JP2017211035A - transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a transmission capable of reducing wear of a clutch, and capable of improving power transmission efficiency.SOLUTION: A transmission 1 includes a hydraulic type power transmission device 60 at a second counter shaft 30 which is a power transmission path shared by a first speed stage and a rearward speed stage. In the transmission 1, the hydraulic type power transmission device 60 transmits the power of the second counter shaft 30 to an output disc shaft 61 by a hydraulic pressure in the first speed stage and the rearward speed stage. In the second counter shaft 30, a first speed driven gear 31 and a rearward speed driven gear 37 are arranged on one end side closest to an engine 2, and a second output gear 68 is arranged on the other end side farthest from the engine 2. The hydraulic type power transmission device 60 is arranged between the first speed driven gear 31 and the second output gear 68 on the second counter shaft 30.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a transmission including a hydraulic power transmission device.

  Conventionally, in a transmission mounted on a vehicle such as an automobile, a technique has been known in which gear shifting is continuously performed using hydraulic oil (see Patent Document 1). In the device described in Patent Document 1, a hydraulic power transmission device that transmits power by hydraulic oil and a belt type continuously variable transmission mechanism that transmits power by a winding transmission device are connected in series. Since the power described in Patent Document 1 passes through the hydraulic power transmission device at all shift speeds, smooth traveling can be realized by slipping on the hydraulic power transmission device even when the vehicle starts or travels at a low speed. .

Japanese Patent No. 4375462

  However, in the conventional transmission described in Patent Document 1, since the low power transmission efficiency of the hydraulic power transmission device reaches all the gears, the power transmission efficiency may be deteriorated at all the gears. was there.

  On the other hand, in a conventional transmission equipped with a friction clutch as a power transmission device, the clutch is operated in a half-clutch state in order to adjust the degree of power transmission when the vehicle starts or when traveling at a low speed. For this reason, since the clutch is in a half-clutch state for a long time, the wear of the clutch may increase, and further, the clutch may become high temperature and the power transmission efficiency may decrease.

  In recent years, AMT (Automated Manual Transmission) has been developed as a transmission that can achieve both the excellent power transmission efficiency of a manual transmission and the convenience of an automatic transmission. This AMT is a parallel shaft gear type manual transmission. The shift operation is automated by providing an automatic transmission unit in the machine. This AMT also uses a friction clutch as a starting device, and there is a possibility that the wear of the clutch may increase due to a half-clutch state for a long time.

  The present invention has been made paying attention to the above problems, and an object of the present invention is to provide a transmission capable of reducing clutch wear and improving power transmission efficiency. To do.

  The present invention is provided between an input shaft to which power is transmitted from a drive source via a friction clutch, an output shaft for outputting power after shifting, and between the input shaft and the output shaft. And a stepped transmission in which a plurality of shift stages are switched in a stepped manner, and including a hydraulic power transmission device that transmits power by hydraulic pressure, The shift stage includes a first speed stage that is the slowest speed stage on the forward side, a plurality of high speed stages that are forward side shift stages other than the first speed stage, and a reverse speed stage that is the reverse side shift stage. In addition, the hydraulic power transmission device is provided in a power transmission path shared by the first speed stage and the reverse speed stage.

  As described above, according to the present invention, the wear of the clutch can be reduced and the power transmission efficiency can be improved.

FIG. 1 is a view showing an embodiment of a transmission according to the present invention, and is a rear view of the transmission. FIG. 2 is a diagram showing an embodiment of the transmission of the present invention, and is a left side view of the transmission. FIG. 3 is a diagram showing an embodiment of the transmission of the present invention, and is a right side view of the transmission. FIG. 4 is a diagram showing an embodiment of the transmission of the present invention, and is a skeleton diagram of the transmission. FIG. 5 is a diagram showing an embodiment of a transmission according to the present invention, and is a skeleton diagram of a transmission according to another embodiment.

  Hereinafter, embodiments of a transmission according to the present invention will be described with reference to the drawings. 1 to 5 show a transmission according to an embodiment of the present invention. In FIG. 1 to FIG. 3, up, down, left, and right directions indicate directions viewed from the driver on the vehicle.

