JP2010121699A - Hydraulic circuit device for transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic circuit device for a transmission capable of securing proper line pressure for respective operations of a clutch and a transmission, while restraining an increase in a load of an oil pump. <P>SOLUTION: In this hydraulic circuit device 42 for the transmission, pressure of a hydraulic fluid supplied by the oil pump 50 is adjusted to the line pressure by a hydraulic pressure adjusting part 44, and then, is supplied to the transmission 2 and the clutches 6a and 6b via a line pressure supply oil passage 56. The supplied hydraulic fluid is used for selection operation of a shift stage in the transmission 2 and engaging-disengaging operation of the clutches 6a and 6b. An ECU 76 controls the hydraulic pressure adjusting part 44 so as to become line pressure higher than the line pressure of the hydraulic fluid used for the engaging-disengaging operation of the clutch 2 when performing the selection operation of the shift stage. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a transmission in which a selection operation of a gear stage in a transmission and an operation of a clutch for connecting and disconnecting power transmission to the transmission are performed by hydraulic oil supplied through a common oil passage. The present invention relates to a hydraulic circuit device.

Generally, in an automatic transmission or the like used for a vehicle, a clutch, a torque converter, or the like is provided between a power source and a transmission. In particular, in the case of large vehicles such as buses and trucks, since the power transmitted to the transmission is relatively large, a clutch may be used between the power source and the transmission.
Further, in recent years, two speed change mechanisms are provided in parallel to the power source, and a clutch is provided between the power source and each speed change mechanism, so that the speed change gear selection operation is previously performed by the speed change mechanism that is not used. So-called double clutch transmissions have been developed.

When a clutch is provided between the power source and the transmission and each of the transmission and the clutch is to be controlled using an actuator that is operated by hydraulic pressure, such as an automatic transmission, a predetermined value is assigned to each of the transmission and the clutch. It is necessary to supply hydraulic oil pressurized to the line pressure.
Thus, an automatic transmission apparatus in which a clutch is provided between a power source and a transmission and each of the transmission and the clutch is controlled by a hydraulic actuator is disclosed in Patent Document 1, for example.

The automatic transmission of Patent Document 1 is a double-clutch transmission, and is provided on a first clutch provided on an input shaft of a transmission mechanism that constitutes an odd-numbered shift stage and an input shaft of a transmission mechanism that constitutes an even-numbered speed stage. And a second clutch. In this automatic transmission, after the hydraulic oil supplied from the oil pump is regulated to a predetermined line pressure by the line pressure solenoid valve, a control valve for controlling the first and second clutches, and an actuator of the transmission mechanism Are respectively supplied to control valves for controlling. Further, the excess hydraulic oil in the line pressure solenoid valve is supplied as lubricating oil to the first and second clutches and various parts of the transmission.
JP 2007-263359 A

  When the line pressure of the hydraulic oil supplied to the clutch and the line pressure of the hydraulic oil supplied to the transmission mechanism are made common as in the automatic transmission device of Patent Document 1, the responsiveness at the time of the shift speed selection operation If the line pressure is always set to be relatively high in order to improve the load, the load of the oil pump that supplies hydraulic oil increases, the load of the drive source that drives the oil pump increases, and the drive source is the engine. In such a case, there arises a problem that fuel consumption deteriorates.

  On the other hand, if the hydraulic oil line pressure is always set to be relatively low in order to solve such a problem, there arises a problem that the responsiveness at the time of shift speed change in the transmission mechanism is lowered. In addition, when the hydraulic oil line pressure is set to a low value in this way, in the actuator used for the gear selection operation in the transmission mechanism, this actuator is used to ensure the driving force required for the gear selection operation. There is also a problem of increasing the size.

  In particular, in the double clutch type automatic transmission such as the automatic transmission of Patent Document 1, the hydraulic oil is supplied to the actuator corresponding to the gear selected in the transmission mechanism in use and is not used. It is necessary to supply hydraulic oil also to an actuator corresponding to a gear selected in advance in the transmission mechanism. For this reason, there is a problem that the response of the clutch is lowered when the line pressure of the hydraulic fluid generated due to the selection of the two shift speeds is large and the line pressure is excessively lowered.

  The present invention has been made in view of such a problem, and an object of the present invention is to secure an appropriate line pressure for each operation of the clutch and the transmission while suppressing an increase in the load of the oil pump. An object of the present invention is to provide a hydraulic circuit device for a transmission capable of being made.

  In order to achieve the above object, a hydraulic circuit device for a transmission according to the present invention includes an oil pump that supplies hydraulic oil stored in an oil storage member, and adjusts the pressure of the hydraulic oil supplied by the oil pump to a line pressure. A hydraulic pressure adjusting means that pressurizes, a transmission that has a plurality of shift speeds, and that performs a selection operation of the shift speed using hydraulic oil supplied from the hydraulic pressure adjusting means via a line pressure supply oil path; and the hydraulic pressure adjustment The hydraulic fluid supplied from the means through the line pressure supply oil passage is connected and disconnected to transmit power to the transmission when in the connected state, and to the transmission when in the disconnected state. When performing a selection operation of a clutch that cuts off the transmission of power and a shift stage of the transmission, the hydraulic pressure is set so that the line pressure is higher than the line pressure of the hydraulic oil used for connecting and disconnecting the clutch. Control adjustment means Characterized in that it comprises a that control means (claim 1).

  According to the transmission hydraulic circuit device configured as described above, the hydraulic oil supplied by the oil pump is adjusted to the line pressure by the hydraulic pressure adjusting means, and then the hydraulic oil is supplied via the line pressure supply oil passage. Supplied to the transmission and the clutch. The hydraulic oil thus supplied to the transmission is used when performing a shift speed selection operation, and the hydraulic oil supplied to the clutch is used for connecting / disconnecting the clutch. The control means controls the hydraulic pressure adjusting means so that the line pressure is higher than the line pressure of the hydraulic oil used for the clutch engagement / disengagement operation when selecting the gear position of the transmission.

  Therefore, the selection operation of the gear position of the transmission is performed under a line pressure higher than the line pressure of the hydraulic oil used for connecting / disconnecting the clutch. As a result, high responsiveness can be ensured in the gear selection operation in the transmission. Even if the hydraulic oil is used for the gear selection operation, the line pressure of the hydraulic fluid may decrease, so the line pressure increases during the gear selection operation. It is possible to prevent the line pressure of the hydraulic oil used for the contact operation from decreasing beyond an appropriate range.

  Further, in the transmission hydraulic circuit device, the hydraulic pressure adjusting means includes a relief valve that returns the hydraulic oil supplied from the oil pump to the upstream side from the oil pump when the valve is opened. A spool that is movable between a valve opening position and a valve closing position, a biasing spring that biases the spool in the valve closing direction, and a pressure of the hydraulic oil in the line pressure supply oil path provided in the spool. Is constantly applied to press the spool in the valve opening direction, and the first pressure receiving portion is provided to the spool and when the hydraulic oil pressure of the line pressure supply oil passage is applied. A second pressure receiving portion that presses the spool in the valve opening direction in addition to the pressure of the spool, and the control means switches the presence or absence of application of hydraulic oil to the second pressure receiving portion of the relief valve. And performing change of the line pressure (claim 2).

  According to the hydraulic circuit device for a transmission configured as described above, when the pressure of the hydraulic oil in the line pressure supply oil path is not applied to the second pressure receiving portion, the pressure of the hydraulic oil in the line pressure supply oil path is always maintained. The spool is pressed in the valve opening direction against the urging force of the urging spring only by the applied first pressure receiving portion. On the other hand, when the hydraulic pressure in the line pressure supply oil passage is applied to the second pressure receiving portion, the second pressure receiving portion in addition to the first pressure receiving portion opens the spool against the urging force of the urging spring. Press in the valve direction. For this reason, when the pressure of the hydraulic fluid in the line pressure supply oil passage is not applied to the second pressure receiving portion, the operation is performed in the case where the pressure of the hydraulic fluid in the line pressure supply oil passage is not applied to the second pressure receiving portion. The oil line pressure can be increased.

  Accordingly, with respect to the first pressure receiving portion, the pressure of the hydraulic oil has increased to the line pressure suitable for the gear selection operation in the transmission without applying the pressure of the hydraulic fluid in the line pressure supply oil passage to the second pressure receiving portion. Sometimes, the spool may be formed so as to overcome the urging force of the urging spring and move the spool to the valve opening position. In addition, the second pressure receiving portion is suitable for the operation of the clutch in a state where the first pressure receiving portion is formed in this manner and the pressure of the hydraulic oil in the line pressure supply oil passage is applied to the second pressure receiving portion. What is necessary is just to form so that when the pressure of the hydraulic oil rises to the line pressure, the spool moves to the valve open position by overcoming the biasing force of the biasing spring.

