JP2007292095A - Spool valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shift actuator for preventing the entry of contaminant into a gap between a valve spool and a spool hole during valve operation while preventing the generation of abnormal sounds with fluid cushioning effects. <P>SOLUTION: This spool valve comprises the valve spools 50c, 50c arranged in the spool holes 50b, 50b of valve bodies 50a, 50a to be capable of making stroke. Herein, drain fluid filled in one of fluid chambers 50d, 50d formed in both ends of the valve spools 50c, 50c is drained during valve operation. In an operating fluid circuit connected to both fluid chambers 50d, 50d, one-way balls 50e, 50e are set to form a closed circuit C1 communicated with gaps between each of the spool holes 50b, 50b and the valve spools 50c, 50c. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention belongs to the technical field of a spool valve that discharges a drain fluid filled in a fluid chamber formed at an end of a valve spool during valve operation.

Conventionally, a spool valve used as a hydraulic control valve has a valve spool that is disposed in a spool hole of a valve body so as to be capable of stroke, and is filled in a fluid chamber formed at an end of the valve spool during valve operation. What discharges | emits drain fluid is known (for example, refer patent document 1).
JP 2004-293701 A

  However, the conventional spool valve has a configuration in which foreign substances enter the gap between the valve spool and the spool hole (especially, foreign substances are likely to enter on the side where negative pressure is generated by the valve operation). For this reason, there has been a problem that the valve spool is worn by rubbing the biting foreign matter along with the valve operation, and the biting foreign matter becomes a valve operation resistance and a stick is generated.

  The present invention has been made paying attention to the above problems, and can prevent foreign matter from entering the gap between the valve spool and the spool hole during valve operation, and also prevent the generation of noise by the fluid cushion effect. It is an object of the present invention to provide a spool valve that can be used.

In order to achieve the above object, the present invention includes a valve spool disposed in a spool hole of the valve body so as to be capable of stroke,
In the spool valve that discharges the drain fluid filled in the fluid chamber formed at the end of the valve spool during the valve operation,
In the working fluid circuit connected to the fluid chamber, a flow path blocking structure that forms a closed circuit communicating with the gap between the spool hole and the valve spool is set in the spool stroke region where the drain fluid is discharged. It is characterized by.

Therefore, in the spool valve of the present invention, a closed circuit is formed in the spool stroke region where the drain fluid is discharged by the flow path blocking structure set in the working fluid circuit connected to the fluid chamber during the valve operation. Then, the drain fluid pressurized by the closed circuit passes through the gap between the spool hole and the valve spool and is discharged to the outside.
That is, even if foreign matter enters the gap between the spool hole and the valve spool, it is pushed away by the drain fluid pressurized by the closed circuit, and the foreign matter passes through the gap between the spool hole and the valve spool together with the drain fluid. It is discharged outside.
Further, when a closed circuit is formed in the spool stroke region where the drain fluid is discharged, the drain fluid pressure in the closed circuit increases and the stroke speed of the valve spool decreases.
For this reason, for example, in the full stroke region where the valve spool end surface and the spool hole end surface abut against each other, 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 foreign matter from entering the gap between the valve spool and the spool hole during the valve operation, and to prevent the generation of noise due to the fluid cushion effect.

  Hereinafter, the best mode for carrying out the spool valve 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 a shift actuator having a spool valve of Example 1 is applied.

[Configuration of transmission input section and shaft]
Hereinafter, the structure of the transmission input unit and the shaft in the twin clutch type automatic manual transmission to which the shift actuator having the spool valve 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 transmission mechanism in the twin clutch type automatic manual transmission to which the shift actuator having the spool valve 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 the twin clutch type automatic manual transmission to which the shift actuator having the spool valve 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 configuration of the shift actuator having the spool valve according to the first embodiment will be described with reference to FIG.
FIG. 3 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 having the spool valve 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 spool valve according to the first embodiment includes valve spools 50c and 50c disposed in the spool holes 50b and 50b of the valve bodies 50a and 50a so as to be capable of stroke. , 50c, the drain fluid filled in one of the fluid chambers 50d, 50d formed at both ends of the fluid chamber 50d is discharged.

  Then, the working fluid circuit connected to both the fluid chambers 50d and 50d is closed to communicate with the clearance between the spool holes 50b and 50b and the valve spools 50c and 50c in the spool stroke region where the drain fluid is discharged. One-way balls 50e and 50e (flow path blocking structure) forming the circuit C1 are set.

