JP2007285331A - Shift actuator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shift actuator capable of preventing wear and noise from occurring by the cushioning effect of a fluid during the shifting. <P>SOLUTION: In this 3-5 shift actuator 50, a 3-5 shift fork 41 connected to shift pistons 50c, 50c is operated in the shift direction by supplying a pressurizing fluid into one of both fluid chambers 50d, 50d formed in the shift pistons 50c, 50c at both ends during the shifting and discharging the drain fluid charged in the other fluid chamber. Orifices 50e, 50e for suppressing the discharged amount of the drain fluid is set in a circuit into which the drain fluid is discharged according to the stroking operations of the shift pistons 50c, 50c among the operating fluid circuits connected to the both fluid chambers 50d, 50d. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention belongs to the technical field of a shift actuator that uses a working fluid as a working medium and operates a shift operating member connected to a shift piston in a shift direction during shifting.

Conventionally, as a shift actuator for operating a shift fork connected to a shift piston in a shift direction, a shift piston that is disposed in a cylinder hole of an actuator body so as to be capable of stroke and connected to the shift fork, and both ends of the shift piston There is known a fluid chamber formed in a surface position and a shared working fluid circuit connected to each fluid chamber (see, for example, Patent Document 1).
JP 2005-326016 A

  However, in the above-described conventional shift actuator, at the time of shifting, pressurized fluid is supplied from one working fluid circuit to one of the fluid chambers from the working fluid circuit, and the drain fluid filled in the other fluid chamber remains as it is. To discharge from the working fluid circuit, the shift piston end surface and cylinder hole end surface or the shift fork and actuator body abut against each other when the shift actuator is operated, and the abutting portion is worn away or contacted with metal when abutting. There was a problem that abnormal noise was generated.

  The present invention has been made paying attention to the above problem, and an object of the present invention is to provide a shift actuator capable of preventing the occurrence of wear and noise due to a fluid cushion effect during a shift operation.

In order to achieve the above object, in the present invention, a shift piston that is disposed in a cylinder hole of an actuator body so as to be capable of stroke and to which a shift operation member is connected, a fluid chamber formed at both end face positions of the shift piston, With
When shifting, the pressurized fluid is supplied to one of the fluid chambers and the drain fluid filled in the other fluid chamber is discharged, thereby shifting the shift operation member connected to the shift piston. In the shift actuator that operates in the direction
Of the working fluid circuits connected to the two fluid chambers, a flow path restricting portion that suppresses the drain fluid discharge amount is set in a circuit that drains the drain fluid according to the stroke operation of the shift piston.

Therefore, in the shift actuator of the present invention, during the shift operation in which the pressurized fluid is supplied to one of the fluid chambers formed at the both end face positions of the shift piston, the other according to the stroke operation of the shift piston. The drain fluid filled in the fluid chamber is discharged through the flow restrictor.
That is, during the shift operation, the drain fluid filled in the fluid chamber is discharged while receiving the pushing force according to the stroke operation of the shift piston, but the drain fluid is discharged through the flow restrictor, so that The path restricting portion becomes the discharge resistance, the drain fluid discharge amount is limited, the drain fluid pressure in the fluid chamber is increased, and the stroke speed of the shift piston is decreased.
For this reason, for example, in the stroke region where the end face of the shift piston and the end face of the cylinder hole abut, the drain fluid itself having increased pressure exhibits a fluid cushion effect that acts as a cushion that receives and relaxes the impact force.
As a result, it is possible to prevent the occurrence of wear and noise due to the fluid cushion effect during the shift operation.

  Hereinafter, the best mode for carrying out the shift actuator of the present invention will be described based on Examples 1 to 3 shown in the drawings.

First, the configuration will be described.
FIG. 1 is a skeleton diagram showing a twin clutch type automatic manual transmission to which the shift actuator of the first embodiment is applied.

[Configuration of transmission input section and shaft]
Hereinafter, the configuration of the transmission input unit and the shaft in the twin clutch type automatic manual transmission to which the shift actuator of the first embodiment is applied will be described.
As shown in FIG. 1, the twin-clutch automatic manual transmission includes a first clutch CA that is engaged at the time of selection of an odd-numbered gear group among a plurality of gear speeds, and an even-numbered one of a plurality of gear speeds. And a second clutch CB that is engaged when a gear group is selected. A transmission case 1, a drive input shaft 2, a torsional damper 3, an oil pump 4, a first transmission input shaft 5, and a second transmission input shaft 6 are provided.

The first clutch CA is for odd gears (first speed, third speed, fifth speed, reverse), and the second clutch CB is an even gear speed (second speed, fourth speed, sixth speed). ).
The drive sides of both clutches CA and CB are connected via a torsional damper 3 to a drive input shaft 2 for inputting a rotational drive force from a power source such as an engine.

The driven side of the first clutch CA inputs a rotational driving force from a power source such as an engine to the first transmission input shaft 5 at the time of engagement by selecting an odd gear.
The driven side of the second clutch CB inputs a rotational driving force from a power source such as an engine to the second transmission input shaft 6 at the time of engagement by selection of the even gear.

  The oil pump 4 is always operated by the engine E. The oil discharged from the oil pump 4 is used as a hydraulic pressure source, and the engagement / release control of both clutches CA and CB and the shift speed selection control by the shift actuator are executed. Then, the excess oil is used as a lubricating oil to lubricate necessary parts.

  The second transmission input shaft 6 is a hollow shaft, the first transmission input shaft 5 is a solid shaft, and is connected to the first transmission input shaft 5 via a front needle bearing 7 and a rear needle bearing 8. The second transmission input shaft 6 is rotatably supported in a concentric state.

  The second transmission input shaft 6 is rotatably supported by a ball bearing 9 with respect to the front wall 1 a of the transmission case 1. The first transmission input shaft 5 protrudes from the rear end of the second transmission input shaft 6, and the rear end portion 5 a of the protruding first transmission input shaft 5 passes through the intermediate wall 1 b of the transmission case 1. At the same time, it is rotatably supported by the ball bearing 10 with respect to the intermediate wall 1b.

  The rear end portion 5 a of the first transmission input shaft 5 is provided with a transmission output shaft 11 on the same axis. The transmission output shaft 11 is connected to the rear end wall of the transmission case 1 by a tapered roller bearing 12 and an axial bearing 13. The first transmission input shaft 5 is rotatably supported on the rear end portion 5a of the first transmission input shaft 5 via the needle bearing 14.

  A counter shaft 15 is provided in parallel with the first transmission input shaft 5, the second transmission input shaft 6, and the transmission output shaft 11, and this is connected to the transmission case 1 via roller bearings 16, 17, 18. The front end wall 1a, the intermediate wall 1b, and the rear end wall 1c are rotatably supported.

[Configuration of transmission mechanism]
Next, the structure of the speed change mechanism in the twin clutch type automatic manual transmission to which the shift actuator of the first embodiment is applied will be described.
As shown in FIG. 1, the twin-clutch automatic manual transmission has a synchronous meshing mechanism as a speed change mechanism, and is a constantly meshing type that achieves six forward speeds and one reverse speed with a plurality of gear pairs having different gear ratios. It has a gear train.

  A park gear 69 and a counter gear 19 are integrally provided at the rear end of the counter shaft 15, an output gear 20 is provided on the transmission output shaft 11, and the counter gear 19 and the output gear 20 are engaged with each other to counter the counter shaft. 15 is drive-coupled to the transmission output shaft 11. The counter gear 19 and the output gear 20 constitute a fifth speed gear set G5.