According to the hydraulic circuit device for a transmission according to the present invention, hydraulic fluid having a line pressure higher than that of the hydraulic fluid used for connecting / disconnecting the clutch is used when selecting the shift stage of the transmission. Therefore, high responsiveness can be ensured for the operation of selecting a gear position in the transmission.
In addition, even if the hydraulic oil is used in the gear selection operation, the line pressure of the hydraulic fluid may be reduced, the operation used for connecting / disconnecting the clutch during the gear selection operation. Since the line pressure is higher than the line pressure of the oil, it is possible to prevent the line pressure of the hydraulic oil used for the clutch connecting / disconnecting operation from decreasing beyond an appropriate range.

  In addition, the hydraulic oil line pressure is not always set to be high, but is increased when the transmission gear stage is selected, so that the hydraulic oil line pressure is always set to high. In comparison, the load of the oil pump and the load of the drive source that drives the oil pump can be reduced. Therefore, for example, when an engine is used as the drive source of the oil pump, the fuel consumption of the engine can be improved.

In addition, since the line pressure is higher than the line pressure of the hydraulic oil used for the clutch connection / disconnection operation during the gear selection operation, hydraulic oil having the same line pressure as the hydraulic oil used for the clutch connection / disconnection operation is used. Compared with the case of using, it is possible to reduce the size of an actuator used for a shift speed selection operation in the transmission.
According to the hydraulic circuit device for a transmission of claim 2, the hydraulic fluid used for the clutch connecting / disconnecting operation by applying the hydraulic pressure of the line pressure supply oil passage to the second pressure receiving portion. The line pressure can be obtained. On the other hand, by selecting a state in which the pressure of the hydraulic oil in the line pressure supply oil passage is not applied to the second pressure receiving portion, the transmission gear stage selection that is higher than the hydraulic oil line pressure used for the clutch connection / disconnection operation The line pressure of the hydraulic oil used when performing the operation can be obtained.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a skeleton diagram showing an overall configuration of a transmission 1 to which a hydraulic circuit device according to an embodiment of the present invention is applied. The transmission 1 is mounted on a vehicle and is configured as a double clutch type automatic transmission. As shown in FIG. 1, the transmission 1 includes a transmission 2 and a clutch 6 for transmitting and interrupting power from the engine 4 that is a power source of the vehicle to the transmission 2.

  The clutch 6 includes two wet clutches, a first clutch 6a and a second clutch 6b. The input sides of the first clutch 6 a and the second clutch 6 b are connected to the output shaft of the engine 4 through a common clutch input shaft 8. The output side of the first clutch 6 a is connected to the first input shaft 10 of the transmission 2, while the output side of the second clutch 6 b is connected to the second input shaft 12 of the transmission 2. The first input shaft 10 is coaxially disposed outside the second input shaft 12, and the first input shaft 10 and the second input shaft 12 are rotatable independently of each other.

  In addition, the first clutch 6a and the second clutch 6b are connected and disconnected independently by a clutch actuator (not shown) that operates by receiving supply of hydraulic oil adjusted to a line pressure, which will be described later. It has come to be. Further, the clutch facings of the first clutch 6a and the second clutch 6b are cooled by hydraulic oil supplied for cooling, which will be described later.

The first input shaft 10 includes a reverse drive gear 14a, a first speed drive gear 16a, a fifth speed drive gear 18a, and a third speed drive gear 20a in order from the first clutch 6a side. On the other hand, it is arranged to be relatively rotatable.
A reverse idler gear 14b that always meshes with the reverse drive gear 14a is fixed to an idler shaft 22 that is disposed in parallel with the first input shaft 10 and the second input shaft 12. The reverse idler gear 14b is always meshed with a reverse driven gear 14c fixed to a counter shaft 24 disposed in parallel with the first input shaft 10 and the second input shaft 12.

  Further, the counter shaft 24 has a first speed driven gear 16b that always meshes with the first speed drive gear 16a, a fifth speed driven gear 18b that always meshes with the fifth speed drive gear 18a, and a third speed gear that always meshes with the third speed drive gear 20a. The fast driven gear 20b is fixed. The three pairs of drive gears 16a, 18a and 20a and the driven gears 16b, 18b and 20b constitute a first gear mechanism 26.

  On the other hand, on the second input shaft 12, the fourth speed drive gear 28a, the second speed drive gear 30a, and the sixth speed drive gear 32a are relative to the second input shaft 12 in this order from the second clutch 6b side. It is rotatably arranged. The counter shaft 24 has a fourth speed driven gear 28b that always meshes with the fourth speed drive gear 28a, a second speed driven gear 30b that always meshes with the second speed drive gear 30a, and a sixth speed that always meshes with the sixth speed drive gear 32a. The driven gear 32b is fixed. The three pairs of drive gears 28a, 30a, 32a and the driven gears 28b, 30b, 32b constitute a second gear mechanism 34.

  A counter gear 36 is fixed to the end of the counter shaft 24 on the sixth speed driven gear 32b side. The counter gear 36 is always meshed with an output gear 40 fixed to the output shaft 38 of the transmission 2, whereby the driving force of the counter shaft 24 is transmitted to the output shaft 38. The driving force output from the output shaft 38 is transmitted to driving wheels (not shown) so that the vehicle travels.

  In the first gear mechanism 26, a first synchronizer S1 that rotates integrally with the first input shaft 10 is disposed between the reverse drive gear 14a and the first speed drive gear 16a. The first synchronizer S1 selectively selects any one of the state where the reverse gear is selected, the state where the first gear is selected, and the state where neither the reverse gear or the first gear is selected. It can be switched. Such selection of the gear position by the first synchronizer S1 is also employed in a conventional transmission, and therefore, detailed description thereof is omitted here.

  When the reverse gear is selected, the reverse drive gear 14a is connected to the first input shaft 10 by the first synchronizer S1. In this case, when the first clutch 6a is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the first input shaft 10 via the first clutch 6a, the drive transmitted to the first input shaft 10 is transmitted. The force is transmitted from the reverse drive gear 14a to the reverse driven gear 14c via the reverse idler gear 14b. The driving force transmitted to the reverse driven gear 14 c is further transmitted from the counter gear 36 through the output gear 40 to the output shaft 38, and thus the vehicle is moved backward by the driving force transmitted to the output shaft 38.

  On the other hand, when the first gear is selected, the first speed drive gear 16a is connected to the first input shaft 10 by the first synchronizer S1. In this case, when the first clutch 6a is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the first input shaft 10 via the first clutch 6a, the drive transmitted to the first input shaft 10 is transmitted. The force is transmitted from the first speed drive gear 16a to the first speed driven gear 16b. The driving force transmitted to the first speed driven gear 16b is further transmitted from the counter gear 36 through the output gear 40 to the output shaft 38, and thus the vehicle advances by the driving force transmitted to the output shaft 38.

Note that, when neither the reverse gear stage nor the first speed gear stage is selected, neither the reverse drive gear 14a nor the first speed drive gear 16a is connected to the first input shaft 10.
In the first gear mechanism 26, a second synchronizer S2 that rotates integrally with the first input shaft 10 is disposed between the fifth speed drive gear 18a and the third speed drive gear 20a. Any of the state in which the fifth gear is selected by the second synchronizer S2, the state in which the third gear is selected, and the state in which neither the fifth gear nor the third gear is selected. Can be selectively switched. Since the selection of the gear position by the second synchronizer S2 is also adopted in the conventional transmission, detailed description thereof is omitted here.

  When the fifth speed is selected, the fifth speed drive gear 18a is connected to the first input shaft 10 by the second synchronizer S2. In this case, when the first clutch 6a is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the first input shaft 10 via the first clutch 6a, the drive transmitted to the first input shaft 10 is transmitted. The force is transmitted from the fifth speed drive gear 18a to the fifth speed driven gear 18b. The driving force transmitted to the fifth speed driven gear 18b is further transmitted from the counter gear 36 to the output shaft 38 via the output gear 40, and thus the vehicle advances by the driving force transmitted to the output shaft 38.

  On the other hand, when the 3rd speed gear stage is selected, the 3rd speed drive gear 20a is connected with the 1st input shaft 10 by 2nd synchronizer S2. In this case, when the first clutch 6a is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the first input shaft 10 via the first clutch 6a, the drive transmitted to the first input shaft 10 is transmitted. The force is transmitted from the third speed drive gear 20a to the third speed driven gear 20b. The driving force transmitted to the third speed driven gear 20b is further transmitted from the counter gear 36 to the output shaft 38 via the output gear 40, and thus the vehicle advances by the driving force transmitted to the output shaft 38.

