JP6329189B2 - Control device for automatic transmission - Google Patents

Description

  The present invention relates to a control device for an automatic transmission.

  Patent Document 1 discloses a configuration for controlling a double clutch transmission. In this configuration, when clutch-on failure is detected for clutches of even-numbered shafts and odd-numbered shafts at the time of clutch-on failure, the double clutch transmission is controlled so as to command the neutral position to the synchronizer.

JP 2005-147403 A

  However, in the configuration of Patent Document 1, for example, when the transmission includes a shift stage configured to transmit the rotation of the input shaft directly to the output shaft via the one-way clutch, the input shaft When an abnormality occurs in the clutch connecting the engine and the engine, there is a possibility that power transmission cannot be interrupted.

  In view of the above problems, the present invention provides an automatic transmission control device capable of reliably interrupting power transmission when an abnormality occurs in clutch operation control.

A control device according to a first aspect of the present invention includes a first input shaft and a second input shaft connected to a prime mover of a vehicle via a first clutch and a second clutch, respectively.
An output shaft capable of transmitting power to the drive wheels of the vehicle;
A first transmission gear group, which is arranged between the first input shaft and the output shaft, and constitutes a plurality of first gears for transmitting power from the prime mover to the drive wheels while shifting;
A first switching mechanism capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through the plurality of first gears;
A second speed change gear group that is disposed between the second input shaft and the output shaft and that constitutes a plurality of second speed stages for transmitting power from the prime mover to the drive wheels while changing speed.
A second switching mechanism capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through the plurality of second gears;
The minimum transmission speeds of the plurality of first shift speeds and the plurality of second speed speeds are such that the rotation of the first input shaft is directly rotated via the one-way clutch. A control device for an automatic transmission configured to transmit to
First supply means for supplying hydraulic oil for operating the first clutch;
A hydraulic pressure release means arranged between the first clutch and the first supply means, and configured to release the hydraulic pressure of the hydraulic oil;
Detection means for detecting an operating state of the first supply means;
Oil pressure detecting means for detecting the oil pressure of the hydraulic oil in the oil pressure releasing means;
Control means for controlling the hydraulic pressure release means to release the hydraulic pressure when an abnormality of the first supply means is detected based on the detection result of the detection means;
Equipped with a,
The control means, when it is determined that there is no abnormality in the first supply means based on the detection result of the detection means, further determines the presence or absence of abnormality of the hydraulic pressure release means based on the detection result of the hydraulic pressure detection means,
Wherein, when said abnormality of the hydraulic release means based on a detection result of the pressure detecting means is detected, characterized that you control the first supply means to the first clutch disconnected state And

Further, according to the control device of the second aspect of the present invention, the hydraulic pressure release means includes:
A solenoid valve that inputs hydraulic oil of a predetermined hydraulic pressure, shuts off the hydraulic oil output in the set state, and outputs the hydraulic oil in the operational state;
By moving the valve body based on the operating state of the solenoid valve and the biasing force of the elastic member acting on the valve body, the input side oil passage, the output side first oil passage, and the output side second oil passage An oil passage switching valve for switching the communication state with any one of the oil passages,
By releasing the hydraulic pressure by moving the valve body based on the hydraulic pressure of the hydraulic oil input from the oil passage switching valve and the biasing force of the elastic member acting on the valve body, or releasing the hydraulic pressure A pressure release valve that switches to a sealed state,
It is characterized by providing.

Further, according to the control device of the third aspect of the present invention, the oil pressure detecting means is connected to the oil passage on the output side of the pressure release valve,
The pressure release valve shuts off the output of hydraulic oil to the output-side oil passage in the released state, and outputs the hydraulic oil input from the first oil passage to the output-side oil passage in the sealed state. The hydraulic pressure detecting means detects the hydraulic pressure of the hydraulic oil in the sealed state.

Further, according to the control device of the fourth aspect of the present invention, the control means controls the solenoid valve to the operating state when controlling to the release state for releasing the hydraulic pressure,
The oil path switching valve is configured to bring the input-side oil path and the output-side second oil path into communication with each other based on the hydraulic pressure of the hydraulic oil input from the solenoid valve.
The pressure release valve is in a release state in which the hydraulic pressure is released by moving the valve body based on the hydraulic pressure of hydraulic oil input from the second oil passage on the output side of the oil passage switching valve. It is characterized by doing.

Further, according to the control device of the fifth aspect of the present invention, the control means controls the solenoid valve to the set state when controlling to the sealed state that does not release the hydraulic pressure,
The oil passage switching valve makes the input-side oil passage and the output-side first oil passage communicate with each other based on the biasing force of the elastic member acting on the valve body,
The pressure release valve moves the valve body based on hydraulic pressure of hydraulic oil and an urging force of the elastic member input via the first oil passage on the output side of the oil passage switching valve. The sealing state is such that the hydraulic pressure is not released.

According to the configuration of the first to fifth aspects of the present invention, there is provided an automatic transmission control device capable of reliably interrupting power transmission when an abnormality occurs in clutch operation control. Is possible. Further, according to the configuration of the first aspect to the eighth aspect of the present invention, the configuration of the automatic transmission configured to transmit the rotation of the lowest shift stage directly to the output shaft via the one-way clutch. In this case, it is possible to prevent the engine stall from occurring by reliably interrupting the power transmission.

Further, according to the configuration of the first aspect of the present invention, the failure of the hydraulic pressure release mechanism itself can be detected, so that the failure is reliably detected, and the control device for the automatic transmission with higher structural reliability and safety. It becomes possible to provide.

In addition, according to the configurations of the first to fifth aspects of the present invention, when an abnormality occurs in the operation control of the clutch, it is ensured that the engine stall has occurred by releasing the hydraulic pressure and reliably shutting off the power transmission. It becomes possible to prevent.

The figure which shows typically schematic structure of the control apparatus which concerns on embodiment, and the automatic transmission to which this is applied. The block diagram which shows the electric constitution of the control apparatus which concerns on embodiment. The figure explaining the structure of the hydraulic pressure release mechanism which concerns on embodiment. The figure explaining the structure of the hydraulic pressure release mechanism which concerns on embodiment. The figure explaining the structure of the hydraulic seal mechanism which concerns on embodiment. The figure explaining the structure of the hydraulic seal mechanism which concerns on embodiment.

  Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to FIGS. 1 to 4A and 4B. However, the components described in this embodiment are merely examples, and the technical scope of the present invention is determined by the scope of the claims, and is not limited by the following individual embodiments. Absent.

[Configuration of automatic transmission]
A control device for an automatic transmission according to an embodiment of the present invention will be described. As shown in FIG. 1, the control device 1 of this embodiment is applied to an automatic transmission 10 of a vehicle V. The vehicle V includes an internal combustion engine (hereinafter referred to as “engine”) 3 as a prime mover. While the vehicle V is traveling, the power of the engine 3 is shifted via the automatic transmission 10 while being driven. , 63 (only one is shown).

  The vehicle V can be configured, for example, as a type in which the engine 3 is mounted near the center of the vehicle V and drives the driving wheels 63 as rear wheels, that is, a midship engine / rear drive type.

  The crankshaft 3a of the engine 3 is connected to the automatic transmission 10 via a flywheel 3b and a rotary shaft 3c. The crankshaft 3a, flywheel 3b and rotary shaft 3c are arranged concentrically with each other. ing.

  This automatic transmission 10 is of a dual clutch type automatic MT type, and includes a first clutch 5 and a second clutch 6, a first input shaft 11, a second input shaft 12, Two input shafts 20, an output shaft 30, a reverse shaft 40, a sub output shaft 50, and the like are provided. These shafts (the first input shaft 11, the second input shaft 12, the sub second input shaft 20, the output shaft 30, the reverse shaft 40, and the sub output shaft 50) all have a mission (not shown) via a bearing (not shown). The case is rotatably supported.

  The first clutch 5 is of a wet multi-plate clutch type. The first clutch 5 includes a flywheel type outer clutch plate 5a concentrically and integrally attached to the rotary shaft 3c, an inner clutch plate 5b concentrically and integrally attached to one end of the first input shaft 11, and an inner clutch plate 5b. A return spring (not shown) for urging the clutch plate 5b to be separated from the outer clutch plate 5a is provided.