  First, the configuration will be described. In FIGS. 1, 2, 3, and 4, the transmission 1 includes an input shaft 10 to which the power of the engine 2 is transmitted. The input shaft 10 includes a clutch 3 that switches power between the engine 2 and the input shaft 10 to a cut-off state / connected state at one end on the engine 2 side.

  The clutch 3 includes a flywheel 3A connected to the crankshaft 2A of the engine 2 and a friction plate 3B arranged to face the flywheel 3A. The friction plate 3B is connected to the input shaft 10.

  The transmission 1 also includes an output shaft 50 that transmits the power after the shift to drive wheels (not shown). The output shaft 50 is disposed coaxially with the input shaft 10 on the other end side of the input shaft 10.

  Further, the transmission 1 includes a first counter shaft 20 and a second counter shaft 30 in parallel with the input shaft 10. The first counter shaft 20 is disposed below and to the right of the input shaft 10. The second counter shaft 30 is disposed below and to the left of the input shaft 10 and further below the first counter shaft 20.

  The input shaft 10 includes, in order from the engine 2 side, a second speed driving gear 12, a first speed driving gear 11, a third speed driving gear 13, a fourth speed driving gear 14, a 4-5 speed switching device 44, a fifth speed driving gear 15, A six-speed switching device 46 is provided. The second speed drive gear 12, the first speed drive gear 11, and the third speed drive gear 13 are fixed to the input shaft 10. The 4-speed drive gear 14 and the 5-speed drive gear 15 are rotatably installed on the input shaft 10.

  The 4-5 speed switching device 44 has a shift sleeve 44A and meshing clutches 44B, 44C. The shift sleeve 44 </ b> A is attached to the input shaft 10 so as to be movable in the axial direction of the input shaft 10 and to rotate integrally with the rotation direction of the input shaft 10.

  The meshing clutch 44B meshes with the side surface of the 4-speed drive gear 14 as the shift sleeve 44A moves to the 4-speed drive gear 14 side. The meshing clutch 44C meshes with the side surface of the fifth speed drive gear 15 as the shift sleeve 44A moves to the fifth speed drive gear 15 side.

  In the 4-5 speed switching device 44, the shift sleeve 44A rotates integrally with the 4th speed drive gear 14 to form the 4th speed stage, and the shift sleeve 44A rotates integrally with the 5th speed drive gear 15 to change the 5th speed stage. Form.

  The 6-speed switching device 46 has a shift sleeve 46A and a meshing clutch 46C. The shift sleeve 46 </ b> A is attached to the input shaft 10 so as to be movable in the axial direction of the input shaft 10 and to rotate integrally with the rotation direction of the input shaft 10.

  The meshing clutch 46C meshes with a 6-speed driven gear 56 provided at one end of the output shaft 50 on the engine 2 side as the shift sleeve 46A moves to the output shaft 50 side. The 6-speed switching device 46 forms a 6-speed stage by the shift sleeve 46 </ b> A rotating integrally with the 6-speed driven gear 56. At the sixth speed, the input shaft 10 and the output shaft 50 are directly connected, and the output shaft 50 rotates at the same speed as the input shaft 10.

  The first counter shaft 20 includes, in order from the engine 2 side, the reverse speed drive gear 27, the second speed driven gear 22, the 2-3 speed switching device 42, the 3rd speed driven gear 23, the 4th speed driven gear 24, and the 5th speed driven gear. 25, a first output gear 28 is provided.

  The reverse speed drive gear 27, the second speed driven gear 22, and the third speed driven gear 23 are rotatably installed on the first counter shaft 20. The second speed driven gear 22 and the reverse speed driving gear 27 are connected to each other so as to be integrally rotatable.

  The fourth speed driven gear 24 and the fifth speed driven gear 25 are fixed to the first counter shaft 20.

  The 2-3 speed switching device 42 includes a shift sleeve 42A and meshing clutches 42B and 42C. The shift sleeve 42 </ b> A is attached to the first counter shaft 20 so as to be movable in the axial direction of the first counter shaft 20 and to rotate integrally with the rotation direction of the first counter shaft 20.

  The meshing clutch 42B meshes with the side surface of the second speed driven gear 22 as the shift sleeve 42A moves to the second speed driven gear 22 side. The meshing clutch 42C meshes with the side surface of the third-speed driven gear 23 as the shift sleeve 42A moves to the third-speed driven gear 23 side.