When neither the fifth speed gear stage nor the third speed gear stage is selected, neither the fifth speed drive gear 18a nor the third speed drive gear 20a is connected to the first input shaft 10.
In the second gear mechanism 34, a third synchronizer S3 that rotates integrally with the second input shaft 12 is disposed between the fourth speed drive gear 28a and the second speed drive gear 30a. Any of the state in which the fourth gear is selected by the third synchronizer S3, the state in which the second gear is selected, and the state in which neither the fourth gear nor the second gear is selected. Can be selectively switched. Since the selection of the gear position by the third synchronizer S3 is also adopted in the conventional transmission, detailed description thereof is omitted here.

  When the fourth speed is selected, the fourth speed drive gear 28a is connected to the second input shaft 12 by the third synchronizer S3. In this case, when the second clutch 6b is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the second input shaft 12 via the second clutch 6b, the drive transmitted to the second input shaft 12 is transmitted. The force is transmitted from the fourth speed drive gear 28a to the fourth speed driven gear 28b. The driving force transmitted to the fourth speed driven gear 28 b is further transmitted from the counter gear 36 to the output shaft 38 via the output gear 40, and thus the vehicle advances by the driving force transmitted to the output shaft 38.

  On the other hand, when the 2nd speed gear stage is selected, the 2nd speed drive gear 30a is connected with the 2nd input shaft 12 by 3rd synchronizer S3. In this case, when the second clutch 6b is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the second input shaft 12 via the second clutch 6b, the drive transmitted to the second input shaft 12 is transmitted. The force is transmitted from the second speed drive gear 30a to the second speed driven gear 30b. The driving force transmitted to the second speed driven gear 30b is further transmitted from the counter gear 36 through the output gear 40 to the output shaft 38, and thus the vehicle advances by the driving force transmitted to the output shaft 38.

  In the second gear mechanism 34, a fourth synchronizer S4 that rotates integrally with the second input shaft 12 is disposed between the second speed drive gear 30a and the sixth speed drive gear 32a. The fourth synchronizer S4 can selectively switch between the state in which the sixth speed gear stage is selected and the state in which the sixth speed gear stage is not selected. Since the selection of the gear position by the fourth synchronizer S4 is also employed in the conventional transmission, detailed description thereof is omitted here.

  When the sixth speed is selected, the sixth speed drive gear 32a is connected to the second input shaft 12 by the fourth synchronizer S4. In this case, when the second clutch 6b is connected and the driving force of the engine 4 is transmitted from the clutch input shaft 8 to the second input shaft 12 via the second clutch 6b, the drive transmitted to the second input shaft 12 is transmitted. The force is transmitted from the sixth speed drive gear 32a to the sixth speed driven gear 32b. The driving force transmitted to the sixth speed driven gear 32 b is further transmitted from the counter gear 36 through the output gear 40 to the output shaft 38, and thus the vehicle advances by the driving force transmitted to the output shaft 38.

  In this way, in the first gear mechanism 26 and the second gear mechanism 34, the gears are selected by the synchronization devices S1, S2, S3, S4. As described above, the driving force of the engine 4 is transmitted to the first gear mechanism 26 via the first clutch 6a, and the driving force of the engine 4 is transmitted to the second gear mechanism 34 via the second clutch 6b. Therefore, for example, when the first clutch 6a is in the connected state and the second clutch 6b is in the disconnected state, the driving force is applied to the output shaft 38 via any of the gears selected by the first gear mechanism 26. It is possible to select one of the gear positions with the second gear mechanism 34 while outputting. Further, by setting the first clutch 6a to the disconnected state and the second clutch 6b to the connected state, the driving force is output to the output shaft 38 via any one of the gears selected by the second gear mechanism 34. However, it is possible to select any one of the gear positions with the first gear mechanism 26.

  Therefore, when the gear position is switched, the next predicted gear shift in the gear mechanism to which the driving force of the engine 4 is not transmitted at that time out of the first gear mechanism 26 and the second gear mechanism 34. Select the gear in advance and connect the one in the disconnected state while disconnecting the one in the connected state of the first clutch 6a and the second clutch 6b when there is a request to change the gear position. Accordingly, it is possible to continuously output the driving force from the output shaft 32 even when the gear position is switched. As a result, it is possible to improve the driving feeling at the time of shift speed switching.

  The operation of the first clutch 6a and the second clutch 6b in the clutch 6 and the selection of the gear position in the first gear mechanism 26 and the second gear mechanism 34 are performed using hydraulic oil pressurized to the line pressure. Is called. That is, as described above, each of the first clutch 6a and the second clutch 6b is provided with a clutch actuator, and the first clutch 6a and the second clutch 6b are adjusted by adjusting the supply of hydraulic oil to the clutch actuator. Are independently connected, disconnected, and half-clutch. The first gear mechanism 26 and the second gear mechanism 34 are provided with speed change actuators for the synchronization devices S1, S2, S3, and S4, respectively, and the supply of hydraulic oil to the clutch actuator is adjusted. Thus, the gear stage is selected by driving the synchronizer corresponding to the gear stage to be selected.

In addition to supplying hydraulic oil adjusted to an appropriate line pressure to these actuators, the transmission device 1 uses the hydraulic oil to provide a first clutch 6a and a second clutch 6b that are wet clutches. A hydraulic circuit device is provided for cooling the clutch facing and lubricating various parts in the transmission 1.
FIG. 2 is an overall configuration diagram of the hydraulic circuit device 42 provided in the transmission 1. The hydraulic circuit device 42 receives a hydraulic pressure adjusting unit (hydraulic pressure adjusting means) 44 for adjusting the pressure of the hydraulic oil to a predetermined line pressure, and a part of the hydraulic oil supplied from the hydraulic pressure adjusting unit 44, and receives the received operation. And a temperature adjusting unit 46 that adjusts the temperature of the oil. The hydraulic oil whose temperature is adjusted by the temperature adjusting unit 46 is supplied to a cooling lubrication mechanism 48 for cooling the clutch facings of the first clutch 6a and the second clutch 6b and for lubricating parts in the transmission 1. .

  The hydraulic pressure adjustment unit 44 includes an oil pump 50 that is driven by the engine 4. The oil pump 50 takes in hydraulic oil from an oil pan (oil storage member) 54 via an oil filter 52 and supplies the hydraulic oil to a line pressure supply oil path 56. The line pressure supply oil passage 56 is provided with an accumulator 58 for accumulating the pressure of the hydraulic oil that rises as the hydraulic oil is supplied from the oil pump 50.

In order to adjust the pressure of the hydraulic oil in the line pressure supply oil passage 56 supplied from the oil pump 50 to a predetermined line pressure in cooperation with the accumulator 58, the hydraulic pressure adjustment unit 44 is provided with a relief valve 60. Yes.
The relief valve 60 is a spool valve, and has a spool 64 that slides in a cylindrical valve body 62. The spool 64 receives a biasing force of a biasing spring 66 provided in the valve body 62, and is biased toward the extending direction of the biasing spring 66, that is, rightward in FIG.

  The spool 64 is formed with a first land 64a provided on the urging spring 66 side and a second land (first pressure receiving portion) 64b having the same diameter as the first land 64a. An annular oil groove 68 is formed between the land 64a and the second land 64b. The second land 64b is integrally provided with a third land (second pressure receiving portion) 64c on the same axis as the second land 64b in a direction opposite to the first land 64a. The diameter of the third land 64c is smaller than the diameter of the second land 64b. Correspondingly, the valve body 62 of the relief valve 60 also slides inside the third land 64c on the third land 64c side. The diameter is reduced stepwise.

  A stopper 64 d is provided at the end of the spool 64 on the third land 64 c side so as to project in the axial direction of the spool 64, and the stopper 64 d is supported by the urging force of the urging spring 66. Even when the spool 64 moves until it comes into contact with the second land 64b, an annular first oil chamber 70 is formed between the second land 64b and the valve body 62, as shown in FIG. 2, and the third land 64c. An annular second oil chamber 72 is formed between the valve body 62 and the valve body 62.

As shown in FIG. 2, the first oil chamber 70 is connected to a line pressure supply oil passage 56, and hydraulic oil discharged from the oil pump 50 is always supplied. The second oil chamber 72 is connected to a line pressure supply oil passage 56 via a line pressure control valve 74 as shown in FIG.
The line pressure control valve 74 communicates the second oil chamber 72 and the line pressure supply oil passage 56 to supply the hydraulic oil discharged from the oil pump 50 into the second oil chamber 72, and a second position. This is an electromagnetic valve that can be selectively switched to either the second position for discharging the hydraulic oil in the oil chamber 72 to the oil pan 54.