  A first clutch / actuator 71 (first HCA: hydro pressure control actuator) supplies a hydraulic fluid of a predetermined hydraulic pressure (clutch pressure PH) to drive the inner clutch plate 5b to the outer clutch plate 5a side ( 1st supply part). The first clutch / actuator 71 (first HCA) is a combination of an electric motor electrically connected to the ECU 2 and a hydraulic circuit including a hydraulic device such as a hydraulic cylinder driven by the electric motor (both shown in FIG. Not shown). When the drive signal from the ECU 2 is supplied, the first clutch / actuator 71 drives the inner clutch plate 5b of the first clutch 5 toward the outer clutch plate 5a while resisting the urging force of the return spring. A predetermined hydraulic fluid is supplied through an oil passage 91. The ECU 2 connects / disconnects the first clutch 5 by controlling the first clutch / actuator 71 via the first clutch / actuator 71 (first HCA). When the first clutch 5 is connected, the power of the engine 3 is transmitted to the first input shaft 11 via the first clutch 5. That is, the power of the engine 3 is transmitted to a one-way clutch (hereinafter referred to as a one-way clutch 37) via the first input shaft 11, the first speed drive gear 13, and the first speed driven gear 36. In the automatic transmission according to the present embodiment, the lowest speed (first speed) of the plurality of speeds is such that the rotation of the first input shaft is directly transmitted to the output shaft 30 via the one-way clutch (one-way clutch 37). It is configured.

  Here, the rotation sensor 74 and the stroke sensor 75 detect the operating state of the first clutch / actuator 71 (first HCA) and input the detection result to the ECU 2. Based on the detection results of the rotation sensor 74 and the stroke sensor 75, the ECU 2 determines whether or not the first clutch / actuator 71 (first HCA) is operating normally. When the first clutch / actuator 71 (first HCA) is not operating normally, the ECU 2 controls the operation of each actuator to stop.

  In the configuration of the control device 1 of the present embodiment, the hydraulic oil pressure (clutch) of hydraulic oil supplied from the first clutch / actuator 71 to the oil passage 91 between the first clutch 5 and the first clutch / actuator 71 is further increased. A hydraulic pressure release mechanism 70 for releasing the pressure PH) is provided.

  The first clutch 5 cannot be disconnected at an appropriate timing if the motor or hydraulic circuit of the first clutch / actuator 71 breaks down while the hydraulic fluid having the clutch pressure PH is supplied from the first clutch / actuator 71. Can occur. In this case, the first clutch 5 remains connected, and power transmission to the one-way clutch 37 cannot be interrupted. The operation state of the first clutch / actuator 71 is detected by the rotation sensor 74 and the stroke sensor 75. The rotation sensor 74 detects the rotation state of the rotor of the electric motor of the first clutch / actuator 71. The stroke sensor 75 detects the operating state of the hydraulic equipment in the hydraulic circuit. When the ECU 2 determines that the first clutch / actuator 71 (first HCA) has failed (for example, the state in which the first clutch 5 cannot be disconnected) based on the detection results of the rotation sensor 74 and the stroke sensor 75, the control of the ECU 2 is performed. Based on this, the hydraulic pressure release mechanism 70 performs a release operation to release the clutch pressure PH. As a result, even when the first clutch / actuator 71 (first HCA) fails in a state where the hydraulic oil is supplied, the power transmission to the one-way clutch 37 can be cut off. A specific configuration of the hydraulic pressure release mechanism 70 will be described in detail later.

  The second clutch 6 is of the same wet multi-plate clutch type as the first clutch 5. The second clutch 6 includes an outer clutch plate 6a concentrically and integrally fixed to the outer clutch plate 5a of the first clutch 5, an inner clutch plate 6b integrally attached to one end of the second input shaft 12, and an inner clutch plate 6b. A return spring (not shown) for urging the clutch plate 6b to be separated from the outer clutch plate 6a is provided.

  The second clutch / actuator 72 (second HCA) serves as a supply unit (second supply unit) that supplies hydraulic oil of a predetermined hydraulic pressure (clutch pressure) to drive the inner clutch plate 6b to the outer clutch plate 6a side. Function. The second clutch / actuator 72 is configured in the same manner as the first clutch / actuator 71 described above, and resists the urging force of the return spring when the drive signal from the ECU 2 is supplied. A predetermined hydraulic fluid is supplied through an oil passage 92 so as to drive the inner clutch plate 6b toward the outer clutch plate 6a. The ECU 2 connects / disconnects the second clutch 6 by controlling the second clutch / actuator 72 via the second clutch / actuator 72 (second HCA). When the second clutch 6 is connected, the power of the engine 3 is transmitted to the second input shaft 12 via the second clutch 6. Here, the rotation sensor 74 and the stroke sensor 75 detect the operating state of the second clutch / actuator 72 (second HCA), and input the detection result to the ECU 2. Based on the detection results of the rotation sensor 74 and the stroke sensor 75, the ECU 2 determines whether or not the second clutch / actuator 72 (second HCA) is operating normally. When the second clutch / actuator 72 (second HCA) is not operating normally, the ECU 2 controls the operation of each actuator to be stopped.

  The inner clutch plate 5b of the first clutch 5 described above is fixed to the first input shaft 11 described above at one end portion on the engine 3 side. On the first input shaft 11, the second input shaft 12, the 3rd speed drive gear 14, the 3-5 speed synchro mechanism 18, the 5th speed drive gear 15, and the 7th speed are sequentially arranged from the engine 3 side to the opposite side. A drive gear 16, a 7-9 speed sync mechanism 19, and a first speed drive gear 13 are provided. These elements (second input shaft 12 to 7-9 speed sync mechanism 19) are arranged concentrically with the first input shaft 11. The 3-5 speed sync mechanism 18 and the 7-9 speed sync mechanism 19 function as a first switching mechanism capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through a plurality of first gears.

  The second input shaft 12 is hollow, and is rotatably fitted to the first input shaft 11 through its inner hole. The inner clutch plate 6b of the second clutch 6 is concentrically attached to one end of the second input shaft 12 on the engine 3 side, and the gear 12a is concentrically attached to the other end. Yes. The gear 12a always meshes with a reverse / input gear 41 described later.

  The third-speed drive gear 14 is rotatably provided on the first input shaft 11 and always meshes with a later-described third-speed driven gear 32 of the output shaft 30, and these gears (the third-speed drive gear 14, the third-speed drive gear 14). The third forward speed is constituted by the driven gear 32). Further, the third speed drive gear 14 is always meshed with a reverse gear 42 described later.

  The fifth speed drive gear 15 is rotatably provided on the first input shaft 11 and always meshes with a later-described 4-5 speed driven gear 33 of the output shaft 30, and these gears (fifth speed). The drive gear 15, 4-5 speed driven gear 33) constitutes the fifth forward speed.

  Further, although the detailed description of the 3-5 speed sync mechanism 18 described above is omitted here, it is configured in the same manner as the sync mechanism proposed by the present applicant in, for example, Japanese Patent No. 4242189, and is not shown in the figure. It is connected to a gear actuator 73 (see FIG. 2) via a 5-speed shift fork.

  The gear actuator 73 is a combination of an electric motor electrically connected to the ECU 2, a gear mechanism, and the like. During the speed change operation, the gear actuator 73 is controlled by the ECU 2 through a 3-5 speed shift fork. The 5-speed sync mechanism 18 is driven. As a result, the third speed drive gear 14 or the fifth speed drive gear 15 is connected to the first input shaft 11 or the connection is released, so that the third forward speed or the fifth forward speed is in the in-gear state and the neutral state. Can be switched between.

  The seventh speed drive gear 16 is rotatably provided on the first input shaft 11 and always meshes with a later-described 6-7 speed driven gear 34 of the output shaft 30, and these gears (seventh speed drive gear). The sixth forward speed is constituted by the 16, 6-7 speed driven gear 34). Further, the 9th speed drive gear 17 is rotatably provided on the first input shaft 11 and always meshes with an 8-9 speed driven gear 35 described later of the output shaft 30, and these gears (9th speed). The drive gear 17, 8-9 speed driven gear 35) constitutes the 9th forward speed.