  The 2-3 speed switching device 42 forms the second speed stage by the shift sleeve 42A rotating integrally with the second speed driven gear 22 and the third speed stage by rotating the shift sleeve 42A integrally with the third speed driven gear 23. Form.

  The second countershaft 30 is provided with a reverse speed driven gear 37, a 1-R speed switching device 41, a first speed driven gear 31, and a hydraulic power transmission device 60 in order from the engine 2 side. The first speed driven gear 31 and the reverse speed driven gear 37 are rotatably installed on the second counter shaft 30.

  The 1-R speed switching device 41 includes a shift sleeve 41A and meshing clutches 41B and 41C. The shift sleeve 41 </ b> A is attached to the second counter shaft 30 so as to be movable in the axial direction of the second counter shaft 30 and to rotate integrally with the rotation direction of the second counter shaft 30.

  The meshing clutch 41B meshes with the side surface of the reverse speed driven gear 37 as the shift sleeve 41A moves to the reverse speed driven gear 37 side. The meshing clutch 41C meshes with the side surface of the first speed driven gear 31 as the shift sleeve 41A moves to the first speed driven gear 31 side.

  The 1-R speed switching device 41 forms a reverse speed stage when the shift sleeve 41A rotates integrally with the reverse speed driven gear 37, and the first speed stage when the shift sleeve 41A rotates integrally with the first speed driven gear 31. Form.

  The reverse speed driven gear 37, the 1st speed drive gear 11, the 2nd speed drive gear 12, the 3rd speed drive gear 13, the 4th speed drive gear 14 and the 5th speed drive gear 15 are the reverse speed drive gear 27, the 1st speed driven gear 31, respectively. The second-speed driven gear 22, the third-speed driven gear 23, the fourth-speed driven gear 24, and the fifth-speed driven gear 25 are always meshed.

  Of these constantly meshing gear pairs, the first speed drive gear 11 and the first speed driven gear 31 are gear pairs that form the first speed, which is the slowest gear position on the forward side.

  The gear pair of the second speed drive gear 12 and the second speed driven gear 22 is a gear pair that forms a second speed stage on the higher speed side than the first speed stage.

  Similarly, the gear pair of the third speed driving gear 13 and the third speed driven gear 23 is a gear pair forming the third speed stage on the higher speed side than the second speed stage, and the gear of the fourth speed driving gear 14 and the fourth speed driven gear 24. The pair is a gear pair that forms the fourth speed stage on the higher speed side than the third speed stage, and the gear pair of the fifth speed drive gear 15 and the fifth speed driven gear 25 forms the fifth speed stage on the higher speed side than the fourth speed stage. Gear pair.

  The meshing clutch 46 </ b> C and the sixth speed driven gear 56 of the sixth speed switching device 46 are a gear pair that forms a sixth speed stage on the higher speed side than the fifth speed stage. In the following, a gear stage of two or more speeds is called a high speed.

  A first final gear 51 and a second final gear 52 are fixed to the output shaft 50 in order from the engine 2 side. The first final gear 51 and the second final gear 52 are always meshed with the first output gear 28 and the second output gear 68.

  Input shaft 10, output shaft 50, first counter shaft 20, second counter shaft 30, each gear pair forming first to sixth gears, and 1-R switching devices 41, 2 to 3 The switching device 42, the 4-5 speed switching device 44, and the 6 speed switching device 46 constitute the stepped transmission 4 that switches the gear position by changing the gear pair through which power passes. The transmission 1 is provided with a transmission case 1C, and the stepped transmission 4 is housed in the transmission case 1C.

  The input shaft 10 is supported by the transmission case 1C via a bearing 5A at one end on the engine 2 side, and supported by the output shaft 50 via a bearing 5D at the other end opposite to the engine 2. The output shaft 50 is supported by the transmission case 1C via a bearing 5B at one end on the engine 2 side, and supported by the transmission case 1C via a bearing 5C at the other end opposite to the engine 2. . The first counter shaft 20 is supported on the transmission case 1C via a bearing 6A at one end on the engine 2 side, and supported on the transmission case 1C via a bearing 6B on the other end opposite to the engine 2. Yes. The second counter shaft 30 is supported by the transmission case 1C via a bearing 7A at one end on the engine 2 side, and supported by the transmission case 1C via a bearing 7C at the other end opposite to the engine 2. Yes. The hydraulic power transmission device 60 on the second countershaft 30 is supported by the transmission case 1C via a bearing 7B. The bearings 5B, 6B, and 7B are arranged at the same position in the axial direction, that is, at positions facing each other in the radial direction.