  Therefore, when the line pressure control valve 74 is in the first position, the hydraulic oil supplied by the oil pump 50 and increased in pressure is supplied to both the first oil chamber 70 and the second oil chamber 72. As a result, the second land 64 b and the third land 64 c receive the pressure of the hydraulic oil and are pressed against the urging force of the urging spring 66. When the pressing force of the hydraulic oil acting on the second land 64b and the third land 64c exceeds the urging force of the urging spring 66, the spool 64 moves to the left in FIG. FIG. 3 shows the state of the relief valve 60 and the line pressure control valve 74 in such a state.

  As shown in FIG. 3, the annular oil groove 68 formed in the spool 64 is in a state where the spool 64 is moved to the left in FIGS. 2 and 3 by the pressure of the hydraulic oil as described above. The line pressure supply oil passage 56 and the hydraulic oil passage on the upstream side of the oil pump 50 are communicated with each other. That is, at this time, the relief valve 60 is opened, and the hydraulic oil in the line pressure supply oil passage 56 is returned to the upstream side of the oil pump 50 through the annular oil groove 68. Hereinafter, when the spool 64 is in such a position, the spool 64 is in the valve open position.

  On the other hand, as shown in FIG. 2, when the stopper 64 d of the spool 64 is in contact with the valve body 62 by the biasing force of the biasing spring 66, the upstream side of the line pressure supply oil passage 56 and the oil pump 50. The communication with the hydraulic oil flow path is blocked by the first land 64a. That is, at this time, the relief valve 60 is closed, and the hydraulic oil in the line pressure supply oil passage 56 is not returned to the upstream side of the oil pump 50. Hereinafter, when the spool 64 is in such a position, the spool 64 is in the valve closing position.

  When the line pressure control valve 74 is in the second position, the supply of hydraulic oil from the line pressure supply oil passage 56 to the second oil chamber 72 is shut off, and the hydraulic oil in the second oil chamber 72 is controlled by the line pressure control. Since the oil is discharged to the oil pan 54 via the valve 74, the pressure of the hydraulic oil supplied from the line pressure supply oil passage 56 does not act on the third land 64c. Accordingly, only the second land 64b is pressed against the urging force of the urging spring 66 by the pressure of the hydraulic oil. When the pressing force of the hydraulic oil acting on the second land 64b exceeds the urging force of the urging spring 66, the spool 64 moves to the valve opening position. For this reason, in order to move the spool 64 to the valve opening position as compared with the case where the line pressure control valve 74 is in the first position and hydraulic oil is also supplied to the second oil chamber 72 from the line pressure supply oil passage 56. Requires higher hydraulic oil pressure. FIG. 4 shows a state where the spool 64 is moved to the valve open position by the pressure of the hydraulic oil when the line pressure control valve 74 is in the second position.

  Regardless of whether the line pressure control valve 74 is in the first position or the second position, the pressure of the hydraulic oil acting on the spool 64 is increased by the pressure of the hydraulic oil in the line pressure supply oil passage 56, and the urging spring When the urging force of 66 is exceeded, the spool 64 moves from the valve closing position to the valve opening position. When the spool 64 moves to the valve open position in this manner, the hydraulic oil in the line pressure supply oil passage 56 is returned to the upstream side of the oil pump 50, so the pressure of the hydraulic oil in the line pressure supply oil passage 56 decreases. When the hydraulic oil pressure decreases to some extent, the spool 64 returns to the valve closing position again by the biasing force of the biasing spring 66. Therefore, the line pressure of the hydraulic oil in the line pressure supply oil passage 56 is maintained at a predetermined pressure.

  As described above, when the line pressure control valve 74 is in the second position, the hydraulic oil pressure in the line pressure supply oil passage 56 does not increase compared to when the line pressure control valve 74 is in the first position. The spool 64 does not move to the valve open position against the biasing force of the biasing spring 66. For this reason, the hydraulic oil in the line pressure supply oil passage 56 is adjusted to a higher line pressure when the line pressure control valve 74 is in the second position than when the line pressure control valve 74 is in the first position.

  Here, in the present embodiment, the line pressure of the hydraulic oil obtained when the line pressure control valve 74 is in the first position is connected / disconnected including the half clutch state of the first clutch 6a and the second clutch 6b. The pressure receiving areas of the second lands 64b and the third lands 64c and the urging force of the urging spring 66 are set so that the first reference value (for example, 0.8 MPa), which is as low as possible when performing appropriately. Associated and set.

Further, the hydraulic oil line pressure obtained when the line pressure control valve 74 is in the second position is larger than the first reference value in order to ensure sufficient responsiveness when selecting the gear position in the transmission 2. The pressure receiving area of the second land 64b and the urging force of the urging spring 66 are set in association with each other so that the second reference value (for example, 1.6 MPa) is higher.
That is, the pressure receiving area of the second land 64b is set to the line pressure of the second reference value in a state where the line pressure control valve 74 is set to the second position and the hydraulic oil in the line pressure supply oil passage 56 is not supplied to the second oil chamber 72. What is necessary is just to set so that when the hydraulic oil pressure rises, the spool 64 moves to the valve open position by overcoming the biasing force of the biasing spring 66. The pressure receiving area of the third land 64c is set as described above, and the line pressure control valve 74 is set to the first position to set the pressure receiving area of the second land 64b to the second oil chamber 72. When the hydraulic oil pressure is increased to the first reference line pressure with the hydraulic oil supplied, the spool 64 moves to the valve open position by overcoming the biasing force of the biasing spring 66. Good.

  The hydraulic circuit device 42 controls the line pressure control valve 74 to select the line pressure of the hydraulic oil when selecting a shift speed in the transmission 2 or deselecting the selected shift speed, that is, when selecting a shift speed. An ECU (control means) 76 is provided to properly adjust the control. That is, the ECU 76 executes line pressure control for properly adjusting the line pressure, thereby controlling the line pressure control valve 74 to set the hydraulic oil line pressure to either the first reference value or the second reference value. Switch to.

FIG. 5 is a flowchart of line pressure control executed by the ECU 76. The ECU 76 repeatedly executes the line pressure control at a predetermined control period according to the flowchart of FIG.
When the line pressure control is started, the ECU 76 determines whether or not the value of the flag F1 is 0 in step S1. The flag F1 is used to indicate whether or not an instruction for selecting a gear position in the transmission 2 or an instruction for canceling selection of a gear stage being selected, that is, whether or not a gear shift instruction has been issued, and the value of the flag F1 is 1 Indicates that a gear shift instruction has been issued. The initial value of the flag F1 is 0. Here, it is determined that the value of the flag F1 is 0, and the ECU 76 advances the process to step S2.

  In step S2, the ECU 76 determines whether or not a shift instruction has been issued. The ECU 76 monitors the signal of the speed change actuator in the transmission 2 and determines whether or not a speed change instruction has been issued based on the signal of the speed change actuator. First, if it is determined in step S2 that a gear change instruction has not been issued, the ECU 76 advances the process to step S7, sets the line pressure control valve 74 as the first position, and ends the control cycle.

  Also in the next control cycle, the ECU 76 starts the process from step S1 and determines whether or not the value of the flag F1 is zero. Since the value of the flag F1 is still 0, the ECU 76 advances the process from step S1 to step S2, and determines again whether or not a shift instruction has been issued. If no shift instruction has been issued, the ECU 76 advances the process to step S7 and sets the line pressure control valve 74 to the first position. Therefore, the ECU 76 holds the line pressure control valve 74 in the first position unless a gear change instruction is issued.

  When the line pressure control valve 74 is set to the first position, as shown in FIG. 3, the hydraulic oil in the line pressure supply oil passage 56 passes through the line pressure control valve 74 and the second oil chamber 72 of the relief valve 60. To be supplied. Therefore, as described above, when the line pressure of the hydraulic oil in the line pressure supply oil passage 56 increases to the first reference value, the spool 64 of the relief valve 60 moves to the valve open position as shown in FIG. The hydraulic oil in the line pressure supply oil passage 56 is returned to the upstream side of the oil pump 50 through the relief valve 60. Accordingly, when the line pressure of the hydraulic oil in the line pressure supply oil passage 56 decreases, the spool 64 of the relief valve 60 moves to the valve closing position, and the hydraulic oil in the line pressure supply oil passage 56 becomes oil. The pump 50 is not returned to the upstream side. Accordingly, the hydraulic oil line pressure in the line pressure supply oil passage 56 is substantially maintained at the first reference value.