  Between the rear end portion 5a of the first transmission input shaft 5 and the countershaft 15, there is a gear group of an odd gear group (first speed, third speed, reverse), that is, in order from the front side. A first speed gear set G1, a reverse gear set GR, and a third speed gear set G3 are arranged.

  The first speed gear set G1 meshes a first speed input gear 21 provided at the rear end portion 5a of the first transmission input shaft 5 and a first speed output gear 22 provided on the counter shaft 15 with each other. Configure together.

  The reverse gear set GR includes a reverse input gear 23 provided at the rear end 5a of the first transmission input shaft 5, a reverse output gear 24 provided on the countershaft 15, and a reverse idler meshing with both gears 23,24. And a gear 25. The reverse idler gear 25 is rotatably supported with respect to a reverse idler shaft 25a protruding from the intermediate wall 1b of the transmission case 1.

  The third speed gear set G3 meshes a third speed input gear 26 provided at the rear end 5a of the first transmission input shaft 5 and a third speed output gear 27 provided on the countershaft 15. Configure together.

  A 1-R synchronous mesh mechanism 28 is provided on the countershaft 15 between the first speed gear set G1 and the reverse gear set GR. The first speed output gear 22 is driven to the countershaft 15 by causing the coupling sleeve 28a of the 1-R synchronous meshing mechanism 28 to stroke leftward from the illustrated neutral position and to be splined to the clutch gear 28b. The first speed can be selected by combining. Further, the coupling sleeve 28a of the 1-R synchronous meshing mechanism 28 is stroked to the right from the neutral position shown in the drawing, and the clutch gear 28c is spline-fitted to drive the reverse output gear 24 to the countershaft 15. The reverse speed can be selected.

  On the rear end portion 5a of the first transmission input shaft 5 between the third speed gear set G3 and the output gear 20, a 3-5 synchronous meshing mechanism 29 is provided. Then, the third-speed input gear 26 is input to the first transmission by causing the coupling sleeve 29a of the 3-5 synchronous mesh mechanism 29 to stroke leftward from the neutral position shown in the figure and to be spline-fitted to the clutch gear 29b. Drive-coupled to the shaft 5 allows the third speed to be selected. Further, the coupling sleeve 29a of the 3-5 synchronous meshing mechanism 29 is stroked to the right from the neutral position shown in the figure, and is splined to the clutch gear 29c, whereby the first transmission input shaft 5 and the output gear 20 are Is directly connected and the fifth speed can be selected.

  Between the second transmission input shaft 6 and the countershaft 15, a gear set of an even-numbered speed group (second speed, fourth speed, sixth speed), that is, a sixth speed gear in order from the front side. A set G6, a second speed gear set G2, and a fourth speed gear set G4 are arranged.

  The sixth speed gear set G6 is configured by meshing a sixth speed input gear 30 provided on the second transmission input shaft 6 and a sixth speed output gear 31 provided on the countershaft 15.

  The second speed gear set G2 is configured by meshing a second speed input gear 32 provided on the second transmission input shaft 6 and a second speed output gear 33 provided on the countershaft 15.

  The fourth speed gear set G4 is configured by meshing a fourth speed input gear 34 provided on the second transmission input shaft 6 and a fourth speed output gear 35 provided on the countershaft 15.

  A 6-N synchronous meshing mechanism 37 is provided on the counter shaft 15 on the side of the sixth speed gear set G6. Then, the sixth speed output gear 31 is driven to the countershaft 15 by causing the coupling sleeve 37a of the 6-N synchronous meshing mechanism 37 to stroke leftward from the illustrated neutral position and to be splined to the clutch gear 37b. Combined, the 6th speed can be selected.

  A 2-4 synchronous meshing mechanism 38 is provided on the countershaft 15 between the second speed gear set G2 and the fourth speed gear set G4. Then, the second-speed output gear 33 is driven to the countershaft 15 by causing the coupling sleeve 38a of the 2-4 synchronous meshing mechanism 38 to stroke leftward from the neutral position shown in the figure and to be splined to the clutch gear 38b. Combined, the second speed can be selected. Further, the 4th-speed output gear 35 is driven to the countershaft 15 by causing the coupling sleeve 38a of the 2-4 synchronous meshing mechanism 38 to stroke rightward from the neutral position shown in the figure and to be splined to the clutch gear 38c. Combined to enable selection of 4th speed.

[Configuration of transmission hydraulic control system and electronic control system]
FIG. 2 is a control system diagram showing a shift hydraulic pressure control system and an electronic control system in a twin clutch type automatic manual transmission to which the shift actuator of the first embodiment is applied.
As shown in FIG. 2, the twin clutch type automatic manual transmission includes a 3-5 shift fork 41, a 1-R shift fork 42, a 6-N shift fork 43, 2 -4 shift fork 44, first control valve unit 45, second control valve unit 46, and automatic MT controller 47 are provided.

  The 3-5 shift fork 41 is engaged with the coupling sleeve 29 a of the 3-5 synchronous meshing mechanism 29 and is fixed to the first shift rod 48. The first shift rod 48 is supported so as to be movable in the axial direction with respect to the front end wall 1 a and the intermediate wall 1 b of the transmission case 1. Then, the 3-5 shift bracket 49 is fixed to the first shift rod 48, and the end portion of the 3-5 shift bracket 49 is loosely supported by the spool connecting shaft portion of the 3-5 shift actuator 50. That is, the 3-5 shift fork 41 strokes leftward (when the third speed is selected) or rightward (when the fifth speed is selected) from the illustrated neutral position according to the spool operation of the 3-5 shift actuator 50. .

  The 1-R shift fork 42 is engaged with the coupling sleeve 28a of the 1-R synchronous meshing mechanism 28, and is provided on the second shift rod 51 so as to be capable of stroke in the axial direction. The second shift rod 51 is provided in a fixed state in the axial direction with respect to the front end wall 1 a and the intermediate wall 1 b of the transmission case 1. The end portion of the bracket arm portion 42b that is integrally formed with the bracket cylindrical portion 42a of the 1-R shift fork 42 is idled and supported by the spool connecting shaft portion of the 1-R shift actuator 52. That is, the 1-R shift fork 42 strokes from the neutral position shown in the drawing to the left (when the first speed is selected) or right (when the reverse speed is selected) according to the spool operation of the 1-R shift actuator 52.

  The 6-N shift fork 43 is engaged with the coupling sleeve 37 a of the 6-N synchronous meshing mechanism 37, and is provided on the second shift rod 51 fixed in the axial direction with respect to the transmission case 1 so as to be capable of stroke in the axial direction. Then, the end portion of the bracket arm portion 43 b formed integrally with the bracket cylindrical portion 43 a of the 6-N shift fork 43 is idled and supported by the spool connecting shaft portion of the 6-N shift actuator 53. That is, the 6-N shift fork 43 strokes from the neutral position shown in the drawing to the left (when the sixth speed is selected) according to the spool operation of the 6-N shift actuator 53.

  The 2-4 shift fork 44 is engaged with the coupling sleeve 38 a of the 2-4 synchronous meshing mechanism 38, and is provided on the second shift rod 51 fixed in the axial direction with respect to the transmission case 1 so as to be capable of stroke in the axial direction. The end portion of the bracket arm portion 44b formed integrally with the bracket cylindrical portion 44a of the 2-4 shift fork 44 is loosely supported by the spool connecting shaft portion of the 2-4 shift actuator 54. That is, the 2-4 shift fork 44 strokes from the neutral position shown in the figure to the left (when the second speed is selected) or right (when the fourth speed is selected) according to the spool operation of the 2-4 shift actuator 54. .