  Here, the first counter shaft 20 is arranged closer to the transmission case 1C than the input shaft 10 is. For this reason, the shape and size of the transmission case 1 </ b> C are affected by the arrangement and diameter of each driven gear on the first counter shaft 20. In the present embodiment, the first countershaft 20 is provided with the reverse speed drive gear 27, the second speed driven gear 22, the 2-3 speed switching device 42, the third speed driven gear 23, and the fourth speed driven gear 24 in order from the engine 2 side. A fifth speed driven gear 25 and a first output gear 28 are provided.

  That is, a relatively large-diameter second-speed driven gear 22 is disposed on one end side close to the engine 2, and a relatively small-diameter fifth-speed driven gear 25 is disposed on the other end side far from the engine 2. Thereby, the transmission case 1C can be formed in a tapered shape with a diameter reduced toward the other end side far from the engine 2, and the size can be reduced.

  Lubricating oil is sealed inside the transmission case 1C, and the stepped transmission 4 is lubricated and cooled by the lubricating oil. The oil surface position of the lubricating oil is set to a position below the input shaft 10 and the output shaft 50 and above the second counter shaft 30.

  The transmission 1 is provided with an automatic transmission unit 1B above the transmission case 1C. The automatic transmission unit 1B is configured to switch the shift stage of the transmission 1 according to a command from the controller in response to a request from the driver. And the clutch 3 is intermittently operated.

  Specifically, the automatic transmission unit 1B operates the 1-R switching device 41, the 2-3 speed switching device 42, the 4-5 speed switching device 44, and the 6th speed switching device 46, so Either a 6th speed gear stage or a reverse speed stage is formed.

  Further, the automatic transmission unit 1B switches the clutch 3 to the disconnected / connected state by engaging or releasing the friction plate 3B of the clutch 3 with respect to the flywheel 3A. The automatic transmission unit 1B controls the clutch 3 to a half-clutch state (half-engaged state) when the vehicle starts or travels at a low speed, and controls the clutch 3 to a disengaged state when switching the gear stage during traveling. Do things.

  Therefore, the transmission 1 adjusts the rotational speed of the output shaft 50 and controls the output shaft 50 by switching the gear position in the stepped transmission 4 and controlling the degree of engagement of the clutch 3 by the automatic transmission unit 1B. The power output from 50 is adjusted.

  The hydraulic power transmission device 60 is a fluid coupling including an input-side rotation element and an output-side rotation element (not shown), and transmits the power input to the input-side rotation element to the output-side rotation element by the hydraulic oil pressure. The input side rotation element is connected to the second counter shaft 30 and rotates integrally with the second counter shaft 30.

  A first speed driven gear 31 and a reverse speed driven gear 37 are provided at one end of the hydraulic power transmission device 60 on the engine 2 side. On the other end side opposite to the engine 2, an output disk shaft 61 that rotates integrally with the output side rotating element is provided. The output disk shaft 61 is arranged coaxially with the second counter shaft 30 on the outer peripheral side of the second counter shaft 30, and one end portion on the engine 2 side is connected to the output side rotating element, and is opposite to the engine 2. Is extended to the transmission case 1C and supported by the transmission case 1C via a bearing 7B. A second output gear 68 is fixed to the other end of the output disk shaft 61. The hydraulic power transmission device 60 transmits power from the second countershaft 30 to the output disk shaft 61 with the hydraulic oil slipping at the first speed and the reverse speed. On the other hand, the hydraulic power transmission device 60 needs to be cooled because it generates heat due to the sliding of the hydraulic oil. In contrast, the oil level position of the transmission case 1 </ b> C is set above the hydraulic power transmission device 60. For this reason, the hydraulic power transmission device 60 can be cooled by the lubricating oil.