  The 7-9 speed sync mechanism 19 is configured in the same manner as the 3-5 speed sync mechanism 18 described above, and is connected to the gear actuator 73 via a 7-9 speed shift fork (not shown). During the speed change operation, the 7-9 speed sync mechanism 19 is driven by the gear actuator 73, so that the seventh forward speed or the ninth forward speed is switched between the in-gear state and the neutral state.

  The first-speed drive gear 13 is fixed to the first input shaft 11 and always meshes with a later-described first-speed driven gear 36 of the output shaft 30, and these gears (first-speed drive gear 13, first-speed driven gear). 36) constitutes the first forward speed.

  On the auxiliary second input shaft 20 (second input shaft) described above, the input gear 27, the second speed driving gear 21, the second speed driving gear 21, the fourth speed synchronization mechanism 25, the fourth speed, in order from the engine 3 side to the opposite side. A drive gear 22, a 6-speed drive gear 23, a 6-8 speed sync mechanism 26, and an 8 speed drive gear 24 are provided. These elements (second speed drive gear 21 to input gear 27) are arranged concentrically with the sub second input shaft 20. The 2-4 speed sync mechanism 25 and the 6-8 speed sync mechanism 26 function as a second switching mechanism capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through a plurality of second gears.

  The input gear 27 is always meshed with the reverse input gear 41, and the reverse input gear 41 is always meshed with the gear 12a of the second input shaft 12 as described above. Thereby, the sub second input shaft 20 is connected to the second input shaft 12 via these gears (the input gear 27, the reverse / input gear 41, and the gear 12a).

  The second-speed drive gear 21 is rotatably provided on the sub-second input shaft 20 and always meshes with the second-speed driven gear 31 of the output shaft 30, and these gears (second-speed drive gear 21). The second forward gear 31) constitutes the second forward speed.

  Further, the 4-speed drive gear 22 is rotatably provided on the sub-second input shaft 20, and is always meshed with the 4-5-speed driven gear 33 of the output shaft 30, and these gears (4-speed drive) The gear 22, 4-5 speed driven gear 33) constitutes the fourth forward speed.

  The 2-4 speed sync mechanism 25 is connected to the gear actuator 73 described above via a 2-4 speed shift fork (not shown). During the speed change operation, the gear actuator 73 drives the 2-4 speed sync mechanism 25 to switch the second forward speed or the fourth forward speed between the in-gear state and the neutral state.

  The 6-speed drive gear 23 is rotatably provided on the sub-second input shaft 20 and always meshes with the 6-7-speed driven gear 34 of the output shaft 30, and these gears (6-speed drive). A forward sixth speed is constituted by the gears 23 and 6-7 (speed driven gear 34).

  Further, the 8-speed drive gear 24 is rotatably provided on the sub-second input shaft 20, and always meshes with the 8-9-speed driven gear 35 described above, and these gears (8-speed drive gear 24). , 8-9 speed driven gear 35) constitutes the eighth forward speed.

  The 6-8 speed sync mechanism 26 is connected to the gear actuator 73 described above via a 6-8 speed shift fork (not shown). During the speed change operation, the 6-8 speed sync mechanism 26 is driven by the gear actuator 73, so that the sixth forward speed or the eighth forward speed is switched between the in-gear state and the neutral state. In this embodiment, the 2nd speed drive gear 21 to the 8th speed drive gear 24, the 2nd speed driven gear 31, the 4th to 5th speed driven gear 33, the 6th to 7th speed driven gear, and the 8th to 9th speed driven gear 35 are the second. It corresponds to the transmission gear group, and the synchro mechanisms 25 and 26 and the gear actuator 73 correspond to the second switching mechanism.

  The output shaft 30 has a second speed driven gear 31, a third speed driven gear 32, a 4-5 speed driven gear 33, a 6-7 speed driven gear 34, and an 8-9 speed in order from the engine 3 side to the opposite side. A driven gear 35 and a first speed driven gear 36 are arranged. All of these four gears (second speed driven gear 31 to 8-9 speed driven gear 35) are fixed concentrically to the output shaft 30.

  The first speed driven gear 36 is concentrically connected to the output shaft 30 via a one-way clutch 37. As a result, when the rotation of the output shaft 30 during forward travel of the vehicle V is positive rotation, when the positive rotation speed of the first speed driven gear 36 is higher than the positive rotation speed of the output shaft 30, the first input shaft 11 Is transmitted to the output shaft 30 via the first speed drive gear 13, the first speed driven gear 36, and the one-way clutch 37. On the other hand, when the positive rotation speed of the first-speed driven gear 36 falls below the positive rotation speed of the output shaft 30, the function of the one-way clutch 37 causes the power transmission between the first input shaft 11 and the output shaft 30. Is cut off.

  As described above, the 2-speed driven gear 31 is driven by the 2-speed drive gear 21, the 4-5-speed driven gear 33 is driven by the 4-speed drive gear 22 and the 5-speed drive gear 15, and the 6-7-speed driven gear 34 is driven by the 6-speed. The 8th-9th driven gear 35 meshes with the 8th speed drive gear 24 and the 9th speed drive gear 17 respectively. Further, the third speed driven gear 32 always meshes with the gear 51 of the auxiliary output shaft 50 in addition to the above-described third speed drive gear 14.

  A gear 51 and a bevel gear 52 are concentrically fixed to the auxiliary output shaft 50, and the bevel gear 52 is disposed at an end portion on the engine 3 side and always meshes with the bevel gear 61 of the final reduction gear 60. With the above configuration, the power of the output shaft 30 is transmitted to the left and right drive wheels 63, 63 via the sub output shaft 50, the final reduction gear 60, and the drive shafts 62, 62.

  The output shaft 30 is provided with an output rotation speed sensor 80, and this output rotation speed sensor 80 is electrically connected to the ECU 2 (see FIG. 2). The output rotation speed sensor 80 detects the rotation speed of the output shaft 30 and outputs a detection signal representing it to the ECU 2. The ECU 2 calculates a vehicle speed VP that is the speed of the vehicle V based on the detection signal of the output rotation speed sensor 80.

  On the reverse shaft 40, a reverse input gear 41, a reverse synchronization mechanism 43, and a reverse gear 42 are provided in order from the engine 3 side toward the opposite side. The reverse input gear 41 is fixed concentrically to the reverse shaft 40 and always meshes with the input gear 27 described above. The reverse gear 42 is rotatably provided on the reverse shaft 40 and always meshes with the above-described third-speed drive gear 14 on the first input shaft 11.

  The reverse sync mechanism 43 is configured in the same manner as the 3-5 speed sync mechanism 18 described above, and is connected to the gear actuator 73 via a reverse shift fork (not shown). During a shift operation during reverse travel, the reverse sync mechanism 43 is driven by the gear actuator 73, whereby the reverse gear 42 is coupled to the reverse shaft 40. When the reverse gear is set to the neutral state, the reverse synchronization mechanism 43 releases the connection between the reverse gear 42 and the reverse shaft 40.

  A gear stage sensor 81 (see FIG. 2) is provided in the vicinity of the gear actuator 73. This gear stage sensor 81 detects and detects the operating state of the gear actuator 73 and outputs a detection signal representing it to the ECU 2.

  The vehicle V is provided with a shift lever device and an accelerator pedal (both not shown). This shift lever device is of the floor shift lever type, and has five positions as a shift position: a parking position, a reverse position, a neutral position, a drive position, and a sport position. The shift position is configured to be switchable between five positions.

  The shift lever device is provided with a shift position sensor 82 (see FIG. 2), and this shift position sensor 82 detects which of the five shift positions is selected in the shift lever device. , A detection signal representing it is output to the ECU 2.

  As shown in FIG. 2, a crank angle sensor 83 and an accelerator opening sensor 84 are electrically connected to the ECU 2. The crank angle sensor 83 outputs a CRK signal, which is a pulse signal, to the ECU 2 as the crankshaft 3a rotates. The CRK signal is output at one pulse every predetermined crank angle (for example, 1 °), and the ECU 2 calculates the rotational speed (hereinafter referred to as “engine speed”) NE of the engine 3 based on the CRK signal.