  The one-way balls 50e, 50e are closed circuits that communicate with the clearances between the spool holes 50b, 50b and the valve spools 50c, 50c after the stroke amount of the valve spools 50c, 50c has exceeded the neutral position shown in FIG. It is set to form.

  As shown in FIG. 3, the valve spools 50c and 50c are disposed in the spool holes 50b and 50b of the valve bodies 50a and 50a in a strokeable manner, and a 3-5 shift fork 41 is connected to the fluid chambers 50d and 50d. Is formed at both end face positions of the valve spools 50c and 50c, and supplies a pressurized fluid to one of the fluid chambers 50d and 50d at the time of shifting, and a drain filled in the other fluid chamber. The 3-5 shift actuator 50 that moves the 3-5 shift fork 41 connected to the valve spools 50c, 50c in the shift direction by discharging the fluid is provided.

The configuration of the spool valve according to the first embodiment will be described in detail. As shown in FIG. 3, the valve spools 50c and 50c are divided into large-diameter spool portions 50c1 and 50c1, small-diameter spool portions 50c2 and 50c2, and a stepped surface 50c3. 50c3, a stepped valve spool.
The spool holes 50b and 50b are stepped valve spool holes having large diameter spool holes 50b1 and 50b1, small diameter spool 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 spool portions 50c2 and 50c2 and the small-diameter spool holes 50b2 and 50b2, the peripheral surfaces of the small-diameter spool portions 50c2 and 50c2, and the spool step surface 50c3. , 50c3, body step surfaces 50b3, 50b3, and second fluid chambers 50d2, 50d2 surrounded by large diameter spool 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. Sub-circuits 50g and 50g, and one-way balls 50e and 50e that are set at midway positions of the sub-circuits 50g and 50g and block the flow from the second fluid chambers 50d2 and 50d2 to the main circuits 50f and 50f.

  The second clearance t2 between the large diameter spool portions 50c1, 50c1 and the large diameter spool holes 50b1, 50b1 is set larger than the first clearance t1 between the small diameter spool portions 50c2, 50c2 and the small diameter spool holes 50b2, 50b2. (See FIG. 5).

  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 shifting operation in the twin clutch type automatic manual transmission 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.
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 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.

[Valve operation by spool valve]
Conventionally, as a spool valve used as a shift actuator, as shown in FIG. 4, a valve spool that is disposed in a spool hole of a valve body so as to be capable of stroke is provided, and a fluid formed at an end of the valve spool during valve operation. It is known to drain the drain fluid that fills the chamber.

  However, the spool valve shown in FIG. 4 has a structure in which foreign matter enters the gap between the valve spool and the spool hole, and therefore, wear of the valve spool caused by rubbing the biting foreign matter along with the valve operation. In addition, the foreign matter that has been bitten becomes resistance to valve operation and sticks are generated. In particular, as the applicant previously proposed in Japanese Patent Application No. 2005-225380, in order to detect the shift position, the one having a configuration in which a magnet is embedded in the valve spool magnetically disposes metal powder, metal scraps, etc. Since it is adsorbed, impurities are more likely to enter the gap between the valve spool and the spool hole.

  On the other hand, in the spool valve of the first embodiment, it is possible to prevent foreign matter from entering the gap between the valve spool and the spool hole during valve operation, and to prevent the generation of noise due to the fluid cushion effect. I was able to do it.

  That is, paying attention to the fact that if the drain fluid that has been discharged from the drain circuit as it is is discharged through the gap between the valve spool and the spool hole, the drain fluid itself becomes a removal medium that discharges the contaminants on the flow. In the working fluid circuit connected to the fluid chamber 50d, a one-way ball 50e that forms a closed circuit C1 communicating with the gap between the spool hole 50b and the valve spool 50c is set in the spool stroke region where the drain fluid is discharged. Adopted the configuration.