  In addition, as shown in FIG. 5, you may comprise the transmission 1 so that it may be provided with the 1st to 5th gear stage. In FIG. 5, the stepped transmission 4 of the transmission 1 includes a 4-5 speed switching device 47 instead of the 4-5 speed switching device 44 of FIG. 4. The 4-5 speed switching device 47 is disposed on the other end side of the 4th speed drive gear 14 on the input shaft 10.

  In FIG. 5, a 5-speed driven gear 55 is arranged on one end side of the output shaft 50 instead of the 6-speed driven gear 56 of FIG. 4.

  The 4-5 speed switching device 47 has a shift sleeve 47A and meshing clutches 47B, 47C. The shift sleeve 47 </ b> A is attached to the input shaft 10 so as to be movable in the axial direction of the input shaft 10 and to rotate integrally with the rotation direction of the input shaft 10.

  The meshing clutch 47B meshes with the side surface of the 4-speed drive gear 14 as the shift sleeve 47A moves to the 4-speed drive gear 14 side. The meshing clutch 47C meshes with the fifth speed driven gear 55 as the shift sleeve 47A moves to the fifth speed driven gear 55 side.

  The 4-5 speed switching device 47 forms a 4th speed stage by the shift sleeve 47A rotating integrally with the 4th speed drive gear 14, and the 5th speed stage by the shift sleeve 47A rotating integrally with the 5th speed driven gear 55. Form. At the fifth speed stage, the input shaft 10 and the output shaft 50 are directly connected, and the output shaft 50 rotates at the same speed as the input shaft 10.

  Next, the operation of the transmission 1 will be described for each shift stage.

(Forward 1st gear)
When the vehicle is in a stopped state, the transmission 1 is maintained with the clutch 3 in a power cut-off state in response to a command from the automatic transmission unit 1B.

  When the driver selects forward (for example, D range) by a shift lever (not shown), the 1-R switching device 41 is operated by the command of the automatic transmission unit 1B, and the first-speed driven gear 31 is coupled to the second countershaft 30, The first gear is formed.

  Thereafter, when the driver operates an accelerator pedal (not shown) and tries to start, the clutch 3 is controlled from the half-clutch state to the connected state according to a command from the automatic transmission unit 1B.

  The power of the engine 2 is transmitted to the input shaft 10 and from the first speed drive gear 11 fixed to the input shaft 10 through the first speed driven gear 31 coupled to the second counter shaft 30, the hydraulic power transmission device 60. To the input side element.

  Thereafter, the motive power is transmitted to the output side transmission element by hydraulic pressure, and is transmitted to the output disk shaft 61 connected to the output side transmission element.

  Finally, power is transmitted from the second output gear 68 fixed to the output disk shaft 61 to the second final gear 52 fixed to the output shaft 50, so that the power is transmitted to the output shaft 50 and the vehicle moves forward.

  In the transmission 1, the clutch 3 and the hydraulic power transmission device 60 are both present in the power transmission path as the power transmission device at the first speed and the reverse speed described later. The clutch 3 can adjust the degree of power transmission mainly by the hydraulic power transmission device 60 after shortening the time of the half-clutch state to the connected state.

  The transmission 1 can travel repeatedly starting and stopping or traveling at a low vehicle speed by operating the hydraulic power transmission device 60 with the clutch 3 in a connected state at the first speed and a reverse speed described later. .

(Forward high speed)
When the vehicle speed rises above a certain speed after the forward start, a shift to a high speed stage is performed based on a shift map preset in the automatic transmission unit 1B.

  In response to a command from the automatic transmission unit 1B, the clutch 3 is controlled to be disengaged, the 1-R switching device 41 is operated, the first speed driven gear 31 is released from the second countershaft 30, and the second to third speed The switching device 42 is operated and the second speed driven gear 22 is coupled to the first counter shaft 20 to form the second speed stage. Thereafter, the clutch 3 is controlled to be connected.

  The power of the engine 2 is transmitted to the input shaft 10 and transferred from the second speed drive gear 12 fixed to the input shaft 10 to the first counter shaft 20 via the second speed driven gear 22 coupled to the first counter shaft 20. introduce.

