JP2018115748A - Control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve responsiveness of a fastening operation while preventing double bond of two fastening elements when an actuator corresponding to one of the two fastening elements is in ON-failure.SOLUTION: A control device 100 includes: a first solenoid valve 31 for controlling the pressure of a discharge oil of a hydraulic pump P and supplying it to a forward clutch FWD/C; a second solenoid valve 32 for controlling the pressure of the discharge oil of the hydraulic pump P and supplying it to a reverse brake REV/B; and a valve unit 50 for restricting an oil pressure which is supplied to the reverse brake REV/B by the second solenoid valve 32, when the first solenoid valve 31 is supplying a fastening pressure Pf for the forward clutch FWD/C to fasten with respect to the forward clutch FWD/C.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a control device that controls the operation of a first fastening element and a second fastening element that are arranged between a driving source for driving and a drive wheel.

  Patent Document 1 discloses an automatic transmission that switches between two fastening elements (for example, a forward fastening element and a reverse fastening element) by a manual valve that moves in conjunction with the operation of a shift lever.

JP 2005-155730 A

  In the automatic transmission described in Patent Document 1, when the manual valve supplies hydraulic pressure to one fastening element, the other fastening element communicates with the tank. For this reason, when the manual valve is switched to supply hydraulic pressure to the other fastening element, it takes time until the hydraulic pressure rises to the fastening pressure of the other fastening element, and the response is delayed.

  Therefore, it is conceivable to employ a shift-by-wire system that switches between two fastening elements by providing an actuator corresponding to each fastening element instead of the manual valve.

  However, in the automatic transmission disclosed in Patent Document 1, when such a shift-by-wire system is employed, if the actuator corresponding to one of the two fastening elements fails to turn on, the two fastening elements are There is a risk of double bonds.

  The present invention has been made in view of such a technical problem. When an actuator corresponding to one of the two fastening elements fails to be turned on, the two fastening elements are prevented from being double-coupled. However, it aims at improving the response of a fastening operation.

  A control device according to an aspect of the present invention includes a first actuator that regulates and supplies a discharge oil of a hydraulic pump to a first fastening element, and a second actuator that regulates and supplies the discharge oil of the hydraulic pump to a second fastening element And a valve unit that restricts a hydraulic pressure that the second actuator supplies to the second fastening element when the first actuator supplies a fastening pressure that the first fastening element fastens to the first fastening element. It is characterized by providing.

  According to this aspect, when the actuator corresponding to one of the two fastening elements fails to be turned on, the two fastening elements can be prevented from being double-coupled, and the response of the fastening operation can be improved.

It is a figure which shows the 1st position in the control apparatus which concerns on 1st Embodiment of this invention. It is a figure which shows the 2nd position in the control apparatus which concerns on 1st Embodiment of this invention. It is a flowchart of the control which the control apparatus which concerns on 1st Embodiment of this invention performs. It is a figure which shows the state in the middle of switching to a 1st position. It is a figure which shows the state in the middle of switching to a 2nd position. It is a time chart of the control which the control device concerning a 1st embodiment of the present invention performs. It is a time chart of the control which the control device concerning a 1st embodiment of the present invention performs. It is a figure which shows the 1st position in the control apparatus which concerns on 2nd Embodiment of this invention. It is a figure which shows the 2nd position in the control apparatus which concerns on 2nd Embodiment of this invention.

<First Embodiment>
Hereinafter, a first embodiment of the present invention will be described with reference to the accompanying drawings.

  1 and 2 are schematic configuration diagrams of the control device 100 according to the present embodiment. In the present embodiment, a case where the control device 100 is used in a continuously variable transmission will be described as an example. The control device 100 includes a forward clutch FWD / C (forward fastening element) as a first fastening element and a reverse brake REV / as a second fastening element of a transmission disposed between the driving source for driving and the drive wheels. Controls the operation of B (reverse fastening element).

  Control device 100 has a first position, a second position, and an intermediate position between the first position and the second position as positions corresponding to the range of the transmission. In the present embodiment, the first position is a position corresponding to the D range, that is, the forward range. The second position is a position corresponding to the R range, that is, the reverse range. The intermediate position is a position corresponding to the N range, that is, the neutral range.

  FIG. 1 shows a state where the control device 100 realizes the first position (D range), and FIG. 2 shows a state where the control device 100 realizes the second position (R range).

  The control device 100 regulates the discharge oil from the hydraulic pump P and supplies it to the forward clutch FWD / C as a first actuator 31 and the reverse brake REV by regulating the discharge oil from the hydraulic pump P. The second solenoid valve 32 as a second actuator to be supplied to / B, and the controller 20 as a controller for controlling the first solenoid valve 31 and the second solenoid valve 32 are provided.