As shown in FIG. 2, the first control valve unit 45 includes a line pressure solenoid valve 70 that regulates the line pressure PL based on the oil discharged from the oil pump 4, and the shift actuator 50. , 51, 52, 53, the first clutch pressure solenoid valve 71 for generating the clutch control pressure for the first clutch CA based on the even speed step pressure Pe from the actuator hydraulic control valve 59 for generating the actuator operating pressure, and the odd speed shift And a second clutch pressure solenoid valve 72 for generating a clutch control pressure for the second clutch CB based on the step pressure Po.
The oil pump 4 and the line pressure solenoid valve 70 are connected by a pump pressure oil passage 73.
The line pressure solenoid valve 70 and the actuator hydraulic control valve 59 are connected by a line pressure oil passage 74.
The first clutch pressure solenoid valve 71 and the actuator hydraulic pressure control valve 59 are connected by an even-speed gear pressure oil passage 75.
The second clutch pressure solenoid valve 72 and the actuator hydraulic pressure control valve 59 are connected by an odd gear speed pressure oil passage 76.
The first clutch pressure solenoid valve 71 and the clutch oil chamber of the first clutch CA are connected by a first clutch pressure oil passage 77. The first clutch pressure oil passage 77 is provided with a first clutch pressure sensor (not shown).
The second clutch pressure solenoid valve 72 and the clutch oil chamber of the second clutch CB are connected by a second clutch pressure oil passage 78. The second clutch pressure oil passage 78 is provided with a second clutch pressure sensor (not shown).

  As shown in FIG. 2, the second control valve unit 46 includes a second valve body 82, a 3-5 shift actuator 50, a 1-R shift actuator 52, a 6-N shift actuator 53, and 2-4. Shift actuator 54, 3-5 shift position sensor 55, 1-R shift position sensor 56, 6-N shift position sensor 57, 2-4 shift position sensor 58, actuator hydraulic control valve 59 (for shift control) Control valve).

  The actuator hydraulic control valve 59 generates an even speed step pressure Pe and an odd speed step pressure Po based on the line pressure PL adjusted by the first control valve unit 45, and further according to the selected speed step. Actuator operating pressure is supplied to each shift pressure oil passage to each shift actuator 50, 52, 53, 54.

  The automatic MT controller 47 inputs information from a vehicle speed sensor 60, an accelerator opening sensor 61, a range position sensor 62, and other sensors / switches 63, and performs clutch engagement control for each valve solenoid of the first control valve unit 45. A command (including a line pressure control command) is output, and a gear selection control command is output to each valve solenoid of the actuator hydraulic control valve 59.

[Control valve unit layout]
Next, the arrangement configuration of the first control valve unit 45 and the second control valve unit 46 will be described.
First, in the first embodiment, as shown in FIGS. 1 and 2, in the twin clutch type automatic manual transmission, the transmission case 1 is provided with a hydraulic control valve for generating a control hydraulic pressure to the transmission element that is hydraulically operated at the time of shifting. Among the hydraulic control valves, the clutch control control valves 70, 71, 72 for controlling both clutches CA, CB provided in the transmission input section are selected, and the selected clutch control control valves 70, 71, 72 are selected. The clutches CA and CB are disposed close to each other.

  As shown in FIG. 1, the clutch control valves 70, 71, 72 are side portions of both clutches CA, CB provided in the transmission input portion, and are the same as the clutches CA, CB. It is arranged at a position higher than the height.

  The valve body of the hydraulic control valve includes a first valve body 81 that houses the clutch control control valves 70, 71, 72, and a second valve body 82 that houses an actuator hydraulic control valve 59 that controls the gear ratio of the transmission mechanism. The clutch control valve 70, 71, 72 and the first valve body 81 constitute a first control valve unit 45, and the actuator hydraulic control valve 59 and the second valve body 82 constitute a second control valve. A unit 46 is configured, and the first control valve unit 45 and the second control valve unit 46 are arranged at different positions of the transmission case 1.

  As shown in FIG. 1, the specific valve unit arrangement is such that the transmission case 1 includes an oil pump 4 provided at a transmission input portion, a clutch case portion 1d for accommodating both clutches CA and CB, and a gear train. A first transmission mechanism case portion 1e and a second transmission mechanism case portion 1f are divided, the first control valve unit 45 is disposed at a side position of the clutch case portion 1d, and the second control valve unit 46 is disposed. The transmission mechanism case portions 1e and 1f are disposed at the bottom position.

[Configuration of shift actuator]
Next, the structure of the shift actuator of Example 1 is demonstrated based on FIG.
FIG. 3 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 according to the first embodiment.
Here, the 3-5 shift actuator 50 will be described as an example, but the other 1-R shift actuator 52, 6-N shift actuator 53, and 2-4 shift actuator 54 also have the same configuration.

  As shown in FIG. 3, the 3-5 shift actuator 50 is arranged so that it can be stroked in the cylinder holes 50b, 50b of the actuator bodies 50a, 50a, and the shift pistons 50c, 50c to which the 3-5 shift fork 41 is connected. And fluid chambers 50d and 50d formed at both end face positions of the shift pistons 50c and 50c, and at the time of shift, supply pressurized fluid to one of the fluid chambers 50d and 50d, By discharging the drain fluid filled in the other fluid chamber, the 3-5 shift fork 41 connected to the shift pistons 50c, 50c is operated in the shift direction.

  Of the working fluid circuits connected to the fluid chambers 50d and 50d, the orifices 50e and 50e that suppress the drain fluid discharge amount only to the circuit that drains the drain fluid according to the stroke operation of the shift pistons 50c and 50c. (Channel restrictor) is set.

  The orifices 50e and 50e are not set in a circuit for supplying pressurized fluid to both the fluid chambers 50d and 50d, but are set only in a circuit in which drain fluid is discharged along with the stroke operation of the shift pistons 50c and 50c. .

  The orifices 50e and 50e are set in a circuit in which the drain fluid is discharged after the stroke amount of the shift pistons 50c and 50c has moved beyond the neutral position shown in FIG.

The configuration of the 3-5 shift actuator 50 according to the first embodiment will be described in detail. As shown in FIG. 3, the shift pistons 50c and 50c are divided into large-diameter piston portions 50c1 and 50c1, small-diameter piston portions 50c2 and 50c2, and pistons. A stepped piston having step surfaces 50c3 and 50c3 is provided.
The cylinder holes 50b and 50b are stepped cylinder holes having large diameter cylinder holes 50b1 and 50b1, small diameter cylinder holes 50b2 and 50b2, and body step surfaces 50b3 and 50b3.

  As the fluid chambers 50d and 50d, the first fluid chambers 50d1 and 50d1 surrounded by the end surfaces of the small-diameter piston portions 50c2 and 50c2 and the small-diameter cylinder holes 50b2 and 50b2, the peripheral surfaces of the small-diameter piston portions 50c2 and 50c2, and the piston step surface 50c3. , 50c3, body step surfaces 50b3, 50b3 and second fluid chambers 50d2, 50d2 surrounded by large-diameter cylinder holes 50b1, 50b1.

  The working fluid circuit is connected to main circuits 50f and 50f connected to end surface positions of the first fluid chambers 50d1 and 50d1, and to body step surface positions of the second fluid chambers 50d2 and 50d2 and main circuits 50f and 50f. The sub-circuits 50g and 50g, the orifices 50e and 50e set in the middle of the sub-circuits 50g and 50g, and both circuit ends are connected to the sub-circuits 50g and 50g, and bypass the orifices 50e and 50e. And two-way circuits 50h, 50h that permit only one-way flow from the fluid chambers 50d2, 50d2 to the main circuits 50f, 50f.

