possible to reduce the negative pressure generated on the side of the bake ring 35, and the lubricating oil can be supplied efficiently.

  Next, the operation of the transmission 10 according to the present embodiment will be described with reference to FIGS. 3A, 3B, 4A, and 4B. The arrows shown in FIGS. 3A and 3B indicate oil lubrication paths.

  As illustrated in FIG. 3A and FIG. 4A, the lubricating oil fed from the output shaft 11 normally uses the centrifugal force generated by the rotation of the third speed driven gear 16 to cause the needle bearing 37 to move. To the side surface of the third speed driven gear 16.

  In addition to the side surface side of the third-speed driven gear 16, the lubricating oil fed from the input shaft 11 uses the centrifugal force generated by the rotational operation of the clutch hub 34, and passes through the clutch hub 34. It is supplied to the bake ring 35 side.

  At this time, the lubricating oil supply valve 41 provided in the lubricating oil supply passage 43 uses the centrifugal force generated by the rotation operation of the third-speed driven gear 16 so that the spherical portion 41a moves to the stepped portion 43c. It is in contact. For this reason, the lubricating oil supply passage 43 is normally closed by the spherical portion 41a.

  In the present embodiment, an urging member 42 that urges the lubricating oil supply valve 41 toward the outer peripheral surface side of the third speed driven gear 16 is provided. For this reason, in addition to the centrifugal force generated by the rotation operation of the third-speed driven gear 16 as described above, the sphere member 41a of the lubricating oil supply valve 41 is pressed against the stepped portion 43c by the biasing member 42. It becomes possible to seal the lubricating oil supply passage 43 more reliably.

  In this way, by sealing the lubricating oil supply passage 43, leakage of the lubricating oil from the lubricating oil supply passage 43 can be suppressed during normal times. As a result, it becomes possible to supply the lubricating oil only to the side surface side of the third-speed driven gear 16 and the bokeling 35 side at normal times, and the amount of lubricating oil can be reduced.

  At this time, if the lubricating oil supply passage 43 is open, negative pressure may be applied to the side surface side of the third speed driven gear 16 and the boke ring 35 side. Since the oil supply passage 43 is sealed, negative pressure on the side surface side of the third speed driven gear 16 and the boke ring 35 side can be reduced. Therefore, the lubricating oil fed from the input shaft 11 can be efficiently supplied to the side surface side of the third speed driven gear 16 and the boke ring 35 side.

  On the other hand, as illustrated in FIGS. 3B and 4B, when the sleeve 36 of the third meshing clutch 33 is fitted to the third speed driven gear 16, the sleeve 36 is pressed against the inner peripheral surface of the sleeve 36 and lubricated oil. The supply valve 41 moves. Thereby, the lubricating oil supply passage 43 is opened.

  As a result, the lubricating oil fed from the input shaft 11 is subjected to centrifugal force generated by the rotation of the third speed driven gear 16 in addition to the side surface side of the third speed driven gear 16 and the bake ring 35 side. Is fed into the lubricating oil supply passage 43. Thus, the lubricating oil can be supplied from the lubricating oil supply passage 43 to the outer peripheral side of the lubricating oil supply passage 43, that is, the fitting portion 38 only when the driven gear 16 and the sleeve 36 of the third speed are fitted. It becomes possible.

  Therefore, according to the transmission 10 of the present embodiment, only when the vehicle is continuously running, that is, when the third speed gear train and the third meshing clutch 33 are engaged, the fitting portion 38. It becomes possible to supply lubricating oil to

  Thereby, according to the transmission 10 of this Embodiment, the oil amount sent to the input shaft 11 can be made small. Further, except when the sleeve 36 and the third-speed driven gear 16 are fitted, they can be supplied only to the side surface side and the boke ring 35 side of the third-speed driven gear 16. As a result, the amount of oil supplied to the input shaft 11 can be reduced, and the negative pressure on the side surface side of the third-speed driven gear 16 and the bokeling 35 side can be reduced. Oil can be supplied.