On the other hand, when a transmission instruction is issued in the transmission 2, the ECU 76 proceeds to step S3 based on the determination in step S2, sets the value of the flag F1 to 1, and further sets the line pressure control valve 74 to the second position in step S4. .
Next, in step S5, the ECU 76 determines whether or not the instructed shift speed selection or deselection of the selected shift speed, that is, the shift speed selection operation has been completed based on the signal of the shift actuator in the transmission 2. judge. Here, since it is not long after the gear shift instruction is given, if the gear selection operation has not been completed, the ECU 76 determines that the gear selection operation has not been completed in step S5, thereby setting the control cycle. finish.

  In step S1 of the next control cycle, the ECU 76 again determines whether or not the value of the flag F1 is 0. At this time, since the value of the flag F1 is changed to 1, the ECU 76 starts the process from step S1. Proceeding to step S4, the line pressure control valve 74 is set to the second position. In step S5, the ECU 76 determines whether or not the gear selection operation has been completed. If the gear selection operation has not yet been completed, the control cycle ends. Therefore, once a gear shift instruction is issued, the line pressure control valve 74 is held at the second position unless the instructed shift speed selection operation is completed.

  When the line pressure control valve 74 is set to the second position, as shown in FIG. 4, the hydraulic oil in the line pressure supply oil passage 56 is not supplied to the second oil chamber 72, The hydraulic oil is discharged to the oil pan 54. Therefore, as described above, the spool 64 of the relief valve 60 does not move to the valve open position until the line pressure of the hydraulic oil in the line pressure supply oil passage 56 rises to the second reference value. When the line pressure of the hydraulic oil rises to the second reference value, the spool 64 of the relief valve 60 moves to the valve open position as shown in FIG. 4, and the hydraulic oil in the line pressure supply oil passage 56 is transferred to the oil pump 50. Returned to the upstream side. Accordingly, when the line pressure of the hydraulic oil in the line pressure supply oil passage 56 decreases, the spool 64 of the relief valve 60 moves to the valve closing position, and the hydraulic oil in the line pressure supply oil passage 56 becomes oil. The pump 50 is not returned to the upstream side. Accordingly, the hydraulic oil line pressure in the line pressure supply oil passage 56 is substantially maintained at the second reference value higher than the first reference value.

After the gear shift instruction is given, when the gear selection operation corresponding to the gear shift instruction is completed, the ECU 76 determines in step S5 that the gear selection operation has been completed, proceeds to step S6, and sets the value of the flag F1. Reset to zero. Further, the ECU 76 sets the line pressure control valve 74 to the first position in the next step S7, and ends the control cycle.
Also in the next control cycle, the ECU 76 starts processing from step S1 and determines whether or not the value of the flag F1 is zero. Since the value of the flag F1 has been reset to 0, the ECU 76 advances the process from step S1 to step S2, and determines whether or not a shift instruction has been issued. If no shift instruction has been issued, the ECU 76 advances the process to step S7 and sets the line pressure control valve 74 to the first position. Accordingly, the ECU 76 keeps the line pressure control valve 74 in the first position unless a gear change instruction is issued again. As a result, as described above, the line pressure of the hydraulic oil in the line pressure supply oil passage 56 is substantially maintained at the first reference value lower than the second reference value.

  When the ECU 76 performs the line pressure control as described above, the line pressure of the hydraulic oil is limited only when the speed change operation such as the selection of the speed change stage or the selection release of the speed change stage being selected is performed in the transmission 2. Is maintained at a second reference value higher than the first reference value. Accordingly, when such a shift speed selection operation is performed in the transmission 2, the operation pressure having the relatively high second reference value of the line pressure is used. High responsiveness can be ensured in operation.

  Further, in this way, at the time of selecting the gear position, the line pressure of the second reference value is higher than the line pressure of the first reference value used for connecting / disconnecting the first clutch 6a or the second clutch 6b. Therefore, even when the hydraulic oil is used for the shift stage selection operation, the hydraulic oil line pressure may decrease, the hydraulic oil used for the connection / disconnection operation of the first clutch 6a or the second clutch 6b. It is possible to prevent the line pressure from falling beyond an appropriate range.

  In particular, in this embodiment, since the transmission 1 is a double clutch type automatic transmission, the selection operation of the gear position is performed in each of the first transmission mechanism 26 and the second transmission mechanism 34. That is, of the first speed change mechanism 26 and the second speed change mechanism 34, the speed change mechanism that is not used while supplying the operating oil to the speed change actuator corresponding to the speed step currently selected in the speed change mechanism that is being used. It is necessary to supply hydraulic oil also to an actuator corresponding to a gear position selected in advance in the mechanism. For this reason, the variation in the line pressure of the hydraulic oil generated with the selection of the two shift speeds is large compared to the state where the shift speed is not selected in either of the two speed change mechanisms. When the line pressure of the hydraulic oil is excessively lowered, there is a possibility that the responsiveness of the clutches of the first clutch 6a and the second clutch 6b is lowered. Therefore, increasing the hydraulic oil line pressure during the gear selection operation in this way is extremely effective in eliminating the adverse effect on the hydraulic oil line pressure caused by the gear selection operation.

  Further, the line pressure of the hydraulic oil is not always set to be high, but is raised to the second reference value at the time of the gear selection operation in the transmission 2, so that the line pressure of the hydraulic oil is always set to Compared to the case where the value is set higher, the load on the oil pump 50 and the load on the engine 4 that drives the oil pump 50 can be reduced. Therefore, the fuel consumption of the engine 4 can also be improved.

Further, since the line pressure of the second reference value is higher than the line pressure of the first reference value used for the connection / disconnection operation of the first clutch 6a or the second clutch 6b during the gear selection operation, the first reference The speed change actuator of the transmission 2 can be reduced in size as compared with the case where hydraulic oil adjusted to the value line pressure is continuously used. Accordingly, the transmission 2 itself can be reduced in size.
By the way, as described above, part of the hydraulic oil supplied by the oil pump 50 is supplied to the temperature adjusting unit 46 via the cooling lubrication oil passage (cooling oil passage) 78 branched from the line pressure supply oil passage 56. Supplied. The hydraulic oil supplied to the temperature adjusting unit 46 is adjusted in temperature by the temperature adjusting unit 46, and then cooled for clutch facing of the first clutch 6 a and the second clutch 6 b and for lubrication of various parts in the transmission 1. The cooling lubrication mechanism 48 is supplied.

  Accordingly, the hydraulic oil before being used for the operation of selecting the gear position in the transmission 2 and the operation of the first clutch 6a and the second clutch 6b is the clutch facing of the first clutch 6a and the second clutch 6b, which are wet clutches. Since it is used for cooling, the clutch oil of the first clutch 6a and the second clutch 6b is effectively used by the hydraulic oil before the temperature rises due to the operation of the transmission 2, the first clutch 6a and the second clutch 6b. Can be cooled to.

The temperature adjusting unit 46 switches the supply state of the hydraulic oil to the supply start valve 80 and the oil cooler 82 for appropriately supplying the hydraulic oil to the cooling lubrication mechanism 48, and sets the temperature of the hydraulic oil within an appropriate range. And a flow path switching valve 84 for adjusting the flow rate.
If the supply of hydraulic oil to the cooling lubrication mechanism 48 is started immediately after the supply of the hydraulic oil by the oil pump 50 is started, the pressure of the hydraulic oil is temporarily decreased by the supply of the hydraulic oil to the cooling lubrication mechanism 48, or the pressure Since the rate of increase decreases, the hydraulic oil pressure cannot be quickly raised to the line pressure. Therefore, in the present embodiment, a supply start valve 80 is provided in the temperature adjustment unit 46.

The supply start valve 80 is a spool valve, and has a spool 88 that slides in a cylindrical valve body 86. The spool 88 receives a biasing force of a biasing spring 90 provided in the valve body 86, and is biased toward the extending direction of the biasing spring 90, that is, rightward in FIG.
The spool 88 is formed with a first land 88a provided on the biasing spring 90 side and a second land 88b having the same diameter as the first land 88a. The first land 88a and the second land 88a are formed on the spool 88. An annular oil groove 92 is formed between 88b and 88b.

  A stopper 88 c is provided at the end of the spool 88 on the second land 88 b side so as to project in the axial direction of the spool 88, and the stopper 88 c is urged by the urging force of the urging spring 90. Even when the spool 88 moves until it comes into contact with the valve body 86, an annular oil chamber 94 is formed between the second land 88b and the valve body 86, as shown in FIG.

  The oil chamber 94 is connected to a cooling lubrication oil passage 78 as shown in FIG. 2, and hydraulic oil discharged from the oil pump 50 is always supplied. Accordingly, the oil pump 50 starts supplying the hydraulic oil, and the pressure of the hydraulic oil supplied to the oil chamber 94 via the line pressure supply oil passage 56 and the cooling lubrication oil passage 78 rises. When the pressing force of the hydraulic oil acting on 88b exceeds the urging force of the urging spring 90, the spool 88 moves to the left in FIG. 6 and 7 show a state where the spool 88 has moved leftward in FIG. 2 due to the pressing force of the hydraulic oil acting on the second land 88b in this way.