  The position of the 3-5 shift fork 41 is held by a check force even if there is no input from the 3-5 shift actuator 50. That is, as shown in FIG. 3, the check ball 90 biased by the check spring 91 has a third speed position ball hole 92, a neutral position ball hole 93 and a fifth speed position ball hole 94 formed in the second shift rod 51. And urgingly fitted into any one of the holes.

Next, the operation will be described.
A manual transmission (manual transmission) has the advantage of simple structure and high efficiency, but all the drivers must perform a shifting operation. Therefore, an automatic manual transmission is referred to as an automatic transmission having a mechanism for automating the shift operation while retaining the advantages of the manual transmission.
The problem with this automatic manual transmission is that the clutch is temporarily disengaged at the time of shifting, so that a sense of incongruity remains due to the torque being interrupted at the time of automatic shifting. In order to solve this problem, it is necessary to eliminate the break in torque. An ordinary manual transmission has one set of clutches. A twin clutch type automatic manual transmission is obtained by adding another set of clutches and switching the two sets of clutches to eliminate torque interruption.
In this twin-clutch automatic manual transmission, at the time of shifting to an adjacent shift stage, first, the actuator hydraulic control valve 59 precedes the clutch change control, and the next shift stage is selected from among the clutch shift stage groups that have been released. And the shift hydraulic pressure to the shift actuator that operates the shift fork in the direction to obtain the selected gear stage is created, and then the first clutch CA and the second clutch CB are used in the clutch control control valves 70, 71, 72. The shift control hydraulic pressure is created, and the gear shift without torque interruption is performed. Hereinafter, the shift operation in the twin clutch type automatic manual transmission to which the shift actuator of the first embodiment is applied will be described.

[Shifting action]
When selecting the neutral position (N range) or the parking position (P range), both the clutches CA and CB are opened, and the shift actuators 50, 52, 53, and 54 are all set to the neutral positions shown in FIG. Keep it. That is, the coupling sleeves 28a, 29a, 37a, 38a of the synchronous mesh mechanisms 28, 29, 37, 38 are all maintained in the neutral position so that the twin clutch automatic manual transmission does not transmit power.

When the D range, R range or manual mode (= manual shift mode by driver operation) for which power transmission is desired is selected, the shift is basically performed according to the following procedure.
At the first speed, the 1-R shift actuator 52 is controlled to move leftward in FIG. 3 to move the coupling sleeve 28a of the synchronous meshing mechanism 28 leftward in FIG. 15 and then the first clutch CA is engaged.
Thus, the drive input from the first clutch CA is axially transmitted by the transmission output shaft 11 via the first transmission input shaft 5 → the first speed gear set G1 → the counter shaft 15 → the output gear sets 19 and 20. Is output and power transmission at the first speed is performed.

When the upshift from the first speed to the second speed is performed, the 2-4 shift actuator 54 is controlled to move leftward in FIG. 3 so that the coupling sleeve 38a of the synchronous meshing mechanism 38 is moved leftward in FIG. The gear 33 is drivably coupled to the countershaft 15, and then the first clutch CA is released and the second clutch CB is engaged (clutch change) to upshift from the first speed to the second speed. I do.
Thus, the drive input from the second clutch CB is axially transmitted by the transmission output shaft 11 via the second transmission input shaft 6 → second speed gear set G2 → counter shaft 15 → output gear sets 19 and 20. The second power transmission is performed.

When the upshift from the second speed to the third speed is performed, the 3-5 shift actuator 50 is controlled to operate in the left direction in FIG. 3 so that the coupling sleeve 29a of the synchronous mesh mechanism 29 is moved in the left direction in FIG. To the first transmission input shaft 5, and then the second clutch CB is released and the first clutch CA is engaged (clutch switching) to change from the first speed to the second speed. Upshift to.
As a result, the drive input from the first clutch CA is axially transmitted by the transmission output shaft 11 via the first transmission input shaft 5 → the third speed gear set G3 → the counter shaft 15 → the output gear sets 19 and 20. The third power transmission is performed.

When the upshift from the third speed to the fourth speed is performed, the 2-4 shift actuator 54 is controlled to move rightward in FIG. 3 so that the coupling sleeve 38a of the synchronous meshing mechanism 38 is moved rightward in FIG. The gear 35 is driven to the countershaft 15 and then the first clutch CA is disengaged and the second clutch CB is engaged (clutch switching) to upshift from the third speed to the fourth speed. I do.
Thus, the drive input from the second clutch CB is axially transmitted by the transmission output shaft 11 via the second transmission input shaft 6 → the fourth speed gear set G4 → the counter shaft 15 → the output gear sets 19 and 20. The fourth power transmission is performed.

When the upshift from the fourth speed to the fifth speed is performed, the 3-5 shift actuator 50 is controlled to move in the right direction in FIG. 3 so that the coupling sleeve 29a of the synchronous meshing mechanism 29 is moved in the right direction in FIG. The first transmission input shaft 5 is directly connected to the transmission output shaft 11, and then the second clutch CB is released and the first clutch CA is engaged (clutch switching) to change from the fourth speed to the fourth speed. Upshift to 5th speed.
As a result, the drive input from the first clutch CA is axially transmitted by the transmission output shaft 11 via the first transmission input shaft 5 → the third speed gear set G3 → the counter shaft 15 → the output gear sets 19 and 20. Is output and power transmission at the fifth speed (speed ratio 1) is performed.

At the time of upshifting from the fifth speed to the sixth speed, by controlling the 6-N shift actuator 53 to move leftward in FIG. 3, the coupling sleeve 37a of the synchronous meshing mechanism 37 is moved leftward in FIG. The gear 31 is drivably coupled to the countershaft 15 and then the first clutch CA is released and the second clutch CB is engaged (clutch switching) to shift up from the fifth speed to the sixth speed. I do.
Thus, the drive input from the second clutch CB is axially transmitted by the transmission output shaft 11 via the second transmission input shaft 6 → the sixth speed gear set G6 → the counter shaft 15 → the output gear sets 19 and 20. Is output and power transmission at the sixth speed is performed. In addition, when the downshift is sequentially performed from the sixth speed to the first speed, the control opposite to the upshift is performed.

When the R range is selected, the 1-R shift actuator 52 is controlled to move rightward in FIG. 3 to move the coupling sleeve 28a of the synchronous meshing mechanism 28 rightward in FIG. 15 and then the first clutch CA is engaged.
As a result, the drive input from the first clutch CA is output in the axial direction by the transmission output shaft 11 via the first transmission input shaft 5 → the reverse gear set GR → the counter shaft 15 → the output gear sets 19 and 20. Then, reverse speed power transmission is performed.

[Shift operation by shift actuator]
Conventionally, as a shift actuator for operating a shift fork connected to a shift piston in the shift direction, as shown in FIG. 4, a shift piston arranged in a cylinder hole of an actuator body so as to be capable of stroke and connected to the shift fork. And a fluid chamber formed at both end face positions of the shift piston, and a common working fluid circuit connected to the fluid chamber and connected to the fluid chamber are known.

  However, in the shift actuator shown in FIG. 4, when shifting, pressurized fluid is supplied from the working fluid circuit to one of the fluid chambers, and the drain fluid filled in the other fluid chamber is supplied. Because it is discharged from the working fluid circuit as it is, when the shift actuator is operated, the shift piston end face and cylinder hole end face that become the stroke stopper, or the shift fork and actuator body abut against each other, and the part that comes into contact with a large force wears out. An abnormal noise occurs due to metal contact at the time of butting.

  On the other hand, in the shift actuator of the first embodiment, during the shift operation, it is possible to prevent the occurrence of wear and noise due to the fluid cushion effect.