  Further, the accelerator opening sensor 84 detects the amount of depression of the accelerator pedal (hereinafter referred to as “accelerator opening”) AP, and outputs a detection signal representing the detected AP to the ECU 2.

  On the other hand, the ECU 2 is composed of a microcomputer including a CPU, RAM, ROM, an I / O interface (all not shown), and the various sensors described above (output rotational speed sensor 80 to accelerator opening sensor 84). In response to the detection signal, various control processes such as a shift control process are executed as described below.

[Hydraulic release mechanism]
Next, the configuration of the hydraulic pressure release mechanism 70 will be described. The hydraulic pressure release mechanism 70 is disposed between the first clutch 5 and the first clutch / actuator 71 and is configured to be able to release the hydraulic pressure of the hydraulic oil. 3A and 3B are diagrams showing the configuration of the hydraulic pressure release mechanism 70 according to the present embodiment. The hydraulic oil is input to the regulator valve 310 from the hydraulic circuit of the first clutch / actuator 71 and a hydraulic pump (both not shown). The regulator valve 310 supplies the hydraulic oil adjusted to a predetermined hydraulic pressure PR from the oil passage 93. Output. The oil passage 93 on the output side of the regulator valve 310 is connected to the oil passage switching valve 330, and the regulator valve 310 supplies hydraulic oil adjusted to a predetermined hydraulic pressure PR via the oil passage 93 to the oil passage switching valve 330. To enter. Further, the regulator valve 310 inputs the hydraulic oil adjusted to a predetermined hydraulic pressure PR to the solenoid valve 320 via the oil passage 93 and the oil passage 93 a branched from the oil passage 93.

(Solenoid valve 320)
The solenoid valve 320 is configured so that the spool valve is opened and closed by energizing the solenoid based on the control of the ECU 2. The solenoid valve 320 receives hydraulic oil PR from the regulator valve 310 via the oil passage 93 and the oil passage 93a, and shuts off the hydraulic oil output in the set state (OFF state) when the spool valve is closed. The hydraulic oil is output from the oil passage 94 in the operating state (ON state) where the valve is open. In other words, the solenoid valve 320 inputs hydraulic oil having a predetermined hydraulic pressure, shuts off the hydraulic oil output in the set state, and outputs the hydraulic oil in the activated state.

(Control of solenoid valve 320 by hydraulic sensor 76 and ECU 2)
When the solenoid valve 320 is in the set state, the hydraulic oil output from the oil passage 93 passes through the oil passage switching valve 330, the oil passage 95, the pressure release valve 340, and the oil passage 97, which will be described later, and the hydraulic sensor 76. Is input. The hydraulic pressure sensor 76 detects the hydraulic pressure of the hydraulic oil input from the oil passage 97 and inputs the detection result to the ECU 2. The ECU 2 determines whether or not a failure has occurred in the hydraulic system of the hydraulic pressure release mechanism 70 based on the comparison between the hydraulic pressure detected by the hydraulic pressure sensor 76 and the reference hydraulic pressure. The hydraulic pressure of the hydraulic fluid input from the oil passage 95 to the pressure release valve 340 and the hydraulic pressure of the hydraulic fluid output from the pressure release valve 340 via the oil passage 97 are substantially the same hydraulic pressure. This hydraulic pressure is substantially the same as the hydraulic pressure of the hydraulic oil output from the regulator valve 310, and is indicated as a hydraulic pressure PR in FIG. 3A.

  A rotation sensor 74 and a stroke sensor 75 are used to detect a failure of the first clutch / actuator 71. The ECU 2 determines whether or not the first clutch / actuator 71 is operating normally based on the detection results of the rotation sensor 74 and the stroke sensor 75. If the abnormality of the hydraulic pressure release mechanism 70 is detected based on the detection result of the hydraulic pressure sensor 76 (hydraulic pressure detecting unit) when the first clutch / actuator 71 is operating normally, the ECU 2 determines that the first clutch 5 The first clutch / actuator 71 is controlled so as to be in a disconnected state.

  When the hydraulic pressure detected by the hydraulic sensor 76 has reached the reference hydraulic pressure, the ECU 2 determines that the hydraulic system in the hydraulic pressure release mechanism 70 is operating normally. When the hydraulic system is operating normally, the ECU 2 controls the solenoid valve 320 to be in the set state (OFF state). That is, the solenoid valve 320 blocks the output of hydraulic oil from the oil passage 94. FIG. 3A is a diagram illustrating a state of the hydraulic pressure release mechanism 70 when the solenoid valve 320 is in the set state (OFF state). In each oil passage shown in FIG. 3A, hatched portions indicate the flow of hydraulic oil. When the rotation sensor 74, the stroke sensor 75, and the hydraulic sensor 76 all detect a normal state, the hydraulic pressure release mechanism 70 does not release the clutch pressure, and the ECU 2 determines that the normal state and the first clutch actuator 71 is controlled.

  On the other hand, when the ECU 2 is in a state (operating state) where the first clutch / actuator 71 fails and the first clutch 5 cannot be disconnected based on the detection results of the rotation sensor 74 and the stroke sensor 75, the ECU 2 The ECU 2 controls to stop the operation of the motor 71 and the hydraulic actuator constituting the hydraulic circuit, and the ECU 2 controls the hydraulic pressure release mechanism 70 to control the hydraulic oil pressure supplied from the first clutch actuator 71. Release (clutch pressure). When the ECU 2 determines from the detection results of the rotation sensor 74 and the stroke sensor 75 that a failure has occurred in the first clutch / actuator 71, the ECU 2 releases the solenoid valve 320 of the hydraulic pressure release mechanism 70 in order to release the clutch pressure. Is controlled so as to be in an operating state (ON state). That is, the ECU 2 controls the energization of the solenoid to switch the state of the solenoid valve 320 from the set state (OFF state) to the operating state (ON state). FIG. 3B is a diagram illustrating a state of the hydraulic pressure release mechanism 70 when the solenoid valve 320 is in the operating state (ON state). In the oil passage shown in FIG. 3B, hatched portions indicate the flow of hydraulic oil.

  Based on the control of the ECU 2, when the spool valve is opened by energizing the solenoid, the solenoid valve 320 outputs the hydraulic oil input from the oil path 93 a from the output oil path 94. In the present embodiment, the hydraulic oil pressure input to the solenoid valve 320 is PR. In order to explicitly distinguish the hydraulic oil pressure input to the solenoid valve 320 from the hydraulic oil pressure output from the solenoid valve 320, the hydraulic oil pressure output from the solenoid valve 320 is expressed as a solenoid pressure SA. . The solenoid pressure SA is substantially the same as the hydraulic pressure PR.

(Oil passage switching valve 330)
The oil passage switching valve 330 moves the valve body 331 based on the operating state of the solenoid valve 320 and the urging force of the elastic member 332 acting on the valve body 331, so that the oil passage 93 on the input side and the output side The communication state of one of the oil passages 95 and the second oil passage 96 on the output side is switched.

  The valve element 331 of the oil passage switching valve 330 is urged from the right side to the left side of the sheet by the urging force of the elastic member (spring) 332. When the solenoid valve 320 is in the set state, hydraulic oil is not input from the oil passage 94 to the oil passage switching valve 330, and therefore the urging force acting on the valve body 331 is only the urging force of the elastic member (spring) 332. On the other hand, when the solenoid valve 320 is in the operating state, the hydraulic oil is input from the oil passage 94 to the oil passage switching valve 330, and the hydraulic pressure (solenoid pressure SA) of the hydraulic oil urges the valve body 331 of the oil passage switching valve 330. To do. That is, when the solenoid valve 320 is in the operating state (ON state), the valve body 331 is urged from the left side to the right side of the drawing by the hydraulic pressure of the hydraulic oil (solenoid pressure SA) input from the oil passage 94. . In the set state (OFF state) or the activated state (ON state) of the solenoid valve 320, the oil passage switching valve 330 moves the position of the valve body 331 based on the urging force acting on the valve body 331, so that the oil on the input side The communication state of the path 93 and a plurality of output-side oil paths (one of the output-side first oil path 95 and the output-side second oil path 96) is switched.