  Thereafter, the power is transmitted from the first output gear 28 fixed to the first counter shaft 20 to the first final gear 51 fixed to the output shaft 50, so that the power is transmitted to the output shaft 50, and the vehicle is in the second speed stage. Run.

  Thereafter, the upshift and the downshift are similarly performed between the second speed and the sixth speed based on a shift map set in advance in the automatic transmission unit 1B.

  The transmission 1 is in a high speed stage, and only the clutch 3 is present in the power transmission path as a power transmission device. The clutch 3 is switched between the disconnected state and the connected state in a short time only when shifting. That is, the transmission 1 performs a shift at the high speed in the same manner as a normal AMT.

(Reverse speed)
When the driver selects a reverse gear (for example, R range) using a shift lever (not shown), the 1-R switching device 41 is operated by a command from the automatic transmission unit 1B, and the reverse gear driven gear 37 is coupled to the second counter shaft 30. Thus, a reverse speed stage is formed.

  Thereafter, when the driver operates an accelerator pedal (not shown) and tries to start, the clutch 3 is controlled from the half-clutch state to the connected state according to a command from the automatic transmission unit 1B.

  The motive power of the engine 2 is transmitted to the input shaft 10, via a second speed driven gear 22 that is rotatably arranged on the first counter shaft 20 from the second speed drive gear 12 fixed to the input shaft 10, and the second speed driven The transmission is transmitted from the reverse drive gear 27 that rotates integrally with the gear 22 to the input side element of the hydraulic power transmission device 60 via the reverse drive gear 37 coupled to the second counter shaft 30.

  That is, the first counter shaft 20 and the pair of the second speed driven gear 22 and the reverse speed drive gear 27 that are rotatably arranged on the first counter shaft 20 constitute a reverse idler gear shaft, and the input shaft 10 Between the first counter shaft 30 and the second counter shaft 30, there is one more transmission path than the power transmission path during forward travel, and the second counter shaft 30 rotates in a direction opposite to the rotational direction during forward travel.

  Thereafter, the motive power is transmitted to the output side transmission element by hydraulic pressure, and is transmitted to the output disk shaft 61 connected to the output side transmission element.

  Finally, the power is transmitted from the second output gear 68 fixed to the output disk shaft 61 to the second final gear 52 fixed to the output shaft 50, so that the power is transmitted to the output shaft 50 and the vehicle moves backward.

  Next, the operation will be described. In the transmission 1 according to the present embodiment, a hydraulic power transmission device 60 is provided on the second countershaft 30 that is a power transmission path shared by the first gear and the reverse gear.

  As a result, when the shift stage is the first speed stage or the reverse speed stage, the clutch 3 and the hydraulic power transmission device 60 are compatible with each other in the power transmission path. Can be adjusted by the hydraulic power transmission device 60 after the clutch is connected for a short time in the half-clutch state.

  Thereby, the time of the clutch 3 in a half-clutch state can be shortened, wear of the clutch 3 can be reduced, and power transmission efficiency can be improved.

  Further, when the gear stage is a high speed stage of 2 or more speeds, the power transmitted to the input shaft 10 is transmitted to the output shaft 50 without passing through the hydraulic power transmission device 60. The power transmission efficiency can be improved by passing through the stepped transmission 4 with good quality.

  Therefore, wear of the clutch 3 can be reduced and power transmission efficiency can be improved.

  Further, the transmission 1 of the present embodiment is arranged in parallel with the first final gear 51 and the first final gear 51 and the second final gear 52 provided on the output shaft 50 and the first final gear 51. A first counter shaft 20 provided with an output gear 28 and a second counter shaft 30 disposed in parallel with the input shaft 10 are provided.

  Further, the input shaft 10 has a first speed drive gear 11 that forms a first speed stage, and a plurality of high speed drive gears that form a plurality of high speed stages, a second speed drive gear 12, a third speed drive gear 13, and a fourth speed drive gear 14 A 5-speed drive gear 15 is provided.

  Further, the first counter shaft 20 has a second speed driven gear 22, a third speed driven gear 23, a fourth speed driven gear 24, a fifth speed driven gear 25, and a second speed driven gear 25 as a plurality of high speed driven gears that mesh with these high speed driving gears. A reverse drive gear 27 that rotates integrally with the fast driven gear 22 is provided.