  In other words, when a cushion member is added mechanically, even if it is possible to temporarily prevent the generation of abnormal noise, the cushion member itself is heavily worn away. Focusing on the point that it cannot be a practical solution, the strokes of the shift pistons 50c, 50c in the working fluid circuit connected to both fluid chambers 50d, 50d formed at the positions of both end faces of the shift pistons 50c, 50c A configuration is adopted in which orifices 50e and 50e for suppressing the discharge amount of the drain fluid are set in the sub-circuits 50g and 50g from which the drain fluid is discharged according to the operation.

Therefore, during the shift operation in which the pressurized fluid is supplied to one of the fluid chambers 50d and 50d formed at both end surface positions of the shift pistons 50c and 50c, the other is performed according to the stroke operation of the shift pistons 50c and 50c. The drain fluid filled in the fluid chamber 50d is discharged through the orifice 50e.
That is, during the shift operation, the drain fluid filled in the fluid chamber 50d is discharged while receiving the pushing force according to the stroke operation of the shift pistons 50c and 50c, but the drain fluid is discharged through the orifice 50e. The orifice 50e becomes a discharge resistance, the drain fluid discharge amount is limited, the drain fluid pressure in the fluid chamber 50d increases, and the stroke speed of the shift pistons 50c, 50c decreases.
For this reason, for example, in the stroke region where the end face of the shift piston and the end face of the cylinder hole abut, the drain fluid itself having increased pressure exhibits a fluid cushion effect that acts as a cushion that receives and relaxes the impact force.
As a result, it is possible to prevent the occurrence of wear and noise due to the fluid cushion effect during the shift operation.

[3-5 Shift operation by shift actuator]
As an example of the shift operation by the shift actuator, the shift operation from the fifth speed to the third speed by the 3-5 shift actuator 50 will be described.

  First, when the fifth speed is selected, the shift pistons 50c and 50c of the 3-5 shift actuator 50 are located on the right side of the neutral position shown in FIG. And the fifth speed position ball hole 94, the fifth speed selection position is maintained. That is, the fluid chambers 50d and 50d, the main circuits 50f and 50f, and the sub-circuits 50g and 50g are only filled with the working fluid (oil) at the atmospheric pressure level.

  When a shift command to the third speed is output in the fifth speed selected state, the shift hydraulic pressure is supplied from the main circuit 50f on the right side of FIG. 3, and among the shift pistons 50c on the right side of FIG. On the end face, the transmission hydraulic pressure acts via the main circuit 50f → the first fluid chamber 50d1, and on the piston step surface 50c3, the main circuit 50f → the sub circuit 50g → the one-way circuit 50h → the sub circuit 50g → the second fluid chamber. Shift hydraulic pressure is applied via 50d2.

Therefore, an oil pressure is generated on the end face of the right shift piston 50c in FIG. 3 by multiplying the pressure receiving area by the shift oil pressure, and the shift pistons 50c, 50c are moved to the right end position (fifth speed position) in FIG. ) To the neural position shown in FIG.
In the stroke region from the right end position (5-th gear position) to the neural position, the left shift piston 50c in FIG. 3 is the right position from the illustrated position, and is formed at the end of the left shift piston 50c. Since the first fluid chamber 50d1 and the second fluid chamber 50d2 are in communication with each other, the working fluid filled in both the fluid chambers 50d1 and 50d2 is connected to the main circuit 50f having a small discharge resistance and the sub circuit 50g having a large discharge resistance. It is discharged quickly via both circuits 50f, 50g.

When the shift pistons 50c, 50c stroke to the neural position shown in FIG. 3, the first fluid chamber 50d1 and the second fluid chamber 50d2 are formed by the small-diameter piston portion 50c2 formed on the end face portion of the left shift piston 50c in FIG. Block communication with.
Therefore, in the region where the shift pistons 50c and 50c stroke from the neutral position to the left end position (third speed position), the working fluid in the second fluid chamber 50d2 is sub-circuit 50g → orifice 50e → sub-circuit 50g → main circuit 50f. It will be discharged through.

  For this reason, the orifice 50e becomes a discharge resistance, the discharge amount of the drain fluid is limited, the drain fluid pressure in the second fluid chamber 50d2 increases, the stroke speed of the shift pistons 50c, 50c decreases, the shift piston end face and the cylinder hole The fluid cushion effect is exhibited in the stroke region where the end surface abuts.

As described above, in the 3-5 shift actuator 50 according to the first embodiment, among the working fluid circuits connected to both the fluid chambers 50d and 50d, the hydraulic fluid is supplied to the fluid chambers 50d and 50d. In addition, orifices 50e and 50e that suppress the discharge amount of the drain fluid are set only in the circuit in which the drain fluid is discharged according to the stroke operation of the shift pistons 50c and 50c.
For example, when an orifice is set in the supply / discharge circuit of the working fluid, the discharge amount of the drain fluid can surely be suppressed, but the supply amount of the pressurized fluid is also reduced, and the stroke operation of the shift piston is started. The rise of force becomes gradual, the shift start response is low, and a long time is required for the shift.
On the other hand, since the orifices 50e and 50e that suppress the drain fluid discharge amount are set only in the circuit from which the drain fluid is discharged, the shift start response is improved and the shift response can be secured.

In the 3-5 shift actuator 50 of the first embodiment, the orifices 50e and 50e are set to a circuit (sub circuit 50g) in which the drain fluid is discharged after the stroke amounts of the shift pistons 50c and 50c are stroked beyond the neutral position.
For example, if an orifice is set in the circuit that drains the drain fluid in the entire stroke area of the shift piston, the stroke response of the slow shift piston is affected by the slowdown of the stroke speed due to the discharge resistance from the start to the end of the stroke. Decreases.
On the other hand, in the first embodiment, the orifices 50e and 50e are set in the circuit where the drain fluid is discharged after the stroke of the neutral position or more, so that a quick stroke operation is ensured up to the neutral position, and the reduction of the shift response is kept small. be able to.

Next, the effect will be described.
In the shift actuator of the first embodiment, the effects listed below can be obtained.

  (1) The shift pistons 50c and 50c, which are disposed in the cylinder holes 50b and 50b of the actuator bodies 50a and 50a so as to be capable of stroke and are connected to the 3-5 shift fork 41, and at both end face positions of the shift pistons 50c and 50c. Fluid chambers 50d and 50d formed, and at the time of shifting, pressurized fluid is supplied to one of the fluid chambers 50d and 50d, and the drain fluid filled in the other fluid chamber is discharged. In the 3-5 shift actuator 50 that moves the 3-5 shift fork 41 connected to the shift pistons 50c, 50c in the shift direction, the working fluid circuit connected to the fluid chambers 50d, 50d The drain fluid is discharged in accordance with the stroke operation of the shift pistons 50c and 50c. Since the orifices 50e and 50e that suppress the discharge amount of the fluid are set, it is possible to prevent the occurrence of wear and noise due to the fluid cushion effect during the shift operation.

  (2) The orifices 50e and 50e are not set in a circuit for supplying pressurized fluid to both fluid chambers 50d and 50d, but are set only in a circuit in which drain fluid is discharged with the stroke operation of the shift pistons 50c and 50c. As a result, the shift start response is improved, and a shift response can be secured.

  (3) The orifices 50e and 50e are set in a circuit in which the drain fluid is discharged after the stroke amount of the shift pistons 50c and 50c is equal to or greater than the neutral position, so that a quick stroke operation is ensured up to the neutral position. The decrease in response can be kept small.