  In a state (set state) where hydraulic oil having solenoid pressure SA is not input from the solenoid valve 320 to the oil passage switching valve 330 via the oil passage 94, the valve body 331 is moved by the urging force of the elastic member (spring) 332. The oil passage 93 on the input side of the oil passage switching valve 330 and the oil passage 95 (first oil passage) on the output side communicate with each other (FIG. 3A). In this communication state, the oil passage switching valve 330 outputs the hydraulic oil input from the oil passage 93 from the oil passage 95 (first oil passage). Here, the oil passage 95a is an oil passage branched from the oil passage 95, and when hydraulic fluid is output from the oil passage switching valve 330, the hydraulic oil is released through the oil passage 95 and the branched oil passage 95a. Input to valve 340.

  On the other hand, when the state of the solenoid valve 320 changes from the set state to the operating state under the control of the ECU 2, the hydraulic oil having the solenoid pressure SA is input to the oil passage switching valve 330 through the oil passage 94 (FIG. 3B). When the biasing force due to the solenoid pressure SA becomes larger than the biasing force due to the elastic member (spring) 332, the valve body 331 biases the difference between the biasing force based on the solenoid pressure SA and the biasing force based on the elastic member (spring) 332. In response to this, it moves from the left side to the right side of the page. Due to the movement of the valve body 331, the connection relation of the oil passages communicated in the set state of the solenoid valve 320 is switched, and the oil passage 93 on the input side and the oil passage 96 on the output side of the oil passage switching valve 330 (the second oil passage 96) Oil channel). In the communication state of the oil passage, the oil passage switching valve 330 outputs the hydraulic oil input from the oil passage 93 from the oil passage 96 (second oil passage).

(Pressure release valve 340)
The pressure release valve 340 releases the hydraulic pressure by moving the valve body 341 based on the hydraulic pressure of the hydraulic oil input from the oil passage switching valve 330 and the urging force of the elastic member 342 acting on the valve body 341. Or, switch to a sealed state that does not release hydraulic pressure. In the released state, the pressure release valve 340 releases the hydraulic pressure of the hydraulic oil supplied via the oil passage 91a. In the sealed state, the pressure release valve 340 releases the hydraulic pressure of the hydraulic oil supplied via the oil passage 91a. Works to seal.

  The valve body 341 of the pressure release valve 340 is urged from the right side to the left side of the sheet by the urging force of the elastic member (spring) 342. When hydraulic oil is output from the oil passage 95 on the output side of the oil passage switching valve 330 (FIG. 3A), the hydraulic oil is input to the pressure release valve 340 via the oil passage 95 and the branched oil passage 95a. The hydraulic pressure PR of the hydraulic oil input through the oil passage 95a urges the valve body 341 of the pressure release valve 340 from the right side to the left side of the drawing. In a state where the valve body 341 of the pressure release valve 340 is urged from the right side to the left side of the drawing, the oil path 95 on the input side and the oil path 97 on the output side of the pressure release valve 340 communicate with each other. In the communication state of the oil passage, the pressure release valve 340 outputs the hydraulic oil input from the oil passage 95 from the oil passage 97.

  A hydraulic sensor 76 is connected to the oil passage 97 on the output side of the pressure release valve 340. The pressure release valve 340 shuts off the output of the hydraulic oil to the oil passage 97 on the output side in the released state, and outputs the hydraulic oil input from the oil passage 95 (first oil passage) in the sealed state. Output to 97. The oil pressure sensor 76 detects the oil pressure of the hydraulic oil in the sealed state. When hydraulic fluid is output from the oil passage 97 on the output side of the pressure release valve 340 in the sealed state, the hydraulic fluid is input to the hydraulic sensor 76 via the oil passage 97. The hydraulic sensor 76 detects the hydraulic pressure of the input hydraulic oil and inputs the detection result to the ECU 2. Based on the detection result of the hydraulic sensor 76, the ECU 2 determines whether or not a failure has occurred in the hydraulic system of the pressure release mechanism 70. For example, when the oil pressure detected by the oil pressure sensor 76 does not reach the reference oil pressure in the sealed state, the ECU 2 determines that a failure has occurred in the hydraulic system of the pressure release mechanism 70.

  On the other hand, when hydraulic oil is output from the oil passage 96 on the output side of the oil passage switching valve 330 (FIG. 3B), the hydraulic oil is input to the pressure release valve 340 via the oil passage 96. The hydraulic pressure of the hydraulic oil input via the oil passage 96 urges the valve body 341 of the pressure release valve 340 from the left side to the right side of the drawing. When hydraulic oil is input from the oil passage 96 to the pressure release valve 340 and the biasing force due to the hydraulic pressure of the input hydraulic oil becomes larger than the biasing force by the elastic member (spring) 342, the valve body 341 of the pressure release valve 340 is It moves from the left side of the drawing to the right side according to the difference between the biasing force based on the hydraulic pressure PR of the hydraulic oil and the biasing force based on the elastic member (spring) 332. By the movement of the valve body 341, the connection relation of the oil passage of the pressure release valve 340 is switched, and the oil passage 95 on the input side and the oil passage 97 on the output side of the pressure release valve 340 are cut off. In the released state in which the hydraulic pressure is released, the hydraulic oil output to the oil passage 97 on the output side is cut off. Therefore, when the hydraulic system of the hydraulic release mechanism 70 is in a normal operating state, the hydraulic pressure detected by the hydraulic sensor 76 Becomes zero. The hydraulic sensor 76 detects that the hydraulic oil pressure has become zero, and inputs the detection result to the ECU 2. The ECU 2 confirms that the oil path switching operation of the oil path switching valve 330 and the pressure release valve 340 has been normally executed by controlling the solenoid valve 320 to the operating state based on the detection result of the hydraulic sensor 76. .

(When controlling to the released state)
The ECU 2 controls the solenoid valve 320 to the operating state when controlling to the release state in which the hydraulic pressure is released. The oil passage switching valve 330 brings the input-side oil passage 93 and the output-side oil passage 96 (second oil passage) into communication based on the hydraulic pressure of the hydraulic oil input from the solenoid valve 320. Then, the pressure release valve 340 moves the valve body 341 based on the hydraulic pressure of the hydraulic oil input from the oil path 96 (second oil path) on the output side of the oil path switching valve 330, thereby reducing the hydraulic pressure. Release to release state.

(When controlling to a sealed state)
The ECU 2 controls the solenoid valve 320 to a set state when controlling to a sealed state where the hydraulic pressure is not released. The oil passage switching valve 330 brings the input-side oil passage 93 and the output-side oil passage 95 (first oil passage) into communication based on the biasing force of the elastic member 332 acting on the valve body 331. The pressure release valve 340 is a valve body based on the hydraulic pressure of hydraulic oil and the urging force of the elastic member 342 input via the oil passage 95 (first oil passage) on the output side of the oil passage switching valve 330. By moving 341, a sealing state in which the hydraulic pressure is not released is achieved.

[Hydraulic seal mechanism 350]
The hydraulic pressure release mechanism 70 releases the hydraulic oil pressure (clutch pressure PH) supplied from the first clutch / actuator 71 to the first clutch 5 in accordance with the movement of the moving mechanism (pressure release valve 340). Or a hydraulic seal mechanism 350 that switches to a sealed state in which the hydraulic pressure is not released.

  When there is no failure in the hydraulic system, the hydraulic seal mechanism 350 is supplied with hydraulic fluid of the clutch pressure PH from the branch oil passage 91a supplied from the first clutch / actuator 71 to the first clutch 5 via the oil passage 91. Seal (seal) so that it is not released. Further, when a failure occurs in the first clutch / actuator 71 or the hydraulic system in a state where the hydraulic oil having the clutch pressure PH is supplied to the first clutch 5, the hydraulic seal mechanism 350 is connected to the casing 351 from the branch oil passage 91a. The hydraulic oil having the clutch pressure PH that has entered the internal space is released through the opening 356 communicating with the external space.