Therefore, when the closed circuit C1 is formed by the operation of the one-way ball 50e, the drain fluid pressurized by the closed circuit C1 passes through the gap t2 between the spool hole 50b and the valve spool 50c and is discharged to the outside. .
For this reason, even if a foreign substance enters the gap t2 between the spool hole 50b and the valve spool 50c, the foreign substance is pushed away by the drain fluid pressurized by the closed circuit C1, and the foreign substance together with the drain fluid also flows into the spool hole 50b and the valve spool 50c. After passing through the gap t2, it is discharged to the outside.
Further, when the closed circuit C1 is formed in the spool stroke region where the drain fluid is discharged, the drain fluid pressure in the closed circuit C1 increases and the stroke speed of the valve spool 50c decreases.
For this reason, for example, in the full stroke region where the valve spool end surface and the spool hole end surface abut against each other, 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 foreign matters from entering the gap between the valve spool 50c and the spool hole 50b during the valve operation, and to prevent the generation of noise due to the fluid cushion effect.

[3-5 Shift operation by shift actuator]
As an example of the valve operation, a 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 valve spools 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 valve spools 50c on the right side of FIG. A speed change hydraulic pressure acts on the end surface via the main circuit 50f → the first fluid chamber 50d1, and the main circuit 50f → the sub circuit 50g → the one-way ball 50e → the sub circuit 50g → the second fluid chamber 50d2 acts on the spool step surface 50c3. The shift oil pressure acts via the.

Accordingly, an oil pressure is generated on the end face of the right side valve spool 50c in FIG. 3 by multiplying the pressure receiving area by the transmission oil pressure, and the oil pressure causes the valve spools 50c, 50c to move 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 valve spool 50c in FIG. 3 is the right position from the illustrated position, and is formed at the end of the left valve spool 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 fluid chambers 50d1 and 50d2 is quickly discharged through the main circuit 50f having a small discharge resistance.

When the valve spools 50c and 50c are stroked 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 spool portion 50c2 formed on the end surface portion of the left valve spool 50c in FIG. The closed circuit C1 is formed by the second fluid chamber 50d2 and the sub circuit 50g to the one-way ball 50e.
Therefore, in the region where the valve spools 50c, 50c stroke from the neutral position to the left end position (third gear position), as shown in FIG. 5, the drain fluid pressure in the closed circuit C1 increases and the operation in the closed circuit C1 occurs. The fluid is discharged through the second gap t2 (> first gap t1) between the large diameter spool hole 50b1 and the large diameter spool portion 50c1.

For this reason, even if impurities enter the second gap t2 between the large-diameter spool hole 50b1 and the large-diameter spool portion 50c1, they are pushed away by the drain fluid pressurized by the closed circuit C1, and the impurities are large together with the drain fluid. After passing through the second gap t2 between the diameter spool hole 50b1 and the large diameter spool portion 50c1, it is discharged to the outside.
Further, the second gap t2 serves as a discharge resistance for the drain fluid, the drain fluid discharge amount is limited, the drain fluid pressure in the closed circuit C1 increases, the stroke speed of the valve spools 50c, 50c decreases, and the valve spool end face The fluid cushion effect is exhibited in the stroke region where the end face of the spool hole abuts.

As described above, in the spool valve included in the 3-5 shift actuator 50 of the first embodiment, after the one-way balls 50e and 50e are stroked beyond the neutral position by the stroke amount of the valve spools 50c and 50c, the large-diameter spool hole 50b1. And a closed circuit C1 communicating with the second gap t2 between the large-diameter spool portion 50c1.
For example, if a closed circuit communicating with the gap between the spool hole and the valve spool is formed in the spool stroke area where drain fluid is discharged in the entire stroke area of the valve spool, the area from the start to the end of the stroke The speed change response is reduced due to the slow stroke of the valve spool due to the effect of the reduction in stroke speed due to the discharge resistance.
On the other hand, in the first embodiment, the stroke is set to form the closed circuit C1 that communicates with the second gap t2 between the large-diameter spool hole 50b1 and the large-diameter spool portion 50c1 after a stroke of the neutral position or more. A rapid stroke operation is ensured, and a reduction in shift response can be kept small.

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

  (1) Valve spools 50c, 50c disposed in the spool holes 50b, 50b of the valve bodies 50a, 50a so as to be capable of stroke are provided, and fluid chambers 50d formed at both ends of the valve spools 50c, 50c during valve operation. , 50d, a spool valve that discharges a drain fluid filled in one fluid chamber, and a working fluid circuit connected to both the fluid chambers 50d, 50d has a spool stroke region in which the drain fluid is discharged, Since the one-way balls 50e and 50e forming a closed circuit C1 communicating with the clearance between the spool holes 50b and 50b and the valve spools 50c and 50c are set, the valve spools 50c and 50c and the spool holes 50b and 50b It is possible to prevent foreign matter from entering the gap between the fluid cushion and the fluid cushion. Effect can prevent the generation of noise.