  Further, the first counter driven gear 31 that meshes with the first speed drive gear 11, the reverse speed driven gear 37 that meshes with the reverse speed drive gear 27, the hydraulic power transmission device 60, and the second counter shaft 30. An output disk shaft 61 coaxially disposed on the outer peripheral side of the shaft 30 and connected to the other end of the hydraulic power transmission device 60, and a second output gear 68 fixed to the output disk shaft 61 and meshing with the second final gear 52 , Is provided.

  The transmission 1 forms a first gear stage by switching the power transmission path so that the power of the input shaft 10 is transmitted to the first speed driven gear 31, and the power of the input shaft 10 is transmitted to any one of the plurality of high speed driven gears. The reverse speed stage is formed by switching the power transmission path so as to transmit to the reverse speed driven gear via one high speed driven gear. Further, the transmission 1 forms a high-speed stage by switching the power transmission path so as to transmit the power of the input shaft 10 to the high-speed driven gear.

  In addition, in the transmission 1, the hydraulic power transmission device 60 transmits the power of the second counter shaft 30 to the output disk shaft 61 by hydraulic pressure at the first speed and the reverse speed.

  According to the above configuration, in order to form the reverse speed stage, the power transmission path is such that the power of the input shaft 10 is transmitted to the reverse speed driven gear via any one of the plurality of high speed driven gears. Therefore, the reverse idler shaft for the reverse speed stage can be eliminated. Thereby, the transmission 1 can be reduced in size.

  Further, in the transmission 1 of the present embodiment, in the second countershaft 30, the first speed driven gear 31 and the reverse speed driven gear 37 are arranged on one end side close to the engine 2, and the second output gear 68 is far from the engine 2. It is arranged on the other end side. Here, since the hydraulic power transmission device 60 is formed of a fluid coupling having a small radial size, it can be disposed inside the transmission case 1C, unlike a torque converter having a large radial size. In the present embodiment, the hydraulic power transmission device 60 is disposed between the first speed driven gear 31 and the second output gear 68 on the second countershaft 30 in the transmission case 1C.

  According to the above configuration, the hydraulic power transmission device 60 can be disposed in the axially central portion where the first speed driven gear 31 and the reverse speed driven gear 37 are not disposed on the second counter shaft 30. Therefore, the input shaft 10, the first counter shaft 20, and the second counter shaft 30 can be arranged close to each other in the radial direction. Thereby, the size of the transmission 1 in the radial direction can be shortened, and the transmission 1 can be downsized.

  In addition, since a large load due to power transmission acts on the first speed driven gear 31 and the reverse speed driven gear 37, the first speed driven gear 31 and the reverse speed driven gear 37 are temporarily arranged at the center of the second counter shaft 30. The second countershaft 20 is displaced in the bending direction. In order to avoid this, when the bearing is arranged at the center of the second countershaft 30, the arrangement of other rotating elements is restricted.

  On the other hand, in the present embodiment, since the first speed driven gear 31 and the reverse speed driven gear 37 are disposed on one end side close to the engine 2 in the second counter shaft 30, one end portion of the first counter shaft 30 is It can be supported by the bearing 7A, and the first countershaft 30 can be prevented from bending.

  In addition, the transmission 1 of the present embodiment includes a third speed drive gear 13, which is a high speed drive gear, a fourth speed drive gear 14, a fifth speed drive gear 15, and a third speed driven gear 23 which is a high speed driven gear. A pair of high-speed gears including the 24-speed driven gear 25 and the fifth-speed driven gear 25 are arranged in the axial direction of the transmission 1 within a range in the length direction of the hydraulic power transmission device 60.

  According to the above configuration, since the high-speed gear pair has a small diameter, the small-diameter high-speed gear pair can be disposed adjacent to the hydraulic power transmission device 60 in the radial direction. For this reason, the high-speed gear pair can be arranged close to the engine 2 in the axial direction of the transmission 1. For this reason, the axial size of the transmission 1 can be shortened, and the transmission 1 can be miniaturized.