  The hydraulic pump P is driven by a travel drive source (not shown). The hydraulic pump P may be an electric hydraulic pump that is driven by a power source such as a battery.

  The hydraulic oil (discharge oil) discharged from the hydraulic pump P is regulated by the pressure regulation circuit 10 and supplied to the supply flow path 41. The first solenoid valve 31 is provided in a first supply passage 42 that branches from the supply passage 41 and communicates with the forward clutch FWD / C, and releases or blocks the first supply passage 42. The second solenoid valve 32 is provided in a second supply flow path 43 that branches from the supply flow path 41 and communicates with the reverse brake REV / B, and releases or blocks the second supply flow path 43. The first and second solenoid valves 31, 32 are constituted by, for example, a three-port proportional solenoid valve. The first and second solenoid valves 31 and 32 are not limited to this, as long as they can regulate the discharge oil from the hydraulic pump P based on an instruction from the controller 20. Also good.

  The controller 20 controls the first solenoid valve 31 and the second solenoid valve 32 in accordance with the driver's range selection operation (shift operation). In the first position (D range) shown in FIG. 1, the first solenoid valve 31 supplies a fastening pressure Pf to the forward clutch FWD / C (hereinafter also referred to as “ON state” of the first solenoid valve 31). The second solenoid valve 32 is in a state of supplying the preload Prr to the reverse brake REV / B (hereinafter also referred to as “preload supply state” of the second solenoid valve 32). In the second position (R range) shown in FIG. 2, the first solenoid valve 31 supplies a preload Prf to the forward clutch FWD / C (hereinafter also referred to as “preload supply state” of the first solenoid valve 31). ), And the second solenoid valve 32 is in a state of supplying the engagement pressure Pr to the reverse brake REV / B (hereinafter also referred to as “ON state” of the second solenoid valve 32). At the intermediate position (N range), the first and second solenoid valves 31 and 32 are both OFF, and the forward clutch FWD / C and the reverse brake REV / B are both in communication with the tank T. The engagement pressure in the present embodiment means a pressure at which the forward clutch FWD / C and the reverse brake REV / B are engaged, or a pressure higher than the engagement pressure. The preload in the present embodiment is a pressure lower than the engagement pressure, and means a pressure at which the forward clutch FWD / C and the reverse brake REV / B are not engaged.

  The control device 100 further includes a valve unit 50 provided between the forward clutch FWD / C and the first solenoid valve 31 and between the reverse brake REV / B and the second solenoid valve 32.

  In the valve unit 50, when the first solenoid valve 31 supplies the fastening pressure Pf to which the forward clutch FWD / C is fastened to the forward clutch FWD / C, the second solenoid valve 32 is set to the reverse brake REV / B. The first solenoid valve 31 moves forward when the hydraulic pressure to be supplied is limited and the second solenoid valve 32 supplies the fastening pressure Pr to which the reverse brake REV / B is engaged with the reverse brake REV / B. The hydraulic pressure supplied to the clutch FWD / C is limited. Hereinafter, a specific configuration of the valve unit 50 will be described.

  The valve unit 50 includes a relief valve 53, a first switching valve 51 communicating the second solenoid valve 32 and the relief valve 53, and a reverse brake REV / The second switching valve 52 that allows the first solenoid valve 31 and the relief valve 53 to communicate with each other is provided by applying the fastening pressure Pr to B.

  The first switching valve 51 branches from the second solenoid valve 32 and the reverse brake REV / B in the second supply flow path 43 and is provided in the second branch flow path 45 communicating with the relief valve 53.

  The second switching valve 52 branches from the first solenoid valve 31 and the forward clutch FWD / C in the first supply flow path 42 and is provided in the first branch flow path 44 that communicates with the relief valve 53.

  The first switching valve 51 includes a pilot chamber 51a. The pilot chamber 51 a communicates with the upstream side (first solenoid valve 31 side) of the second switching valve 52 in the first branch flow path 44 through the first pilot passage 46. When the engagement pressure Pf is supplied from the first solenoid valve 31 to the forward clutch FWD / C through the first supply passage 42, the engagement pressure Pf is supplied to the pilot chamber 51a through the first branch passage 44 and the first pilot passage 46. Is supplied. Thereby, the 1st switching valve 51 releases the 2nd branch flow path 45, and connects the 2nd solenoid valve 32 and the relief valve 53 (state shown in FIG. 1). Further, when the pressure in the pilot chamber 51a becomes a predetermined value or less, the first switching valve 51 blocks the second branch flow path 45.