  (2) The one-way balls 50e, 50e are closed circuits C1 communicating with the clearances between the spool holes 50b, 50b and the valve spools 50c, 50c after the stroke amount of the valve spools 50c, 50c has exceeded the neutral position. Therefore, a quick stroke operation is ensured up to the neutral position, and a reduction in the shift response can be suppressed to a small level.

  (3) The valve spools 50c, 50c are disposed in the spool holes 50b, 50b of the valve bodies 50a, 50a so as to be capable of stroke, and a 3-5 shift fork 41 is connected. The fluid chambers 50d, 50d Formed at both end face positions of the spools 50c, 50c, during shifting, pressurized fluid is supplied to one of the fluid chambers 50d, 50d, and the drain fluid filled in the other fluid chamber is discharged. Thus, since the 3-5 shift fork 41 connected to the valve spools 50c, 50c is provided in the 3-5 shift actuator 50 that operates in the shift direction, the shift operation by the spool valve is a stick operation by the biting of foreign matters. It is possible to reliably prevent the occurrence of malfunctions that cause malfunctions or malfunctions.

  (4) The transmission having the 3-5 shift actuator 50 includes a first clutch CA that is engaged when an odd-numbered gear group is selected from among a plurality of gears, and an even-numbered gear group 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 this 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, It is possible to secure the smooth shift operation, shift operation of the automatic shift mode, it is possible to prevent the occurrence of abnormal noise that discomfort to the occupant by the fluid cushion effect.

  (5) The valve spools 50c, 50c are stepped valve spools having large-diameter spool portions 50c1, 50c1, small-diameter spool portions 50c2, 50c2, and spool step surfaces 50c3, 50c3, and the spool holes 50b, 50b have large diameters. A stepped valve spool hole having spool holes 50b1, 50b1, small diameter spool holes 50b2, 50b2, and body step surfaces 50b3, 50b3. As the fluid chambers 50d, 50d, the end surfaces of the small diameter spool portions 50c2, 50c2, the small diameter spool holes 50b2, The first fluid chambers 50d1 and 50d1 surrounded by 50b2, the peripheral surfaces of the small diameter spool portions 50c2 and 50c2, the step surfaces 50c3 and 50c3, the body step surfaces 50b3 and 50b3, and the large diameter spool holes 50b1 and 50b1. Two fluid chambers 50d2 and 50d2, and the working fluid circuit is located at the end face position of the first fluid chambers 50d1 and 50d1. The connected main circuits 50f, 50f, the body step surface positions of the second fluid chambers 50d2, 50d2, the subcircuits 50g, 50g connected to the main circuits 50f, 50f, and the subcircuits 50g, 50g in the middle positions. One-way balls 50e, 50e that set and block the flow from the second fluid chambers 50d2, 50d2 to the main circuits 50f, 50f, and the small diameter spool portions 50c2, 50c2 and the small diameter spool holes 50b2, 50b2 Since the second gap t2 between the large-diameter spool portions 50c1, 50c1 and the large-diameter spool holes 50b1, 50b1 is set to be larger than the one gap t1, the valve spool 50c, Reliable prevention of entry of foreign matter into the second gap t2 between the spool 50c and the spool holes 50b, 50b and generation of abnormal noise due to the fluid cushion effect It can be.

The second embodiment is an example in which the stroke region where the entry of foreign substances and the fluid cushion effect act is set closer to the stroke end side than the first embodiment.
A control system diagram showing a twin clutch type automatic manual transmission, a transmission hydraulic pressure control system, and an electronic control system to which a shift actuator having a spool valve of the second embodiment is applied is the same as that of the first embodiment shown in FIGS. Therefore, illustration and description are omitted.

Next, the configuration of the shift actuator having the spool valve according to the second embodiment will be described with reference to FIG.
FIG. 6 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 having the spool valve 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. 6, the 3-5 shift actuator 50 having the spool valve includes spool holes 50b and 50b formed in the valve bodies 50a and 50a, and a valve disposed in the spool holes 50b and 50b so as to be capable of stroke. Spools 50c, 50c, and fluid chambers 50d, 50d formed at both end face positions of the valve spools 50c, 50c are provided.