  As shown in FIGS. 6 and 7, the annular oil groove 92 formed in the spool 88 is used for cooling and lubricating oil when the spool 88 is moved leftward in FIGS. 2, 6, and 7. The passage 78 and the passage switching valve 84 are communicated with each other. That is, at this time, the supply start valve 80 is opened, and the hydraulic oil in the cooling lubrication oil passage 78 is supplied to the flow passage switching valve 84 via the annular oil groove 92. Hereinafter, when the spool 88 is in such a position, the spool 88 is in the valve open position.

  On the other hand, as shown in FIG. 2, when the stopper 88 c of the spool 88 is in contact with the valve body 86 by the biasing force of the biasing spring 90, the cooling lubrication oil passage 78, the passage switching valve 84, Is blocked by the first land 88a. That is, the supply start valve 80 is closed, and the supply of hydraulic oil from the cooling lubrication oil passage 78 to the flow path switching valve 84 is not performed. Hereinafter, when the spool 88 is in such a position, the spool 88 is in the valve closing position.

  As described above, when the oil pump 50 starts supplying the hydraulic oil and the pressure of the hydraulic oil supplied to the oil chamber 94 increases, the pressing force of the hydraulic oil acting on the second land 88b is applied to the urging spring. When the urging force of 90 is exceeded, the spool 88 moves to the valve open position. Therefore, the spool 88 is in the valve close position only when the pressure of the hydraulic oil supplied from the oil pump 50 is not sufficiently increased. The hydraulic oil is not supplied from the cooling lubrication oil path 78 to the flow path switching valve 84. In the following description, it is assumed that the spool 88 is in the valve open position unless otherwise specified.

  Note that the pressing force of the hydraulic oil acting on the second land 88b in the spool 88 and the biasing force of the biasing spring 90 are before the pressure of the hydraulic oil supplied from the oil pump 50 reaches the line pressure of the first reference value. Further, the spool 88 is set to move to the valve opening position, and the pressure receiving area of the second land 88b and the biasing force of the biasing spring 90 are set to correspond to this.

The flow path switching valve 84 is a spool valve and has a spool 98 that slides in a cylindrical valve body 96. The spool 98 receives a biasing force of a biasing spring 100 provided in the valve body 96, and is biased toward the extending direction of the biasing spring 100, that is, to the left in FIG.
A first land 98a, a second land 98b, and a third land 98c are formed on the spool 98 from the side of the urging spring 100, and these all have the same diameter. An annular first oil groove 102 is formed between the first land 98a and the second land 98b, and an annular second oil groove 104 is formed between the second land 98b and the third land 98c. Has been.

  A stopper 98 d protrudes from the end of the spool 98 on the side of the third land 98 c toward the axial direction of the spool 98, and the stopper 98 d is urged by the urging force of the urging spring 100. Even when the spool 98 moves until it comes into contact with the annular oil chamber 106, the annular oil chamber 106 is formed between the third land 98 c and the valve body 96.

  The oil chamber 106 is connected to a cooling lubrication oil passage 78 via a temperature control valve 108 as shown in FIG. The temperature control valve 108 communicates the oil chamber 106 with the cooling lubrication oil passage 78, and has a first position for supplying hydraulic oil in the cooling lubrication oil passage 78 supplied from the oil pump 50 to the oil chamber 106. The electromagnetic wave that can be selectively switched to either the second position where the supply of the hydraulic oil from the cooling lubrication oil passage 78 to the oil chamber 106 is shut off and the hydraulic oil in the oil chamber 106 is discharged to the oil pan 54. It is a valve.

  Therefore, when the temperature control valve 108 is in the first position, the hydraulic oil supplied by the oil pump 50 and increased in pressure is supplied to the oil chamber 106, and the third land 98 c is used as the biasing force of the biasing spring 100. It will be pressed against. When the hydraulic oil pressing force acting on the third land 98c exceeds the urging force of the urging spring 100, the spool 98 moves to the right in FIG.

  The relationship between the pressing force of the hydraulic oil acting on the third land 98c and the urging force of the urging spring 100 is similar to the supply start valve 80 described above from the oil pump 50 to the cooling lubrication oil passage 78 and the temperature control valve 108. The spool 98 is set to move rightward in FIG. 2 before the pressure of the hydraulic oil in the oil chamber 106 supplied via the pressure reaches the line pressure of the first reference value. Thus, the pressure receiving area of the third land 98c and the urging force of the urging spring 100 are set.

  Therefore, except for immediately after the start of supply of hydraulic oil by the oil pump 50, when the pressure of the hydraulic oil is sufficiently increased, the hydraulic oil is supplied to the oil chamber 106 when the temperature control valve 108 is in the first position. Thus, the spool 98 is moved to the right in FIG. FIG. 6 shows the state of the flow path switching valve 84 when the temperature control valve 108 is in the first position and the spool 98 moves rightward in FIG. Hereinafter, when the spool 98 of the flow path switching valve 84 is in the position shown in FIG. 6, the spool 98 is in the first position.

  On the other hand, when the temperature control valve 108 is in the second position, the hydraulic oil is not supplied from the cooling lubrication oil passage 78 and the hydraulic oil in the oil chamber 106 is discharged to the oil pan 54. The spool 98 of the valve 84 returns to the left in FIG. 2 by the urging force of the urging spring 100, and the stopper 98 d is in contact with the axial end of the valve body 96. FIG. 7 shows the state of the flow path switching valve 84 when the temperature control valve 108 is in the second position and the spool 98 is in contact with the axial end of the valve body 96 as described above. Hereinafter, when the spool 98 of the flow path switching valve 84 is in the position as shown in FIG. 7, the spool 98 is in the second position.

  When the temperature control valve 108 is in the second position and the spool 98 is in the second position, as shown in FIG. 7, the hydraulic oil supplied from the cooling lubrication oil passage 78 via the supply start valve 80 is The cooling lubrication mechanism 48 is supplied via an annular second oil groove 104 formed in the spool 98. At this time, the first land 98a is interposed between the cooling lubrication oil passage 78 and the oil cooler 82 as shown in FIG. 7, so that the hydraulic oil is not supplied to the oil cooler 82. Yes. In addition, even if there is hydraulic oil that is about to flow out from the oil cooler 82, it is blocked by the second land 98b.

Accordingly, when the temperature control valve 108 is in the second position, the hydraulic oil is supplied to the cooling lubrication mechanism 48 without passing through the oil cooler 82, and the supplied hydraulic oil is supplied to the first clutch 6a and the second clutch. It is used for cooling the clutch facing of 6b and for lubricating the various parts in the transmission 1.
On the other hand, when the temperature control valve 108 is in the first position and the spool 98 is in the first position, the hydraulic oil is supplied from the cooling lubrication oil passage 78 to the cooling lubrication mechanism 48 via the supply start valve 80 as described above. As shown in FIG. 6, the supply is cut off by the third land 98c. At this time, the cooling lubrication oil passage 78 and the oil cooler 82 communicate with each other via an annular first oil groove 102 formed in the spool 98 as shown in FIG. The hydraulic oil inside is supplied to the oil cooler 82 via the first oil groove 102 without passing through the supply start valve 80. Further, the hydraulic oil cooled by the oil cooler 82 and flowing out from the oil cooler 82 is supplied to the cooling lubrication mechanism 48 via the second oil groove 104.

Therefore, when the temperature control valve 108 is in the first position, the hydraulic oil cooled by the oil cooler 82 is supplied to the cooling lubrication mechanism 48, cooling the clutch facings of the first clutch 6a and the second clutch 6b, and Used for lubrication of various parts in the transmission 1.
When the hydraulic oil is supplied to the oil cooler 82 without passing through the supply start valve 80 as described above, the spool 98 is driven by the pressure of the hydraulic oil supplied to the oil chamber 106 via the temperature control valve 108. Since it is in the state moved to the second position, the spool 98 returns to the first position when the pressure of the hydraulic oil decreases for some reason, such as when the operation of the oil pump 50 is stopped. For this reason, the supply of hydraulic oil to the oil cooler 82 performed without the supply start valve 80 is blocked by the first land 98a. At this time, since the supply start valve 80 is also closed due to a decrease in the pressure of the hydraulic oil, the hydraulic oil in the cooling lubrication oil passage 78 is not supplied to the cooling lubrication mechanism 48.