  4A and 4B are diagrams illustrating the configuration of the hydraulic seal mechanism 350 according to the embodiment. FIG. 4A is a diagram illustrating a state where the hydraulic seal mechanism 350 seals (seals) the hydraulic oil pressure, and FIG. 4B is a diagram illustrating a state where the hydraulic seal mechanism 350 releases the hydraulic oil. The hydraulic seal mechanism 350 includes a hollow housing 351, a seal member 352 provided on the inner periphery of the housing 351, a metal ball 353 that is disposed in the housing 351 and is movable along the seal member 352. The piston 354 is movable in the internal space of the housing 351 by a moving mechanism (pressure release valve 340). An opening 356 that communicates the internal space of the housing 351 and the external space of the housing 351 is provided on the side surface of the hollow housing 351. As shown in FIG. 4B, the opening 356 functions as a hydraulic oil passage that opens the hydraulic oil that has entered the internal space of the housing 351 from the oil passage 91 a to the external space of the housing 351.

  The oil passage 91 is an oil passage connecting the first clutch 5 and the first clutch / actuator 71, and the oil passage 91 a is an oil passage branched from the oil passage 91. The end of the hollow casing 351 on the left side of the drawing is referred to as “one end side”, and the end of the hollow casing 351 on the right side of the drawing is referred to as “other end side”. One end side of the hollow casing 351 is connected to an oil passage 91a to which hydraulic oil of a predetermined pressure is input, and the other end side is connected to a moving mechanism (pressure release valve 340). Seal member 352 has a tapered surface 355 formed so that the thickness of seal member 352 in the radial direction of housing 351 gradually increases toward the opening of the oil passage.

  The metal ball 353 pressed by the movement of the piston 354 from the other end side to the one end side of the housing 351 seals the opening of the oil passage 91a by being in close contact with the tapered surface 355. On the other hand, when the piston 354 moves from one end side to the other end side of the housing 351, the piston 354 releases the pressed state of the metal ball 353 and releases the opening of the oil passage 91a. The opening 356 communicates with the oil passage 91a by releasing the pressed state.

  A piston 354 is provided at the end of the valve body 341 of the pressure release valve 340 constituting the moving mechanism, and the piston 354 is configured to move in accordance with the movement of the valve body 341. For example, when the valve body 341 moves from the right side to the left side of the paper (from the other side of the housing 351 to the one side), the piston 354 also moves from the right side to the left side of the paper (from the other side to one side). ) When the valve body 341 of the pressure release valve 340 moves to the forward limit position (forward stroke end) where the valve body 341 can move from the right side to the left side (the other end side to the one end side), the piston 354 becomes a metal as shown in FIG. 4A. The metal ball 353 is brought into close contact with the tapered surface 355 of the seal member 352 by pressing the ball 353.

  In FIG. 4A, a metal ball 353 indicated by a broken line indicates a retreat limit position (retreat stroke end) at which the valve element 341 of the pressure release valve 340 can move from the left side to the right side (from one end side to the other end side of the housing 351). ) Illustrates the position of the metal sphere 353 in a state where it has been moved to (). The broken metal ball 353 is energized by the hydraulic pressure (clutch pressure: PH) of the hydraulic oil that has entered the internal space of the housing 351 from the oil passage 91a, and is pushed back to the position where the piston 354 moves backward (reverse stroke end). ing.

  The seal member 352 is made of an elastic member such as rubber, for example. When the valve body 341 of the pressure release valve 340 moves to the forward stroke end and the metal ball 353 is pressed against the taper surface 355 of the seal member 352 by the movement of the piston 354, the taper surface 355 becomes the surface shape of the metal ball 353. Accordingly, the taper surface 355 of the seal member 352 and the metal ball 353 are in close contact with each other. In this state, the tapered surface 355 and the metal ball 353 seal the opening of the oil passage 91a.

  Further, the seal member 352 is formed with a side seal portion 352a that seals the outer peripheral portion of the side surface of the oil passage 91a. The side seal portion 352a is formed so as to be in close contact with the outer peripheral portion of the side surface of the oil passage 91a. The side seal portion 352a is sealed (sealed) by the tapered surface 355 and the metal ball 353 at the opening of the oil passage 91a. This prevents the hydraulic fluid from leaking from the outer peripheral portion of the side surface of the oil passage 91a.

  In addition, the seal member 352 has an overhang portion 352 b that projects to the outside of the housing 351 along the axial direction C of the housing 351 and projects along the radial direction of the housing 351 that intersects the axial direction C. Is formed. The overhang portion 352b is formed so as to be in close contact with the outer peripheral portion of the side surface of the oil passage 91a in the axial direction C of the housing 351, and is sealed by the tapered surface 355 and the metal ball 353 ( The sealed hydraulic oil is prevented from leaking from the outer peripheral portion of the side surface of the oil passage 91a. Furthermore, the overhanging portion 352b is formed to have an overhanging shape D2 that is larger than the opening diameter D1 on one end side of the housing 351 in the radial direction of the housing 351 that intersects the axial direction C. Even when a load from one end side to the other end side of the housing 351 is applied to the sealing member 352, the sealing member 352 has a protruding shape D2 larger than the opening diameter D1 of the housing 351. Therefore, the position of the seal member 352 with respect to the housing 351 is maintained.

  Furthermore, a convex portion 352 c is formed on the inner peripheral surface of the seal member 352 so as to protrude from the inner peripheral surface toward the inside in the radial direction of the housing 351. The convex portion 352c seals the hydraulic pressure of the hydraulic oil so that the hydraulic oil input from the oil passage 96 does not enter the metal ball 353 side. In a state where the piston 354 is inserted into the internal space of the housing 351, the convex portion 352c is formed so as to be in close contact with the outer peripheral portion of the piston 354. A taper 359 is formed on the end surface of the piston 354 in order to prevent damage to the convex portion 352c due to the end surface of the piston 354 coming into contact with the convex portion 352c when the piston 354 moves. The taper 359 is formed so that the diameter of the piston 354 gradually decreases along the direction from the other end side to the one end side of the housing 351. In a state where the piston 354 is inserted into the internal space of the housing 351, the convex portion 352c seals the hydraulic oil by closely contacting the outer peripheral portion of the piston 354. In any of the moving state of the piston 354, the state in which the piston 354 has moved to the forward stroke end (FIG. 4A), and the state in which the piston 354 has moved to the backward stroke end (FIG. 4B), the convex portion 352c It is possible to maintain the state of being in close contact with the outer peripheral portion and seal (seal) the hydraulic oil. The seal member 352 has a structure in which a tapered surface 355, a side surface seal portion 352a, an overhang portion 352b, and a convex portion 352c are integrally formed.

  For example, when the piston 354 moves from the forward stroke end to the backward stroke end (from one end side to the other end side of the housing 351), the seal member 352 has a protrusion 352c that contacts the outer peripheral portion of the piston 354. A load from one end side of the housing 351 toward the other end side acts. This load acts to shift the position of the seal member 352 inside the housing 351, but the overhang portion 352b of the seal member 352 has an overhang shape D2 larger than the opening diameter D1 on one end side of the housing 351. Thus, the position of the seal member 352 relative to the housing 351 is maintained.

  The metal ball 353 can be, for example, a steel ball or stainless steel ball used for a rolling element of a bearing, and the metal ball has a processing accuracy (sphericity, surface roughness) equivalent to that of the rolling element of the bearing. 353 is processed.

  Focusing on the hydraulic pressure (load) acting on the metal ball 353, if the cross-sectional area of the oil passage 91a is A1, and the hydraulic oil pressure (clutch pressure: PH) of the hydraulic oil supplied through the oil passage 91a is a rough load The load F1 (= A1 × PH) acts on the metal sphere 353.