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 and 50g connected to 50f and 50f, and the main circuits 50f and 50f are set at positions closer to the fluid chambers 50d and 50d than the sub-circuit connection position, and from the fluid chambers 50d and 50d to the main circuits 50f and 50f. One-way balls 50e and 50e that block the flow to the.
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 valve operation, a 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 valve spools 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. 6, and the main circuit 50f is connected to the end face of the right valve spool 50c in FIG. → The one-way ball 50e → 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 auxiliary circuit 50g → the fluid chamber 50d.

Accordingly, an oil pressure is generated on the end face of the right side valve spool 50c in FIG. 6 by multiplying the pressure receiving area by the shift oil pressure, and the oil pressure causes the valve spools 50c, 50c to move to the right end position (fifth speed position) in FIG. ) To the neural position shown in FIG. 6, and further exceeds the neural position, and as shown in FIG. 7, the left valve spool 50c strokes to the left until it closes the sub circuit 50g.
In the stroke region from the right end position (5th gear position) to the position where the left valve spool 50c shown in FIG. 7 closes the sub circuit 50g, the sub circuit 50g is not blocked by the left valve spool 50c. The working fluid filled in the fluid chamber 50d is quickly discharged through the sub circuit 50g having a small discharge resistance.

Of the valve spools 50c, 50c, in the region where the left valve spool 50c strokes from the position where it closes the sub circuit 50g to the left end position (third speed position), as shown in FIG. 7, the fluid chamber 50d and the one-way ball A closed circuit C2 is formed by the main circuit 50f interrupted by 50e.
Therefore, in the region where the valve spools 50c, 50c stroke from the position where the sub circuit 50g is closed to the left end position (third speed position), the drain fluid pressure in the closed circuit C2 increases as shown in FIG. The working fluid in C2 is discharged through two paths: a path through the sub circuit 50g and a path through the gap between the spool hole 50b and the valve spool 50c.

For this reason, even if a foreign substance enters the gap between the spool hole 50b and the valve spool 50c, the foreign substance is pushed away by the drain fluid pressurized by the closed circuit C2, and the foreign substance together with the drain fluid is separated from the spool hole 50b and the valve spool 50c. After passing through the gap, it is discharged outside.
Further, the clearance between the spool hole 50b and the valve spool 50c becomes a drain resistance for the drain fluid, the drain fluid discharge amount is limited, the drain fluid pressure in the closed circuit C2 increases, and the stroke speed of the valve spools 50c, 50c decreases. The fluid cushion effect is exhibited in the stroke region where the valve spool end surface and the spool hole end surface abut against each other.

As described above, in the 3-5 shift actuator 50 having the spool valve according to the second embodiment, the one-way balls 50e and 50e are moved beyond the position where the discharge-side valve spool 50c of the valve spools 50c and 50c blocks the sub circuit 50g. After the stroke, the closed circuit C2 communicating with the gap between the spool hole 50b and the valve spool 50c is set.
For this reason, compared with the first embodiment in which the closed circuit is formed after the stroke of the neutral position or more, the stroke amount that ensures a quick stroke operation is increased, and the reduction of the shift response can be further suppressed.

Next, the effect will be described.
In the spool valve 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. One-way ball that sets the circuit 50g, 50g and the main circuit 50f, 50f to a position closer to the fluid chambers 50d, 50d than the sub-circuit connection position, and blocks the flow from the fluid chambers 50d, 50d to the main circuits 50f, 50f. 50e, 50e, so that during the shift operation, the reduction of the shift response is suppressed to be smaller than that of the first embodiment, and the entry of impurities into the gap between the valve spools 50c, 50c and the spool holes 50b, 50b is prevented. It is possible to reliably prevent the generation of abnormal noise due to the fluid cushion effect.

The third embodiment is an example in which the working fluid circuit is simpler than the first and second embodiments.
A control system diagram showing a twin clutch type automatic manual transmission, a transmission hydraulic pressure control system, and an electronic control system to which a shift actuator having a spool valve of the third embodiment is applied is the same as that of the first embodiment shown in FIGS. Therefore, illustration and description are omitted.