  Normally, at the beginning of the operation of the oil pump 50, the temperature of the operating oil has not yet risen, so that it is not necessary to supply the operating oil to the oil cooler 82 by oil temperature control described later. For this reason, as described above, the temperature control valve 108 is set to the second position, and the hydraulic oil is supplied to the cooling lubrication mechanism 48 via the supply start valve 80. When the supply start valve 80 is in the open state with the increase in the hydraulic oil, hydraulic oil starts to be supplied to the cooling lubrication mechanism 48.

  However, even if the temperature of the hydraulic oil has already risen sufficiently and the temperature control valve 108 is in the first position when the supply of hydraulic oil by the oil pump 50 is started, Similarly, the spool 98 of the flow path switching valve 84 does not move to the first position unless the pressure of the hydraulic oil supplied to the oil chamber 106 rises. Therefore, unless the pressure of the hydraulic oil rises sufficiently, the spool 98 is supplied to the cooling lubrication mechanism 48. The hydraulic oil will not be supplied.

  As described above, the temperature adjusting unit 46 switches the temperature control valve 108 between the first position and the second position, thereby supplying hydraulic oil to the cooling lubrication mechanism 48 via the oil cooler 82 and the oil cooler. It is possible to switch between supply of hydraulic oil to the cooling lubrication mechanism 48 that does not go through 82. Therefore, if the temperature control valve 108 is switched between the first position and the second position according to the temperature of the hydraulic oil, the temperature of the hydraulic oil supplied to the cooling lubrication mechanism 48 can be adjusted appropriately. Become.

  Therefore, as shown in FIG. 2, in the hydraulic circuit device 42, a temperature sensor (temperature detection means) 110 for detecting the temperature of the hydraulic oil is provided in the oil pump in order to appropriately adjust the temperature of the hydraulic oil by the temperature adjustment unit 46. 50 upstream. The ECU 76 executes oil temperature control for adjusting the temperature of the hydraulic oil by controlling the temperature control valve 108 based on the temperature of the hydraulic oil detected by the temperature sensor 110.

FIG. 8 is a flowchart of oil temperature control executed by the ECU 76. The ECU 76 repeatedly performs the oil temperature control at a predetermined control period according to the flowchart of FIG.
When the oil temperature control is started, the ECU 76 determines in step S11 whether or not at least one of the first clutch 6a and the second clutch 6b is in a half-clutch state. The ECU 76 monitors the signals of the clutch actuators provided in the first clutch 6a and the second clutch 6b, respectively, and determines the half-clutch state based on the signals from the clutch actuator.

  Here, if neither the first clutch 6a nor the second clutch 6b is in the half-clutch state, the ECU 76 proceeds with the process to step S12 based on the determination in step S11, and determines whether or not the value of the flag F2 is zero. To do. The flag F2 is used to indicate whether or not the temperature T of the hydraulic oil detected by the temperature sensor 110 is equal to or higher than a predetermined first temperature T1 (for example, 100 ° C.). The value of the flag F2 is set to 1 when the temperature becomes equal to or higher than the temperature T1. Since the initial value of the flag F2 is 0, the ECU 76 advances the process from step S12 to step S13, assuming that the value of the flag F2 is 0 here.

  In step S13, the ECU 76 determines whether or not the temperature T of the hydraulic oil detected by the temperature sensor 110 has become equal to or higher than the first temperature T1. Normally, since the temperature of the hydraulic oil has not increased so much at the beginning of the oil temperature control, it is determined here that the temperature T of the hydraulic oil is not equal to or higher than the first temperature T1, and the ECU 76 advances the process to step S18. In step S18, the ECU 76 sets the temperature control valve 108 to the second position and ends the control cycle.

  In the next control cycle, the ECU 76 starts the process again from step S11, and determines whether at least one of the first clutch 6a and the second clutch 6b is in a half-clutch state. Also at this time, if both the first clutch 6a and the second clutch 6b are not in the half-clutch state, the ECU 76 advances the process to step S12 based on the determination in step S11, and determines whether or not the value of the flag F2 is 0. Determine.

Since the value of the flag F2 is still 0, the ECU 76 advances the process from step S12 to step S13, and determines again whether the temperature T of the hydraulic oil has become equal to or higher than the first temperature T1. If the temperature T of the hydraulic oil is not still equal to or higher than the first temperature T1, the ECU 76 advances the process to step S18 and sets the temperature control valve 108 to the second position.
Therefore, if both the first clutch 6a and the second clutch 6b are not in the half-clutch state and the temperature T of the hydraulic oil is not equal to or higher than the first temperature T1, the temperature control valve 108 is held at the second position. become.

  When the temperature control valve 108 is in the second position, as shown in FIG. 7, the hydraulic oil in the cooling lubrication oil passage 78 is not supplied to the oil chamber 106 of the passage switching valve 84, and the spool 98 is energized. The spring 100 is in the second position by the urging force of the spring 100. Therefore, as described above, the hydraulic oil in the cooling lubrication oil passage 78 is not supplied to the oil cooler 82, but is supplied from the supply start valve 80 through the annular second oil groove 104 formed in the spool 98. The cooling lubrication mechanism 48 is supplied. The hydraulic oil thus supplied to the cooling / lubricating mechanism 48 is used for cooling the clutch facings of the first clutch 6a and the second clutch 6b and for lubricating parts of the transmission 1 at various points.

  By being used for cooling of the clutch facing and lubrication in the transmission 1, the temperature of the hydraulic oil gradually increases. If it is determined in step S13 of the oil temperature control that the temperature T of the hydraulic oil detected by the temperature sensor 110 has become equal to or higher than the first temperature T1, the ECU 76 advances the process to step S14 and sets the value of the flag F2 to 1. To do. Further, in the next step S15, the ECU 76 sets the temperature control valve 108 to the first position, and ends the control cycle.

  In the next control cycle, the ECU 76 starts the process again from step S11. If both the first clutch 6a and the second clutch 6b are not in the half-clutch state, the process proceeds to step S12. In step S12, the ECU 76 determines whether or not the value of the flag F2 is 0. Since the value of the flag F2 is 1 at this time, the ECU 76 advances the process to step S16 based on the determination in step S12.

  In step S16, the ECU 76 determines whether or not the temperature T of the hydraulic oil detected by the temperature sensor 110 is equal to or lower than a second temperature T2 (for example, 80 ° C.) set lower than the first temperature T1. If the temperature T of the hydraulic oil is not equal to or lower than the second temperature T2, the ECU 76 advances the process to step S19, sets the temperature control valve 108 to the first position, and ends the control cycle.

Even in the next control cycle, the value of the flag F2 is still 1, so that the first clutch 6a and the second clutch 6b are not in the half-clutch state, and the temperature T of the hydraulic oil detected by the temperature sensor 110 is If the temperature is not lower than the second temperature T2, the ECU 76 advances the process to step S19 and sets the temperature control valve 108 to the first position.
Therefore, when both the first clutch 6a and the second clutch 6b are not in the half-clutch state and the temperature T of the hydraulic oil detected by the temperature sensor 110 is not lower than the second temperature T2, the temperature control valve 108 is used. Is held in the first position.

  When the temperature control valve 108 is in the first position, as shown in FIG. 6, the hydraulic oil in the cooling lubrication oil passage 78 is supplied to the oil chamber 106 of the flow path switching valve 84 via the temperature control valve 108. Therefore, the spool 98 is in the first position. Therefore, as described above, the hydraulic oil in the cooling lubrication oil passage 78 is supplied to the oil cooler 82 via the annular first oil groove 102 formed in the spool 98. The hydraulic oil cooled by the oil cooler 82 is supplied to the cooling lubrication mechanism 48 via the annular second oil groove 104 formed in the spool 98. The hydraulic oil thus supplied to the cooling / lubricating mechanism 48 is used for cooling the clutch facings of the first clutch 6a and the second clutch 6b and for lubricating parts of the transmission 1 at various points.

  In this way, the operating oil is supplied to the cooling lubrication mechanism 48 via the oil cooler 82, whereby the temperature of the operating oil gradually decreases. If it is determined in step S16 of the oil temperature control that the temperature T of the hydraulic oil detected by the temperature sensor 110 has become equal to or lower than the second temperature T2, the ECU 76 advances the process to step S17 and sets the value of the flag F2 to 0. To do. Further, in the next step S18, the ECU 76 sets the temperature control valve 108 to the second position and ends the control cycle.

  In the next control cycle, the ECU 76 starts the process again from step S11. If both the first clutch 6a and the second clutch 6b are not in the half-clutch state, the process proceeds to step S12. In step S12, the ECU 76 determines whether or not the value of the flag F2 is 0. Since the value of the flag F2 at this time is 0, the ECU 76 advances the process to step S13 based on the determination in step S12.