(Modification)
A modification of this embodiment will be described with reference to FIG. FIG. 5 is a cross-sectional view schematically showing a line II-II ′ in FIG. 3B. This modification is different from the above-described first embodiment in that a notch 54 is provided on the inner peripheral surface of the sleeve 56, and the other configurations are the same. Therefore, the same or corresponding parts as those in the first embodiment are denoted by the same reference numerals and the description thereof is omitted.

  In this modification, the notch 54 is formed on the inner peripheral surface of the sleeve 56 as described above. The notch 54 is engaged with the protrusion 41 c of the lubricating oil supply valve 41 when the third speed driven gear 16 and the sleeve 56 are fitted.

  Therefore, it is possible to position the sleeve 56 in which the third speed driven gear 16 and the sleeve 56 are fitted. Further, since the protrusion 41c is engaged with the notch 54, the sleeve 56 can be prevented from coming off.

DESCRIPTION OF SYMBOLS 9 Transmission case 10 Transmission 11 Input shaft 12 Output shaft 13 Intermediate shaft 14 1st speed drive gear 15 2nd speed drive gear 16 3rd speed driven gear 17 4th speed driven gear 18 5th speed Driven gear 24 First speed driven gear 25 Second speed driven gear 26 Third speed drive gear 27 Fourth speed drive gear 28 Fifth speed drive gear 31 First meshing clutch 32 Second Engagement clutch 33 Third engagement clutch 34 Clutch hub 35 Bokeh ring 36 Sleeve 37 Needle bearing 38 Fitting portion 40 Lubricating oil supply means 41 Lubricating oil supply valve 42 Energizing member 43 Lubricating oil supply passage

Claims (7)

An input shaft to which the power of the drive source is input;
An output shaft for outputting power of the drive source;
A plurality of transmission gear trains provided on the input shaft and the output shaft, and capable of transmitting power of the drive source from the input shaft to the output shaft;
A transmission including at least a clutch mechanism capable of switching one of the transmission gear trains between a power transmission state and a cutoff state among the plurality of transmission gear trains;
A first state that is provided in a synchronized gear that constitutes the transmission gear train, and stops supplying lubricating oil to a fitting portion between the synchronized gear and the clutch mechanism in the shut-off state; and in the power transmission state Comprising a lubrication supply means switchable to a second state in which lubricating oil is supplied to the fitting portion;
A transmission characterized by. The lubricating oil supply means is provided in the lubricating oil supply passage for supplying the lubricating oil to the fitting portion and the lubricating oil supply passage, and the lubricating oil supply passage is caused by the operation of the clutch mechanism. A lubricating oil supply valve that opens and closes;
The transmission according to claim 1. The lubricating oil supply valve includes a main body portion that can open and close the lubricating oil supply passage due to the operation of the clutch mechanism, and a protruding portion that protrudes from an outer peripheral surface of the synchronized gear that constitutes a part of the main body portion. And having
Due to the clutch operation, the main body portion opens and closes the lubricating oil supply passage when the protruding portion is pushed inside the synchronized gear.
The transmission according to claim 2. The lubricating oil supply passage has a stepped portion at the boundary between the first and second passages formed with different inner diameters.
Due to the clutch operation, the protruding portion of the lubricating oil supply valve is pushed inside the synchronized gear, and the main body portion is separated from the stepped portion to open and close the lubricating oil supply passage. thing,
The transmission according to claim 2 or 3. The clutch mechanism is formed with a notch that engages with the protruding portion of the lubricating oil supply valve when the power is transmitted.
The transmission according to claim 3 or 4, characterized by the above-mentioned. The lubricating oil supply means further comprises a biasing member that biases the lubricating oil supply valve toward the outer peripheral surface of the synchronized gear;
The transmission according to any one of claims 2 to 5, wherein: The input shaft and the output shaft have an oil passage that feeds lubricating oil into the transmission gear train, the clutch mechanism, and the lubricating oil supply passage,
The lubricating oil is supplied to the transmission gear train and the clutch mechanism when the lubricating oil supply valve is in the first state due to the operation of the clutch mechanism, and the transmission gear train and the clutch when the second state is established. Supplying the lubricating oil to the lubricating oil supply passage in addition to the mechanism;
The transmission according to any one of claims 2 to 6, wherein:

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