  (4) The transmission having the 3-5 shift fork 41 includes a first clutch CA that is engaged when an odd gear group is selected from among a plurality of gears, and an even gear group is selected from among the plurality of gears. A second clutch CB that is sometimes engaged, and a constantly meshing gear train that has a synchronous meshing mechanism and that achieves a plurality of shift speeds by a plurality of gear pairs having different gear ratios. At the time of a shift, the next shift stage is selected from the shift stage group of the released clutch prior to the switching control of the first clutch CA and the second clutch CB, and is generated by the actuator hydraulic control valve 59. Since it is a twin-clutch automatic manual transmission that operates the shift fork 41 in the direction to obtain the shift stage selected by the shift hydraulic pressure, the automatic shift mode During the shift operation, it is possible to prevent the occurrence of abnormal noise that discomfort to the occupant by the fluid cushion effect.

  (5) The shift pistons 50c and 50c are stepped pistons having small-diameter piston portions 50c2 and 50c2 and piston step surfaces 50c3 and 50c3, and the cylinder holes 50b and 50b are large-diameter cylinder holes 50b1 and 50b1. The cylinder holes 50b2 and 50b2 and the stepped cylinder holes 50b3 and 50b3 are stepped cylinder holes. The fluid chambers 50d and 50d are surrounded by the end surfaces of the small diameter piston portions 50c2 and 50c2 and the small diameter cylinder holes 50b2 and 50b2. The first fluid chambers 50d1, 50d1, the peripheral surfaces of the small diameter piston portions 50c2, 50c2, the piston step surfaces 50c3, 50c3, the body step surfaces 50b3, 50b3, and the large diameter cylinder holes 50b1, 50b1. 50 d 2, 50 d 2, and the working fluid circuit is connected to the end surfaces of the first fluid chambers 50 d 1, 50 d 1. And sub-circuits 50g and 50g connected to the body step surface positions of the second fluid chambers 50d2 and 50d2 and the main circuits 50f and 50f, and orifices 50e and 50e set at intermediate positions of the sub-circuits 50g and 50g, Both circuit ends are connected to the sub-circuits 50g and 50g, and only a one-way flow from the second fluid chambers 50d2 and 50d2 to the main circuits 50f and 50f is permitted while bypassing the orifices 50e and 50e. , 50h, a hydraulic fluid circuit capable of preventing the occurrence of wear and noise due to the fluid cushion effect while minimizing a decrease in the speed change response during the shift operation is provided in the actuator bodies 50a, 50a. It can be configured by an external circuit set to

The second embodiment is an example in which the stroke region where the fluid cushion effect acts is set closer to the stroke end side than the first embodiment.
The control system diagram showing the twin clutch type automatic manual transmission to which the shift actuator of the second embodiment is applied, the transmission hydraulic pressure control system, and the electronic control system is the same as that of the first embodiment shown in FIGS. Illustration and description are omitted.

Next, the configuration of the shift actuator of the second embodiment will be described with reference to FIG.
FIG. 5 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 according to the second embodiment.
Here, the 3-5 shift actuator 50 will be described as an example, but the other 1-R shift actuator 52, 6-N shift actuator 53, and 2-4 shift actuator 54 also have the same configuration.

  As shown in FIG. 5, the 3-5 shift actuator 50 includes cylinder holes 50b and 50b formed in the actuator bodies 50a and 50a, and shift pistons 50c and 50c disposed in the cylinder holes 50b and 50b so as to be capable of stroke. And fluid chambers 50d, 50d formed at both end face positions of the shift pistons 50c, 50c.

The working fluid circuit connected to the fluid chambers 50d and 50d includes main circuits 50f and 50f connected to the end surface positions of the fluid chambers 50d and 50d, intermediate positions on the side surfaces of the fluid chambers 50d and 50d, and the main circuit. Sub-circuits 50g, 50g connected to 50f, 50f, orifices 50e, 50e set at positions closer to the fluid chambers 50d, 50d than the sub-circuit connection position of the main circuits 50f, 50f, and the main circuits 50f, 50f. Both circuit ends are connected to each other, and unidirectional circuits 50h and 50h permitting only one-way flow from the main circuits 50f and 50f to the fluid chambers 50d and 50d while bypassing the orifices 50e and 50e.
Since other configurations are the same as those of the first embodiment, the description thereof is omitted.

Next, the operation will be described.
As an example of the shift operation by the shift actuator, the shift operation from the fifth speed to the third speed by the 3-5 shift actuator 50 will be described.

  First, when the fifth speed is selected, the shift pistons 50c and 50c of the 3-5 shift actuator 50 are located on the right side of the neutral position shown in FIG. And the fifth speed position ball hole 94, the fifth speed selection position is maintained. That is, the fluid chambers 50d and 50d, the main circuits 50f and 50f, and the sub-circuits 50g and 50g are only filled with the working fluid (oil) at the atmospheric pressure level.

  When a shift command to the third speed is output in the fifth speed selected state, the shift hydraulic pressure is supplied from the right main circuit 50f in FIG. 5, and the main circuit 50f is provided on the end face of the right shift piston 50c in FIG. → The one-way circuit 50h → the main circuit 50f → the transmission hydraulic pressure acts via the fluid chamber 50d, and the transmission hydraulic pressure acts via the main circuit 50f → the sub circuit 50g → the fluid chamber 50d.

Accordingly, an oil pressure is generated on the end face of the right shift piston 50c in FIG. 5 by multiplying the pressure receiving area by the shift oil pressure, and the shift pistons 50c and 50c are moved to the right end position (fifth speed position) in FIG. ) To the neural position shown in FIG. 5, and further, the left shift piston 50c in FIG.
In the stroke region from the right end position (5th gear position) to the position where the left shift piston 50c in FIG. 5 blocks the sub circuit 50g, the left shift piston 50c in FIG. The working fluid filled in both the fluid chambers 50d is quickly discharged through both the circuits 50f and 50g of the sub circuit 50g having a small discharge resistance and the main circuit 50f having a large discharge resistance.

  Of the shift pistons 50c, 50c, in the region where the left shift piston 50c strokes from the position where the sub circuit 50g is closed to the left end position (third speed position), the working fluid in the left fluid chamber 50d is the main circuit 50f. → Orifice 50e → It is discharged through the main circuit 50f.

  For this reason, the orifice 50e becomes a discharge resistance, the discharge amount of the drain fluid is limited, the drain fluid pressure in the fluid chamber 50d increases, the stroke speed of the shift pistons 50c, 50c decreases, the shift piston end surface and the cylinder hole end surface The fluid cushion effect is exhibited in the stroke region where the struck.

As described above, in the 3-5 shift actuator 50 of the second embodiment, the drain fluid is moved after the orifices 50e and 50e are stroked more than the position where the discharge-side shift piston 50c blocks the sub circuit 50g among the shift pistons 50c and 50c. Is set to a circuit (main circuit 50f) from which the gas is discharged.
For this reason, compared with the first embodiment in which the orifices 50e and 50e are set in the circuit where the drain fluid is discharged after the stroke of the neutral position or more, the stroke amount for ensuring a quick stroke operation is increased, and the shift response is further reduced. It can be kept small.

Next, the effect will be described.
In the shift actuator of the second embodiment, in addition to the effects (1), (2), (3), and (4) of the first embodiment, the following effects can be obtained.