  In step S13, the ECU 76 determines whether or not the temperature T of the hydraulic oil detected by the temperature sensor 110 has become equal to or higher than the first temperature T1. As described above, if the temperature T of the hydraulic oil is not equal to or higher than the first temperature T1, the ECU 76 advances the process to step S18. In step S18, the ECU 76 sets the temperature control valve 108 to the second position and ends the control cycle.

Therefore, when both the first clutch 6a and the second clutch 6b are not in the half-clutch state, the temperature control valve 108 is in the second position as long as the temperature T of the hydraulic oil does not rise again to become the first temperature T1 or higher. Will be held.
By performing the oil temperature control in this way, the ECU 76 supplies the hydraulic oil to the cooling lubrication mechanism 48 without passing through the oil cooler 82 when both the first clutch 6a and the second clutch 6b are not in the half-clutch state. In this case, when the temperature T of the hydraulic oil becomes equal to or higher than the first temperature T1, the hydraulic oil is supplied to the cooling lubrication mechanism 48 via the oil cooler 82. On the other hand, when the first clutch 6a and the second clutch 6b are not in the half-clutch state, when the hydraulic oil is supplied to the cooling lubrication mechanism 48 via the oil cooler 82, the temperature T of the hydraulic oil is the second. When the temperature is equal to or lower than T2, the hydraulic oil is supplied to the cooling lubrication mechanism 48 without passing through the oil cooler 82. Therefore, the temperature of the hydraulic oil supplied to the cooling lubrication mechanism 48 is adjusted within a specific temperature range based on the first temperature T1 and the second temperature T2.

  When the temperature of the hydraulic fluid used for cooling the clutch facing of the first clutch 6a and the second clutch 6b is too low, the viscosity of the hydraulic fluid becomes too high, and the first clutch 6a and the second clutch 6b, which are wet clutches, It becomes resistance when operating. Therefore, by adjusting the temperature of the hydraulic oil used for cooling the clutch facing in a specific temperature range based on the first and second temperatures in this way, the clutch facing can be cooled more effectively. In addition, the viscosity of the hydraulic oil can be maintained within an appropriate range.

Further, when at least one of the first clutch 6a and the second clutch 6b is in the half-clutch state when the ECU 76 is performing the oil temperature control, the ECU 76 performs the process according to the determination in step S11. The temperature control valve 108 is set to the first position, and the control cycle ends.
Even in the next control cycle, the ECU 76 determines in step S11 whether or not at least one of the first clutch 6a and the second clutch 6b is in a half-clutch state, and therefore at least one of the first clutch 6a and the second clutch 6b. As long as is in the half-clutch state, the temperature control valve 108 is held in the first position.

When the temperature control valve 108 is in the first position, the hydraulic oil in the cooling lubrication oil passage 78 is supplied to the cooling lubrication mechanism 48 via the oil cooler 82 as described above, and the first clutch 6a and the first clutch 6a. It is used for cooling the clutch facing of the two-clutch 6b and for lubricating various parts in the transmission 1.
When at least one of the first clutch 6a and the second clutch 6b is in a half-clutch state, the amount of heat generated in the clutch 6 increases, so that the temperature of the hydraulic oil may increase rapidly. However, in the oil temperature control, when at least one of the first clutch 6a and the second clutch 6b is in the half-clutch state, the hydraulic oil is supplied to the cooling lubrication mechanism 48 via the oil cooler 82 regardless of the temperature of the hydraulic oil. Therefore, it is possible to reliably prevent the temperature of the hydraulic oil from rising excessively as the amount of heat generated in the clutch 6 increases.

Although the description of the hydraulic circuit device for a transmission according to one embodiment of the present invention has been completed above, the present invention is not limited to the above embodiment.
For example, in the above-described embodiment, the transmission 1 is configured as a double-clutch automatic transmission having the first transmission mechanism 26 and the second transmission mechanism 34, but the type of the transmission is not limited thereto. That is, the transmission to which the present invention is applied may be a general automatic transmission having a single transmission mechanism, and uses a hydraulic transmission actuator and a clutch actuator according to the operation of the driver. Thus, it may be a transmission that performs a shift speed selection operation and a clutch operation. In any of the transmissions, the same effect can be obtained by applying the present invention as long as the gear selection operation and the clutch operation in the transmission are performed using the hydraulic pressure of the hydraulic oil. .

Moreover, in the said embodiment, although the line pressure of hydraulic oil was changed using the relief valve 60 and the line pressure control valve 74 for controlling the action | operation of this relief valve 60, the change method of a line pressure However, the present invention is not limited to this, and various methods can be applied.
In the above embodiment, the temperature of the hydraulic oil supplied to the cooling lubrication mechanism 48 is adjusted using the flow path switching valve 84 and the temperature control valve 108 for controlling the operation of the flow path switching valve 84. However, the method for adjusting the temperature of the hydraulic oil is not limited to this, and various methods can be applied.

  In the above embodiment, the supply start valve 80 is used so that the hydraulic oil is not supplied to the cooling lubrication mechanism 48 when the pressure of the hydraulic oil is not sufficiently increased immediately after the oil pump 50 starts operating. However, whether or not the supply start valve 80 is provided is arbitrary. The supply start valve 80 is omitted when it is not necessary to quickly raise the hydraulic oil pressure or when the hydraulic oil pressure can be raised immediately even if the hydraulic oil is supplied to the cooling lubrication mechanism 48. You can also

  Moreover, in the said embodiment, although the temperature sensor 110 which detects the temperature of hydraulic fluid was provided in the upstream of the oil pump 50, the arrangement position of the temperature sensor 110 is not limited to this.

1 is a skeleton diagram showing an overall configuration of a transmission to which a hydraulic circuit device according to an embodiment of the present invention is applied. It is a whole block diagram of the hydraulic circuit apparatus applied to the transmission of FIG. In the hydraulic circuit device of FIG. 2, when the line pressure control valve is in the first position, the relief valve is in an opened state and its peripheral configuration. In the hydraulic circuit device of FIG. 2, when the line pressure control valve is in the second position, the relief valve is in an open state and its peripheral configuration. It is a flowchart of the line pressure control which ECU performs. In the hydraulic circuit device of FIG. 2, when a temperature control valve exists in a 1st position, it is a block diagram of a flow-path switching valve and its periphery. FIG. 3 is a configuration diagram of a flow path switching valve and its surroundings when the temperature control valve is in a second position in the hydraulic circuit device of FIG. 2. It is a flowchart of the oil temperature control which ECU performs.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Transmission device 2 Transmission 6 Clutch 44 Hydraulic adjustment part (hydraulic adjustment means)
50 Oil pump 54 Oil pan (oil storage member)
56 Line pressure supply oil passage 60 Relief valve 64 Spool 66 Biasing spring 64b Second land (first pressure receiving portion)
64c 3rd land (2nd pressure receiving part)
76 ECU (control means)
78 Oil passage for cooling 82 Oil cooler 110 Temperature sensor (temperature detection means)

Claims (2)

An oil pump for supplying hydraulic oil stored in the oil storage member;
Hydraulic pressure adjusting means for adjusting the pressure of the hydraulic oil supplied by the oil pump to the line pressure and supplying the line pressure to the line pressure supply oil passage;
A transmission having a plurality of shift speeds, and performing a selection operation of the shift speeds using hydraulic oil supplied from the hydraulic pressure adjustment means via the line pressure supply oil path;
The hydraulic pressure adjusting means is connected and disconnected using hydraulic oil supplied through the line pressure supply oil passage, and transmits power to the transmission when in a connected state, while A clutch that interrupts transmission of power to the transmission;
Control means for controlling the hydraulic pressure adjusting means so that the line pressure is higher than the line pressure of the hydraulic oil used for connecting / disconnecting the clutch when performing the selection operation of the gear position of the transmission. A hydraulic circuit device for a transmission. The hydraulic pressure adjusting means includes a relief valve that, when opened, returns the hydraulic oil supplied from the oil pump to the upstream side of the oil pump,
The relief valve is
A spool movable between a valve opening position and a valve closing position;
A biasing spring that biases the spool in the valve closing direction;
A first pressure receiving portion that is provided on the spool and is constantly applied with the pressure of the hydraulic oil in the line pressure supply oil passage to press the spool in a valve opening direction;
A second pressure receiving portion that is provided on the spool and presses the spool in the valve opening direction in addition to the pressure of the spool by the first pressure receiving portion when the pressure of the hydraulic oil in the line pressure supply oil passage is applied; With
2. The transmission hydraulic circuit according to claim 1, wherein the control means changes the line pressure by switching whether or not hydraulic oil is applied to the second pressure receiving portion of the relief valve. 3. apparatus.

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