  On the other hand, the biasing force of the elastic member 342 acting on the valve body 341 is K, the pressure receiving area of the pressure receiving portion 349 of the valve body 341 of the pressure release valve 340 is A2, and the operation input to the pressure release valve 340 from the oil passage 95a. Assuming that the oil pressure of the oil is PR, a load F2 (= A2 × PR + K) acts on the metal ball 353 via the piston 354 as a rough load. The load F2 acts on the metal ball 353 from the direction facing the load F1. With the valve body 341 of the pressure release valve 340 moved to the forward stroke end on the left side of the paper surface, the hydraulic pressure of the hydraulic oil to be entered from the oil passage 91a into the housing 351 by the metal ball 353 in close contact with the tapered surface 355 ( The relationship between the loads F1 and F2 has a magnitude relationship of F2> F1 so that the clutch pressure PH) can be reliably sealed.

  The hydraulic pressure (clutch pressure: PH) of the hydraulic oil supplied through the oil passage 91a is a known pressure supplied to drive the inner clutch plate 5b of the first clutch 5 to the outer clutch plate 5a side, The hydraulic pressure PR of the hydraulic oil input from the oil passage 95a is a known pressure adjusted by the regulator valve 910. The pressure receiving area A2 of the pressure receiving portion 349 of the valve body 341 can be determined in consideration of the operation responsiveness of the pressure release valve 340. Further, the biasing force K of the elastic member 342 can be acquired based on a known spring constant. If the urging force K of the elastic member 342, the hydraulic pressure (PH and PR), and the pressure receiving area A2 of the valve body 341 are determined, the oil passage 91a satisfies the magnitude relationship (F2> F1) of the load acting on the metal ball 353. The cross sectional area A1 (the diameter Φ1 of the oil passage 91a) can be set. As a result, it is possible to realize a hydraulic seal mechanism that is excellent in operation responsiveness and that can reliably seal the hydraulic pressure.

  In FIG. 4B, the pressure receiving area of the pressure receiving portion S1 and the pressure receiving portion S2 of the valve body 341 is A3. Assuming that the hydraulic pressure of the hydraulic fluid input from the oil passage 96 to the pressure release valve 340 is PR, a load F3 (= A3 × PR) urges the valve body 341 from the left side to the right side as viewed in the drawing. The urging force K of the elastic member 342 acts in a direction opposite to the load F3, and the valve body 341 of the pressure release valve 340 is changed from the left side to the right side of the drawing according to the difference urging force (F3-K). As the valve body 341 moves, the piston 341 also moves from the left side to the right side of the drawing.

  In FIG. 4B, the metal ball 353 indicated by a solid line indicates the position of the metal ball 353 in a state in which the valve element 341 of the pressure release valve 340 has moved from the left side to the right side of the drawing to the reverse limit position (reverse stroke end). This is just an example. A metal ball 353 indicated by a broken line exemplifies the position of the metal ball 353 in a state where the valve body 341 of the pressure release valve 340 has moved to the forward stroke end.

  In the state shown in FIG. 4B, the load F2 as shown in FIG. 4A does not act on the metal ball 353, and the metal ball 353 is attached by the hydraulic pressure (clutch pressure: PH) of the hydraulic oil that has entered from the oil passage 91a. Be forced. Further, the valve body 341 of the pressure release valve 340 moves from the left side to the right side of the drawing sheet by applying a differential biasing force (F3-K) as shown in FIG. 4B. The piston 341 moves from the left side to the right side of the drawing according to the movement of the valve body 341, and is pushed back to the position of the piston 354 in the backward limit (reverse stroke end). The hydraulic oil 400 that has entered the internal space of the housing 351 from the oil passage 91 a is released to the external space of the housing 351 through the opening 356. The convex portion 352c seals the hydraulic oil input from the oil passage 96 so as not to enter the metal ball 353 side, and the hydraulic oil 400 that has entered the internal space of the housing 351 from the oil passage 91a is a pressure release valve. 340 can be sealed so as not to enter the valve body 341 side.

(Fault monitoring control)
It is assumed that the ECU 2 alternately performs the operation determination of the first clutch / actuator 71 (first HCA) and the second clutch / actuator 72 (second HCA) at a predetermined time interval, not at the same timing.

  The ECU 2 is in a connected state in which the second clutch 6 is operated, and in a disconnected state in which the first clutch 5 is not operated, based on the detection result of the detection unit (the rotation sensor 74 and the stroke sensor 75). The ECU 2 determines whether there is an abnormality in the actuator 71 (first supply unit), and the ECU 2 controls the hydraulic pressure release mechanism 70 when an abnormality in the first clutch / actuator 71 (first supply unit) is detected based on the detection result. To release the hydraulic pressure.

  In addition, when the ECU 22 determines that the first clutch / actuator 71 (first supply unit) is normal based on the detection results of the detection unit (the rotation sensor 74 and the stroke sensor 75), the ECU 22 further determines that the hydraulic sensor 76 Based on this detection result, the presence / absence of abnormality of the hydraulic pressure release mechanism 70 is determined. The ECU 2 controls the first clutch / actuator 71 so that the first clutch 5 is not operated when an abnormality of the hydraulic pressure release mechanism 70 is detected based on the detection result.

  For example, when the first clutch / actuator 71 (first HCA) is operating and the gear position where the second clutch / actuator 72 (second HCA) is not operating is selected, the ECU 2 is not operating. The operation of the clutch / actuator 72 (second HCA) is confirmed based on the detection results of the rotation sensor 74 and the stroke sensor 75.

  In addition, when the second clutch / actuator 72 (second HCA) is in operation and the gear position at which the first clutch / actuator 71 (first HCA) is not operating is selected, the ECU 2 is not operating first. The clutch actuator 71 (first HCA) is checked for operation based on the detection results of the rotation sensor 74 and the stroke sensor 75 (first operation check). From the detection results of the rotation sensor 74 and the stroke sensor 75, when the first clutch / actuator 71 fails and the first clutch 5 cannot be disconnected, the ECU 2 controls the hydraulic pressure release mechanism 70 to The hydraulic pressure (clutch pressure) of the hydraulic oil supplied from the actuator 71 is released. For the first clutch / actuator 71 (first HCA) connected to the lowest gear (first-speed drive gear 13), the ECU 2 further performs an operation check based on the detection result of the hydraulic sensor 76 (second operation check). . If the abnormality of the hydraulic pressure release mechanism 70 is detected based on the detection result of the hydraulic sensor 76 when the first clutch / actuator 71 is operating normally from the detection results of the rotation sensor 74 and the stroke sensor 75, the ECU 2 Controls the first clutch / actuator 71 so as not to operate the first clutch 5. That is, when an abnormality of the hydraulic pressure release mechanism 70 is detected based on the detection result of the hydraulic pressure sensor 76, the ECU 2 controls the first clutch / actuator 71 so as to put the first clutch 5 in the disconnected state.

[Summary of embodiment]
Configuration 1. The control device for an automatic transmission according to this embodiment includes the following configuration. That is, the control device for the automatic transmission includes a first input shaft (11) and a second input shaft (coupled to the motor (3) of the vehicle via the first clutch (5) and the second clutch (6), respectively. 20)
An output shaft (30) capable of transmitting power to the drive wheels of the vehicle;
A first transmission gear group (13 to 13), which is disposed between the first input shaft and the output shaft and constitutes a plurality of first gears for transmitting power from the prime mover to the drive wheels while shifting the power. 17)
A first switching mechanism (18, 19) capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through the plurality of first gears;
A second transmission gear group (21 to 21), which is arranged between the second input shaft and the output shaft and constitutes a plurality of second gears for transmitting the power from the prime mover to the drive wheels while shifting the power. 24)
A second switching mechanism (25, 26) capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through the plurality of second gears;
The lowest gear (13) in the plurality of first gears and the plurality of second gears rotates the first input shaft via a one-way clutch (37). A control device (1) for an automatic transmission (10) configured to transmit directly to the output shaft,
First supply means (71) for supplying hydraulic oil for operating the first clutch;
A hydraulic pressure release means (70) disposed between the first clutch (5) and the first supply means (71) and configured to release the hydraulic pressure of the hydraulic oil;
Detection means (74, 75) for detecting an operating state of the first supply means;
Control means (2) for controlling the hydraulic pressure release means to release the hydraulic pressure when an abnormality of the first supply means is detected based on the detection result of the detection means;
It is characterized by providing.