  In addition, since the small-diameter high-speed gear pair can be disposed radially adjacent to the hydraulic power transmission device 60, the distance between the input shaft 10, the first counter shaft 20, and the second counter shaft 30 can be shortened. . For this reason, the radial size of the transmission 1 can be shortened, and the transmission 1 can be miniaturized.

  While embodiments of the invention have been disclosed, it will be apparent to those skilled in the art that changes may be made without departing from the scope of the invention. All such modifications and equivalents are intended to be included in the following claims.

  DESCRIPTION OF SYMBOLS 1 ... Transmission, 2 ... Engine (drive source), 3 ... Clutch (friction clutch), 4 ... Step transmission, 10 ... Input shaft, 11 ... First speed drive Gear: 12 ... 2 speed drive gear (high speed drive gear), 13 ... 3 speed drive gear (high speed drive gear), 14 ... 4 speed drive gear (high speed drive gear), 15 ... 5 speed Drive gear (high-speed drive gear), 20 ... first counter shaft, 22 ... 2-speed driven gear (high-speed driven gear), 23 ... 3-speed driven gear (high-speed driven gear), 24 ... 4 High-speed driven gear (high-speed driven gear), 25 ... 5-speed driven gear (high-speed driven gear), 27 ... reverse drive gear, 28 ... first output gear, 30 ... second counter shaft, 31 ... First-speed driven gear, 37 ... Reverse-speed driven gear, 50 ... Output shaft, 51 ... First final gear, 52 ... Second final gear, 56 ... 6-speed driven Gear, 60 ... Hydraulic power transmission device, 61 ... Output disc shaft 68 ... the second output gear

Claims (4)

An input shaft to which power is transmitted from a driving source via a friction clutch;
An output shaft for outputting the power after shifting;
A transmission provided between the input shaft and the output shaft, wherein a gear stage is formed by meshing of a gear pair and a plurality of gear stages are switched in a stepped manner. ,
It has a hydraulic power transmission device that transmits power by hydraulic pressure,
The plurality of shift speeds include a first speed, which is the slowest speed on the forward side, a plurality of high speeds, which are forward speeds other than the first speed, and a reverse speed, which is the reverse speed. Including steps,
The transmission, wherein the hydraulic power transmission device is provided in a power transmission path shared by the first speed stage and the reverse speed stage. A first final gear and a second final gear provided on the output shaft;
A first counter shaft provided in parallel with the input shaft and provided with a first output gear meshing with the first final gear;
A second counter shaft arranged in parallel with the input shaft,
The input shaft is provided with a first speed drive gear that forms the first speed stage, and a plurality of high speed drive gears that form the plurality of high speed stages,
The first counter shaft is provided with a plurality of high-speed driven gears that respectively mesh with the plurality of high-speed driving gears, and a reverse speed driving gear that rotates integrally with any one of the plurality of high-speed driven gears. And
A first-speed driven gear that meshes with the first-speed drive gear, a reverse-speed driven gear that meshes with the reverse-speed drive gear, the hydraulic power transmission device, and an outer periphery of the second countershaft. An output disk shaft that is coaxially disposed on the side and connected to the other end of the hydraulic power transmission device, and a second output gear that is fixed to the output disk shaft and meshes with the second final gear,
The first gear is formed by switching the power transmission path so that the power of the input shaft is transmitted to the first driven gear.
The reverse speed stage is formed by switching a power transmission path so that the power of the input shaft is transmitted to the reverse speed driven gear via any one of the plurality of high speed driven gears,
The high speed stage is formed by switching the power transmission path so as to transmit the power of the input shaft to the high speed driven gear,
2. The transmission according to claim 1, wherein, in the first speed stage and the reverse speed stage, the hydraulic power transmission device transmits the power of the second counter shaft to the output disk shaft by hydraulic pressure. In the second countershaft, the first speed driven gear and the reverse speed driven gear are arranged on one end side close to the drive source, and the second output gear is arranged on the other end side far from the drive source,
The transmission according to claim 2, wherein the hydraulic power transmission device is disposed between the first-speed driven gear and the second output gear on the second countershaft.   The high-speed gear pair consisting of a plurality of high-speed drive gears and a plurality of high-speed driven gears is disposed in the longitudinal direction of the hydraulic power transmission device in the axial direction of the transmission. The transmission according to claim 2 or claim 3, wherein

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