  (6) The working fluid circuit includes main circuits 50f and 50f connected to the end face positions of the fluid chambers 50d and 50d, and intermediate positions on the side surfaces of the fluid chambers 50d and 50d and the sub-circuits connected to the main circuits 50f and 50f. Both circuit ends are connected to the main circuits 50f and 50f, the orifices 50e and 50e set at positions on the fluid chambers 50d and 50d side of the circuit 50g and the main circuits 50f and 50f from the sub-circuit connection position. And the one-way circuits 50h, 50h that permit only one-way flow from the main circuits 50f, 50f to the fluid chambers 50d, 50d while bypassing the orifices 50e, 50e. A working fluid circuit capable of preventing the occurrence of wear and noise due to the fluid cushion effect while keeping it smaller than that of the first embodiment. It can be constituted by an external circuit set in the rotor bodies 50a and 50a.

The third embodiment is an example in which the subcircuit of the working fluid circuit is configured by an external circuit while the subcircuit of the working fluid circuit is configured by an external circuit in the first embodiment.
The control system diagram showing the twin clutch type automatic manual transmission to which the shift actuator of the third embodiment is applied, the shift hydraulic pressure control system, and the electronic control system is the same as that of the first embodiment shown in FIGS. Illustration and description are omitted.

Next, the structure of the shift actuator of Example 3 is demonstrated based on FIG.
FIG. 6 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 according to the third embodiment.
Here, the 3-5 shift actuator 50 will be described as an example, but the other 1-R shift actuator 52, 6-N shift actuator 53, and 2-4 shift actuator 54 also have the same configuration.

As shown in FIG. 6, the 3-5 shift actuator 50 includes the shift pistons 50c, 50c, large-diameter piston portions 50c1, 50c1, small-diameter piston portions 50c2, 50c2, and piston step surfaces 50c3, 50c3. It has a stepped piston.
The cylinder holes 50b and 50b are stepped cylinder holes having large diameter cylinder holes 50b1 and 50b1, small diameter cylinder holes 50b2 and 50b2, and body step surfaces 50b3 and 50b3.

  As the fluid chambers 50d and 50d, the first fluid chambers 50d1 and 50d1 surrounded by the end surfaces of the small-diameter piston portions 50c2 and 50c2 and the small-diameter cylinder holes 50b2 and 50b2, the peripheral surfaces of the small-diameter piston portions 50c2 and 50c2, and the piston step surface 50c3. , 50c3, body step surfaces 50b3, 50b3 and second fluid chambers 50d2, 50d2 surrounded by large-diameter cylinder holes 50b1, 50b1.

The working fluid circuit is formed inside the external circuits 50i and 50i connected to the end face positions of the first fluid chambers 50d1 and 50d1, and inside the small-diameter piston portions 50c2 and 50c2, and the second fluid chambers 50d2 and 50d2 Internal circuits 50j and 50j communicating with the first fluid chambers 50d1 and 50d1, and orifices 50e and 50e set at intermediate positions of the internal circuits 50j and 50j.
Since other configurations are the same as those of the first embodiment, the description thereof is omitted.

Next, the operation will be described.
As an example of the shift operation by the shift actuator, the shift operation from the fifth speed to the third speed by the 3-5 shift actuator 50 will be described.

  First, when the fifth speed is selected, the shift pistons 50c and 50c of the 3-5 shift actuator 50 are located on the right side of the neutral position shown in FIG. And the fifth speed position ball hole 94, the fifth speed selection position is maintained. That is, the fluid chambers 50d and 50d, the external circuits 50i and 50i, and the internal circuits 50j and 50j are only filled with the working fluid (oil) at the atmospheric pressure level.

  When a gear shift command to the third gear is output in the fifth gear selected state, the gear shift hydraulic pressure is supplied from the external circuit 50i on the right side of FIG. 6, and among the shift piston 50c on the right side of FIG. On the end face, the transmission hydraulic pressure acts via the external circuit 50i → the first fluid chamber 50d1, and the piston step surface 50c3 includes the external circuit 50i → the internal circuit 50j → the orifice 50e → the internal circuit 50j → the second fluid chamber 50d2. The shift hydraulic pressure is applied via this.

Therefore, an oil pressure is generated on the end face of the right shift piston 50c in FIG. 6 by multiplying the pressure receiving area by the shift oil pressure, and the shift pistons 50c, 50c are moved to the right end position (fifth speed position) in FIG. ) To the neural position shown in FIG.
In the stroke region from the right end position (5-th gear position) to the neural position, the left shift piston 50c in FIG. 6 is the right position from the illustrated position, and is formed at the end of the left shift piston 50c. Since the first fluid chamber 50d1 and the second fluid chamber 50d2 are in communication with each other, the working fluid filled in both the fluid chambers 50d1 and 50d2 is quickly discharged through the external circuit 50i.

When the shift pistons 50c and 50c stroke to the neural position shown in FIG. 6, the first fluid chamber 50d1 and the second fluid chamber 50d2 are formed by the small-diameter piston portion 50c2 formed on the end surface portion of the left shift piston 50c in FIG. Block communication with.
Therefore, in the region where the shift pistons 50c, 50c stroke from the neutral position to the left end position (third speed position), the working fluid in the second fluid chamber 50d2 is internal circuit 50j → orifice 50e → internal circuit 50j → first fluid. The chamber 50d1 is discharged through the external circuit 50i.

  For this reason, the orifice 50e becomes a discharge resistance, the discharge amount of the drain fluid is limited, the drain fluid pressure in the second fluid chamber 50d2 increases, the stroke speed of the shift pistons 50c, 50c decreases, the shift piston end face and the cylinder hole The fluid cushion effect is exhibited in the stroke region where the end surface abuts.

  As described above, in the 3-5 shift actuator 50 of the third embodiment, among the working fluid circuits connected to both the fluid chambers 50d and 50d, the circuit for supplying the pressurized fluid to the fluid chambers 50d and 50d is set. First, since the orifices 50e and 50e that suppress the drain fluid discharge amount are set only in the circuit that drains the drain fluid according to the stroke operation of the shift pistons 50c and 50c, the shift start response is improved and the shift response is secured. Can do.

  Further, in the 3-5 shift actuator 50 of the third embodiment, the orifices 50e and 50e are set to a circuit (internal circuit 50j) in which the drain fluid is discharged after the stroke amounts of the shift pistons 50c and 50c are stroked beyond the neutral position. Therefore, a quick stroke operation is ensured up to the neutral position, and a reduction in shift response can be kept small.

Next, the effect will be described.
In the shift actuator of the third embodiment, in addition to the effects (1), (2), (3), and (4) of the first embodiment, the following effects can be obtained.

  (7) The shift pistons 50c and 50c are stepped pistons having small-diameter piston portions 50c2 and 50c2 and piston step surfaces 50c3 and 50c3, and the cylinder holes 50b and 50b are large-diameter cylinder holes 50b1 and 50b1. The cylinder holes 50b2 and 50b2 and the stepped cylinder holes 50b3 and 50b3 are stepped cylinder holes. The fluid chambers 50d and 50d are surrounded by the end surfaces of the small diameter piston portions 50c2 and 50c2 and the small diameter cylinder holes 50b2 and 50b2. The first fluid chambers 50d1, 50d1, the peripheral surfaces of the small diameter piston portions 50c2, 50c2, the piston step surfaces 50c3, 50c3, the body step surfaces 50b3, 50b3, and the large diameter cylinder holes 50b1, 50b1. 50 d 2, 50 d 2, and the working fluid circuit is connected to the end face positions of the first fluid chambers 50 d 1, 50 d 1. i, internal circuits 50j, 50j formed inside the small-diameter piston portions 50c2, 50c2 and communicating with the second fluid chambers 50d2, 50d2 and the first fluid chambers 50d1, 50d1, and the internal circuits 50j, 50j Working fluid which can prevent the occurrence of wear and noise due to the fluid cushion effect while suppressing a decrease in the speed change response during the shift operation. The circuit can be constituted by internal circuits 50j and 50j formed in the shift pistons 50b and 50b, and the peripheral circuits can be simplified.