Configuration 2. The control device further includes a hydraulic pressure detection means (76) for detecting the hydraulic pressure of the hydraulic oil in the hydraulic pressure release means (70),
The control means (2) determines whether there is an abnormality in the hydraulic pressure release means (70) based on the detection result of the hydraulic pressure detection means (76), and controls the operation of the first supply means based on the determination result. It is characterized by controlling.

Configuration 3. In the control device, when the control means (2) determines that there is no abnormality in the first supply means (71) based on the detection results of the detection means (74, 75), the hydraulic pressure detection means (76) ) Based on the detection result of the hydraulic pressure release means (70).
When the abnormality of the hydraulic pressure release means (70) is detected based on the detection result of the hydraulic pressure detection means (76), the control means (2) causes the first clutch (5) to be disconnected. The first supply means (71) is controlled.

Configuration 4. In the control device, the hydraulic pressure release means (70) includes:
A solenoid valve (320) for inputting hydraulic oil of a predetermined hydraulic pressure, shutting off the hydraulic oil output in the set state, and outputting the hydraulic oil in the activated state;
By moving the valve body (331) based on the operating state of the solenoid valve (320) and the biasing force of the elastic member (332) acting on the valve body (331), the oil path (93) on the input side An oil path switching valve (330) for switching the communication state with any one of the first oil path (95) on the output side and the second oil path (96) on the output side;
By moving the valve body (341) based on the hydraulic pressure of the hydraulic oil input from the oil path switching valve (330) and the biasing force of the elastic member (342) acting on the valve body (341), the hydraulic pressure is increased. A pressure release valve (340) for switching to a release state in which the hydraulic pressure is released or a seal state in which the hydraulic pressure is not released,
It is characterized by providing.

Configuration 5. In the control device, the oil pressure detecting means (76) is connected to the oil passage (97) on the output side of the pressure release valve (340),
The pressure release valve (340) shuts off the output of hydraulic oil to the output oil passage (97) in the released state, and the hydraulic oil input from the first oil passage (95) in the sealed state. To the oil passage (97) on the output side,
The hydraulic pressure detection means (76) detects the hydraulic pressure of the hydraulic oil in the sealed state.

Configuration 6. In the control device, the control means (2) controls the solenoid valve (320) to the operating state when controlling to the release state for releasing the hydraulic pressure,
The oil passage changeover valve (330) is configured so that the oil passage (93) on the input side and the second oil passage (96) on the output side are based on the hydraulic pressure of the hydraulic oil input from the solenoid valve (320). And the communication state,
The pressure release valve (340) moves the valve body (341) based on the hydraulic pressure of hydraulic fluid input from the second oil path (96) on the output side of the oil path switching valve (330). To release the hydraulic pressure.

Configuration 7. In the control device, the control means (2) controls the solenoid valve (320) to the set state when controlling to a sealed state that does not release the hydraulic pressure,
The oil passage changeover valve (330) is configured so that the oil passage (93) on the input side and the first oil on the output side are based on the urging force of the elastic member (332) acting on the valve body (331). The road (95) in communication,
The pressure release valve (340) includes hydraulic oil pressure input through the first oil passage (95) on the output side of the oil passage switching valve (330) and the biasing force of the elastic member (342). On the basis of the above, the valve body (341) is moved to be in a sealed state in which the hydraulic pressure is not released.

  According to the above-described configurations 1 to 7, it is possible to provide a control device for an automatic transmission capable of reliably interrupting power transmission when an abnormality occurs in the operation control of the clutch. Further, according to the above-described configurations 1 to 8, in the configuration of the automatic transmission configured to transmit the rotation of the lowest shift speed directly to the output shaft via the one-way clutch, the power transmission is ensured. By shutting off, it is possible to prevent the engine stall.

  Further, according to the above-described configuration 2, since a failure of the hydraulic pressure release mechanism itself can be detected, it is possible to reliably detect the failure and provide a control device for an automatic transmission with higher structural reliability and safety. It becomes possible.

  Further, according to the above-described configurations 3 to 7, when an abnormality occurs in the operation control of the clutch, it is possible to reliably prevent the engine stall by releasing the hydraulic pressure and reliably blocking the power transmission. It becomes possible.

  V vehicle, 1 control device, 2 ECU, 3 engine, 5 first clutch, 6 second clutch, 10 automatic transmission

Claims (5)

A first input shaft and a second input shaft respectively connected to a prime mover of the vehicle via a first clutch and a second clutch;
An output shaft capable of transmitting power to the drive wheels of the vehicle;
A first transmission gear group, which is arranged between the first input shaft and the output shaft, and constitutes a plurality of first gears for transmitting power from the prime mover to the drive wheels while shifting;
A first switching mechanism capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through the plurality of first gears;
A second speed change gear group that is disposed between the second input shaft and the output shaft and that constitutes a plurality of second speed stages for transmitting power from the prime mover to the drive wheels while changing speed.
A second switching mechanism capable of switching between a state where power can be transmitted and a state where power cannot be transmitted through the plurality of second gears;
The minimum transmission speeds of the plurality of first shift speeds and the plurality of second speed speeds are such that the rotation of the first input shaft is directly rotated via the one-way clutch. A control device for an automatic transmission configured to transmit to
First supply means for supplying hydraulic oil for operating the first clutch;
A hydraulic pressure release means arranged between the first clutch and the first supply means, and configured to release the hydraulic pressure of the hydraulic oil;
Detection means for detecting an operating state of the first supply means;
Oil pressure detecting means for detecting the oil pressure of the hydraulic oil in the oil pressure releasing means;
Control means for controlling the hydraulic pressure release means to release the hydraulic pressure when an abnormality of the first supply means is detected based on the detection result of the detection means;
Equipped with a,
The control means, when it is determined that there is no abnormality in the first supply means based on the detection result of the detection means, further determines the presence or absence of abnormality of the hydraulic pressure release means based on the detection result of the hydraulic pressure detection means,
Wherein, when said abnormality of the hydraulic release means based on a detection result of the pressure detecting means is detected, characterized that you control the first supply means to the first clutch disconnected state Control device. The hydraulic pressure release means is
A solenoid valve that inputs hydraulic oil of a predetermined hydraulic pressure, shuts off the hydraulic oil output in the set state, and outputs the hydraulic oil in the operational state;
By moving the valve body based on the operating state of the solenoid valve and the biasing force of the elastic member acting on the valve body, the input side oil passage, the output side first oil passage, and the output side second oil passage An oil passage switching valve for switching the communication state with any one of the oil passages,
By releasing the hydraulic pressure by moving the valve body based on the hydraulic pressure of the hydraulic oil input from the oil passage switching valve and the biasing force of the elastic member acting on the valve body, or releasing the hydraulic pressure A pressure release valve that switches to a sealed state,
The control device according to claim 1 , further comprising: The oil pressure detecting means is connected to the oil passage on the output side of the pressure release valve,
The pressure release valve shuts off the output of hydraulic oil to the output-side oil passage in the released state, and outputs the hydraulic oil input from the first oil passage to the output-side oil passage in the sealed state. And
The control apparatus according to claim 2 , wherein the hydraulic pressure detection unit detects a hydraulic pressure of the hydraulic oil in the sealed state. The control means controls the solenoid valve to the operating state when controlling to a released state for releasing the hydraulic pressure,
The oil path switching valve is configured to bring the input-side oil path and the output-side second oil path into communication with each other based on the hydraulic pressure of the hydraulic oil input from the solenoid valve.
The pressure release valve is in a release state in which the hydraulic pressure is released by moving the valve body based on the hydraulic pressure of hydraulic oil input from the second oil passage on the output side of the oil passage switching valve. control device according to claim 2 or 3, characterized in that. The control means controls the solenoid valve to the set state when controlling to a sealed state that does not release the hydraulic pressure,
The oil passage switching valve makes the input-side oil passage and the output-side first oil passage communicate with each other based on the biasing force of the elastic member acting on the valve body,
The pressure release valve moves the valve body based on hydraulic pressure of hydraulic oil and an urging force of the elastic member input via the first oil passage on the output side of the oil passage switching valve. the control device according to claim 2 or 3, characterized in that the sealing state of not releasing the hydraulic pressure.

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