Next, the configuration of the shift actuator having the spool valve according to the third embodiment will be described with reference to FIG.
FIG. 8 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including the 3-5 shift actuator 50 having the spool valve 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. 8, the 3-5 shift actuator 50 having the spool valve includes spool holes 50b and 50b formed in the valve bodies 50a and 50a, and a valve disposed in the spool holes 50b and 50b so as to be capable of stroke. Spools 50c, 50c, and fluid chambers 50d, 50d formed at both end face positions of the valve spools 50c, 50c are provided.

Then, the working fluid circuit connected to the fluid chambers 50d and 50d is set to the main circuits 50f and 50f connected to the end face positions of the fluid chambers 50d and 50d, and the midway positions of the main circuits 50f and 50f. And one-way balls 50e, 50e that block the flow from the chambers 50d, 50d to the main circuits 50f, 50f.
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 valve operation, a 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 valve spools 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. 8, and the main circuit 50f is provided on the end face of the right valve spool 50c in FIG. → One-way ball 50e → Main circuit 50f → Variable oil pressure acts via the fluid chamber 50d.

Accordingly, an oil pressure is generated on the end surface of the right side valve spool 50c in FIG. 8 by multiplying the pressure receiving area by the shift oil pressure, and the oil pressure causes the valve spools 50c, 50c to move to the right end position (fifth speed position) in FIG. Stroke from left to right.
In the stroke region from the right end position (5th speed position) to the left end position (3rd speed position), the main circuit 50f is blocked by the one-way ball 50e set in the main circuit 50f of the left valve spool 50c.

  That is, in the stroke region for discharging the drain fluid filled in the fluid chamber 50d formed on the end surface of the left valve spool 50c in FIG. 8, the fluid chamber 50d and the one-way ball 50e are blocked as shown in FIG. The closed circuit C3 is formed by the main circuit 50f.

  Therefore, in the region where the valve spools 50c, 50c stroke from the right end position (5th speed position) to the left end position (3rd speed position), as shown in FIG. 8, the drain fluid pressure in the closed circuit C3 increases and the valve spool 50c, 50c closes. The working fluid in the circuit C3 is discharged through the gap between the spool hole 50b and the valve spool 50c. The clearance between the spool hole 50b and the valve spool 50c is set to an optimum value based on experimental results or the like so that the shift response does not decrease.

For this reason, even if foreign matter enters the gap between the spool hole 50b and the valve spool 50c, the foreign matter is pushed away by the drain fluid pressurized by the closed circuit C3, and the foreign matter together with the drain fluid also flows between the spool hole 50b and the valve spool 50c. After passing through the gap, it is discharged outside.
Further, the clearance between the spool hole 50b and the valve spool 50c becomes a drain resistance for the drain fluid, the drain fluid discharge amount is limited, the drain fluid pressure in the closed circuit C3 increases, and the stroke speed of the valve spools 50c, 50c decreases. The fluid cushion effect is exhibited in the stroke region where the valve spool end surface and the spool hole end surface abut against each other.

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

  (7) The working fluid circuit is set to the main circuits 50f and 50f connected to the end face positions of the fluid chambers 50d and 50d, and at a midway position between the main circuits 50f and 50f, and from the fluid chambers 50d and 50d to the main circuit 50f. , 50f that cut off the flow to 50f, so that the structure can be made simple, and during shifting operation, foreign matter can be prevented from entering the gaps between the valve spools 50c, 50c and the spool holes 50b, 50b. In addition, it is possible to reliably achieve the generation of abnormal noise due to the fluid cushion effect.

  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 a closed circuit is formed by a mechanical control using a change in the positional relationship between a spool and a spool hole using a one-way ball fixedly set in a circuit as a flow path blocking structure is shown. However, for example, the flow path blocking structure may be configured to be able to control the flow path blocking from the outside, and a control command for forming a closed circuit may be output by electronic control during valve operation.
In short, in the working fluid circuit connected to the fluid chamber, a flow path blocking structure that forms a closed circuit communicating with the gap between the spool hole and the valve spool in the spool stroke region where the drain fluid is discharged is set. If there is, it is included in the present invention.

  In the first to third embodiments, an example of a spool valve included in a shift actuator applied to a twin-clutch automatic manual transmission is shown, but the present invention may naturally be applied to a spool valve provided in a control valve unit of an automatic transmission. In short, the present invention is applied to a spool valve that includes a valve spool that is disposed in the spool hole of the valve body so as to be capable of stroke, and that discharges a drain fluid filled in a fluid chamber formed at the end of the valve spool during valve operation. be able to.