  The shift actuator of the present invention has been described based on the first to third embodiments. However, the specific configuration is not limited to these embodiments, and the claims are related to each claim. Design changes and additions are allowed without departing from the scope of the invention.

In the first to third embodiments, an example in which an orifice fixed in a circuit is used as a flow path restricting portion and whether or not an orifice action is produced by mechanical control based on the positional relationship between the piston and the cylinder hole is shown. However, for example, the flow restrictor is a variable orifice that can control the cross-sectional area of the flow channel from the outside, and at the time of shifting, a control command for restricting the flow channel to the variable orifice on the drain fluid discharge side is electronically controlled. You may make it output.
In short, among the working fluid circuits connected to the fluid chambers formed at both end face positions of the shift piston, the flow passage restrictor that suppresses the discharge amount of the drain fluid to the circuit in which the drain fluid is discharged according to the stroke operation of the shift piston. Any part that has a set part is included in the present invention.

  In the first to third embodiments, an example of a shift actuator applied to a twin clutch type automatic manual transmission is shown, but the present invention may be applied to a shift actuator of another transmission. In short, at the time of shift, the shift piston is configured by supplying pressurized fluid to one fluid chamber among the fluid chambers formed at both end face positions of the shift piston and discharging the drain fluid filled in the other fluid chamber. The present invention can be applied to a shift actuator that moves a shift operation member connected to the shift actuator in the shift direction.

It is a skeleton figure which shows the twin clutch type automatic manual transmission to which the shift actuator of Example 1 was applied. FIG. 2 is a control system diagram showing a shift hydraulic pressure control system and an electronic control system in a twin clutch type automatic manual transmission to which the shift actuator of the first embodiment is applied. FIG. 3 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 according to the first embodiment. It is the schematic which shows the structure of the shift operation system provided with the conventional shift actuator. 6 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including a 3-5 shift actuator 50 according to Embodiment 2. FIG. 6 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including a 3-5 shift actuator 50 according to Embodiment 3. FIG.

Explanation of symbols

CA 1st clutch
CB 2nd clutch
G1 1st gear set
G2 2nd gear set
G3 3rd speed gear set
G4 4th gear set
G5 5th gear set
G6 6th gear set
GR reverse gear set 1 transmission case 2 drive input shaft 4 oil pump 5 first transmission input shaft 6 second transmission input shaft 11 transmission output shaft 15 counter shaft 41, 42, 43, 44 shift fork (shift operation member)
45 First control valve unit 46 Second control valve unit 50, 52, 53, 54 Shift actuator 59 Actuator hydraulic control valve (control valve for shift control)
50a Actuator body 50b Cylinder hole 50c Shift piston 50d Fluid chamber 50e Orifice (channel restrictor)
50f Main circuit 50g Sub circuit 50h Unidirectional circuit 50i External circuit 50j Internal circuit

Claims (8)

A shift piston that is disposed in a cylinder hole of the actuator body so as to be capable of a stroke, and to which a shift operation member is coupled, and fluid chambers formed at both end face positions of the shift piston,
When shifting, the pressurized fluid is supplied to one of the fluid chambers and the drain fluid filled in the other fluid chamber is discharged, thereby shifting the shift operation member connected to the shift piston. In the shift actuator that operates in the direction
Of the working fluid circuits connected to the two fluid chambers, a shift in which a drain fluid is discharged in accordance with the stroke operation of the shift piston is provided with a flow passage restricting portion that suppresses the discharge amount of the drain fluid. Actuator. The shift actuator according to claim 1, wherein
2. The shift actuator according to claim 1, wherein the flow path restricting portion is not set in a circuit for supplying pressurized fluid to the fluid chamber, but is set only in a circuit in which drain fluid is discharged along with a stroke operation of the shift piston. The shift actuator according to claim 1 or 2,
2. The shift actuator according to claim 1, wherein the flow path restricting portion is set in a circuit that drains the drain fluid after the stroke amount of the shift piston has exceeded a predetermined amount. The shift actuator according to any one of claims 1 to 3,
The transmission having the shift operation member includes a first clutch that is engaged when an odd-numbered gear group is selected from among a plurality of gears, and a second clutch that is engaged when an even-numbered gear group is selected from among a plurality of gears. And a constantly meshing gear train that has a synchronous meshing mechanism and achieves a plurality of shift speeds by a plurality of gear pairs having different gear ratios,
At the time of shifting to an adjacent shift stage, the next shift stage is selected from the shift stage group of the clutch that has been released prior to the switching control of the first clutch and the second clutch, and a control valve for shift control A shift actuator, which is a twin clutch type automatic manual transmission that operates a shift fork in a direction to obtain a shift stage selected by a shift hydraulic pressure generated by the shift actuator. The shift actuator according to any one of claims 1 to 4,
The shift piston is a stepped piston having a small diameter piston portion and a piston step surface,
The cylinder hole is a stepped cylinder hole having a small diameter cylinder hole, a large diameter cylinder hole, and a body step surface,
As the fluid chamber, a first fluid chamber surrounded by the end surface of the small diameter piston portion and the small diameter cylinder hole, a second fluid surrounded by the peripheral surface of the small diameter piston portion, the piston step surface, the body step surface and the large diameter cylinder hole. Forming a chamber,
The working fluid circuit includes a main circuit connected to an end surface position of the first fluid chamber, a sub-circuit connected to a body step surface position of the second fluid chamber and the main circuit, and an intermediate position of the sub circuit. And a one-way circuit that allows only one-way flow from the second fluid chamber to the main circuit while bypassing the orifice and having both circuit ends connected to the sub-circuit. Shift actuator. The shift actuator according to any one of claims 1 to 4,
The working fluid circuit includes a main circuit connected to an end surface position of the fluid chamber, a sub circuit connected to a midway side surface of the fluid chamber and the main circuit, and a fluid chamber from a sub circuit connection position of the main circuit. An orifice set at a side position, and a one-way circuit having both circuit ends connected to the main circuit and allowing only one-way flow from the main circuit to the fluid chamber while bypassing the orifice. Shift actuator. The shift actuator according to any one of claims 1 to 4,
The shift piston is a stepped piston having a small diameter piston portion and a piston step surface,
The cylinder hole is a stepped cylinder hole having a large diameter cylinder hole, a small diameter cylinder hole, and a body step surface,
As the fluid chamber, a first fluid chamber surrounded by the end surface of the small diameter piston portion and the small diameter cylinder hole, a second fluid surrounded by the peripheral surface of the small diameter piston portion, the piston step surface, the body step surface and the large diameter cylinder hole. Forming a chamber,
The working fluid circuit includes an external circuit connected to an end face position of the first fluid chamber, an internal circuit formed inside the small-diameter piston portion, and communicated with the second fluid chamber and the first fluid chamber; A shift actuator having an orifice set at an intermediate position of the internal circuit. A shift piston that is disposed in a cylinder hole of the actuator body so as to be capable of a stroke, and to which a shift operation member is coupled, and fluid chambers formed at both end face positions of the shift piston,
When shifting, the pressurized fluid is supplied to one of the fluid chambers and the drain fluid filled in the other fluid chamber is discharged, thereby shifting the shift operation member connected to the shift piston. In the shift actuator that operates in the direction
A shift actuator that discharges a drain fluid filled in the other fluid chamber while obtaining a fluid cushion effect during a shift operation in which pressurized fluid is supplied to one of the fluid chambers.

Images