It is a skeleton figure which shows the twin clutch type automatic manual transmission to which the shift actuator which has a spool valve of Example 1 was applied. FIG. 3 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 a shift actuator having a spool valve of Example 1 is applied. It is the schematic which shows the structure of the 3-5 shift operation system provided with the 3-5 shift actuator 50 which has a spool valve of Example 1. FIG. It is action explanatory drawing which shows the discharge | emission action of the drain fluid in the shift operation system provided with the shift actuator which has the conventional spool valve. FIG. 6 is an operation explanatory view showing the draining action of the drain fluid in the 3-5 shift operation system including the 3-5 shift actuator 50 having the spool valve of the first embodiment. It is the schematic which shows the structure of the 3-5 shift operation system provided with the 3-5 shift actuator 50 which has a spool valve of Example 2. FIG. FIG. 10 is an operation explanatory view showing the draining action of the drain fluid in the 3-5 shift operation system including the 3-5 shift actuator 50 having the spool valve of the second embodiment. FIG. 6 is a schematic diagram illustrating a configuration of a 3-5 shift operation system including a 3-5 shift actuator 50 having a spool valve according to a third embodiment.

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 Valve body 50b Spool hole 50c Valve spool 50d Fluid chamber 50e One-way ball (channel blocking structure)
50f Main circuit 50g Sub circuit

Claims (8)

It is equipped with a valve spool that can be stroked in the spool hole of the valve body,
In the spool valve that discharges the drain fluid filled in the fluid chamber formed at the end of the valve spool during the valve operation,
In the working fluid circuit connected to the fluid chamber, a flow path blocking structure that forms a closed circuit communicating with the gap between the spool hole and the valve spool is set in the spool stroke region where the drain fluid is discharged. A spool valve characterized by The spool valve according to claim 1, wherein
The spool valve according to claim 1, wherein the flow path blocking structure is configured to form a closed circuit communicating with a gap between the spool hole and the valve spool after the stroke amount of the valve spool is stroked by a predetermined amount or more. The spool valve according to claim 1 or 2,
The valve spool is disposed so as to be able to stroke in the spool hole of the valve body, and a shift operation member is connected thereto,
The fluid chamber is formed at both end face positions of the valve spool,
At the time of 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 valve spool. A spool valve having a shift actuator operated in a direction. The spool valve according to claim 3,
The transmission having the shift actuator includes a first clutch that is engaged when an odd-numbered speed group is selected from among a plurality of speed stages, and a second clutch that is engaged when an even-numbered speed group is selected among a plurality of speed stages. A continuous 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 spool valve, which is a twin-clutch automatic manual transmission that operates a shift fork in a direction to obtain a shift stage selected by a shift hydraulic pressure produced by The spool valve according to any one of claims 1 to 4,
The valve spool is a stepped valve spool having a large diameter spool portion, a small diameter spool portion, and a spool step surface,
The spool hole is a stepped valve spool hole having a large diameter spool hole, a small diameter spool hole, and a body step surface,
As the fluid chamber, a first fluid chamber surrounded by the end surface of the small diameter spool portion and the small diameter spool hole, a second fluid surrounded by the peripheral surface of the small diameter spool portion, the spool step surface, the body step surface and the large diameter spool 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. A one-way ball that sets and blocks the flow from the second fluid chamber to the main circuit,
A spool valve characterized in that a second gap between the large diameter spool portion and the large diameter spool hole is set larger than a first gap between the small diameter spool portion and the small diameter spool hole. The spool valve 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. And a one-way ball which is set at a side position and blocks a flow from the fluid chamber to the main circuit. The spool valve according to any one of claims 1, 3 and 4,
The working fluid circuit has a main circuit connected to an end face position of the fluid chamber, and a one-way ball that is set at an intermediate position of the main circuit and blocks a flow from the fluid chamber to the main circuit. Spool valve to do. It is equipped with a valve spool that can be stroked in the spool hole of the valve body,
In the spool valve that discharges the drain fluid filled in the fluid chamber formed at the end of the valve spool during the valve operation,
A closed circuit is formed in the working fluid circuit connected to the fluid chamber during the spool stroke in which the drain fluid is discharged, and the drain fluid pressurized by the closed circuit is passed through the gap between the spool hole and the valve spool. A spool valve that discharges to the outside after a lapse.

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