  The second switching valve 52 includes a pilot chamber 52a. The pilot chamber 52 a communicates with the upstream side (second solenoid valve 32 side) of the first switching valve 51 in the second branch flow path 45 through the second pilot passage 47. When the engagement pressure Pr is supplied from the second solenoid valve 32 to the reverse brake REV / B through the second supply passage 43, the engagement pressure Pr is supplied to the pilot chamber 52a through the second branch passage 45 and the second pilot passage 47. Is supplied. Thereby, the 2nd switching valve 52 releases the 1st branch flow path 44, and connects the 1st solenoid valve 31 and the relief valve 53 (state shown in FIG. 2). Further, when the pressure in the pilot chamber 52a becomes equal to or lower than a predetermined value, the second switching valve 52 blocks the first branch flow path 44.

  The valve opening pressure of the relief valve 53 is preferably set to be approximately the same as the preload Prf and the preload Prr, or slightly higher than the higher one of the preload Prf and the preload Prr. Thereby, even if the first switching valve 51 or the second switching valve 52 is opened and the preloads Prf and Prr are applied to the relief valve 53, the preloads Prf and Prr are not relieved. Therefore, waste of energy can be eliminated.

  As described above, when the first solenoid valve 31 supplies the fastening pressure Pf to the forward clutch FWD / C, the second solenoid valve 32 and the relief valve 53 are in communication (see FIG. 1). . For this reason, even if the second solenoid valve 32 fails to be ON, for example, and the high pressure (engagement pressure Pr) is supplied to the reverse brake REV / B, the relief valve 53 performs relief. That is, the relief valve 53 limits the hydraulic pressure that the second solenoid valve 32 supplies to the reverse brake REV / B. Thus, even when the forward clutch FWD / C is engaged, even if the second solenoid valve 32 is lost, the pressure in the second supply flow path 43 does not increase to the engagement pressure Pr. Therefore, the reverse brake REV / B is not engaged.

  Further, as described above, when the second solenoid valve 32 supplies the fastening pressure Pr to the reverse brake REV / B, the first solenoid valve 31 and the relief valve 53 are in communication (FIG. 2). reference). For this reason, even if the first solenoid valve 31 fails to be ON, for example, and supplies a high pressure (fastening pressure Pf) to the forward clutch FWD / C, it is relieved by the relief valve 53. That is, the relief valve 53 limits the hydraulic pressure that the first solenoid valve 31 supplies to the forward clutch FWD / C. Thus, even if the first solenoid valve 31 is lost while the reverse brake REV / B is engaged, the pressure in the first supply flow path 42 does not increase to the engagement pressure Pf. Therefore, the forward clutch FWD / C is not fastened.

  The control executed by the control device 100 configured as described above will be described with reference to the flowchart shown in FIG.

  In step S11, the controller 20 determines whether a shift operation from the R range to the D range has been performed. If a shift operation from the R range to the D range has been performed, the process proceeds to step S12. If a shift operation other than the shift operation from the R range to the D range is performed, the process proceeds to step S21. The flow after step S21 will be described later.

  In step S12, the controller 20 turns off the second solenoid valve 32. Specifically, in the state shown in FIG. 2, the controller 20 sets the current applied to the second solenoid valve 32 to zero. When the second solenoid valve 32 is switched to the OFF state, the hydraulic pressure (fastening pressure Pr) in the reverse brake REV / B is discharged to the tank T through the second supply passage 43 and the second solenoid valve 32. As a result, the reverse brake REV / B is released.

  At the same time, the hydraulic oil in the pilot chamber 52 a of the second switching valve 52 is discharged to the tank T through the second pilot passage 47, the second branch passage 45, the second supply passage 43 and the second solenoid valve 32. The When the pressure in the pilot chamber 52a becomes a predetermined value or less, the second switching valve 52 is switched to the OFF state by the biasing force of the spring and blocks the first branch flow path 44 (see FIG. 4).

  In step S13, the controller 20 starts the operation of a built-in timer (not shown).

  In step S14, it is determined whether the time has passed the threshold value Ts1 since the timer started operating. If the threshold value Ts1 has elapsed since the timer started operating, the process proceeds to step S15. If the threshold value Ts1 has not elapsed, the determination in step S14 is repeated. The threshold value Ts1 will be described later.

  In step S15, the controller 20 turns on the first solenoid valve 31. Specifically, the controller 20 applies a current to switch the first solenoid valve 31 to the ON state. When the first solenoid valve 31 is switched to the ON state, the fastening pressure Pf regulated by the first solenoid valve 31 is supplied to the forward clutch FWD / C through the first supply passage 42. As a result, the forward clutch FWD / C is engaged, and the shift range is switched to the D range.

  At this time, the fastening pressure Pf supplied from the first solenoid valve 31 acts on the pilot chamber 51a of the first switching valve 51 through the first supply passage 42, the first branch passage 44, and the first pilot passage 46. . Thereby, the 1st switching valve 51 switches to an ON state, the 2nd branch flow path 45 is open | released, and the 2nd solenoid valve 32 and the relief valve 53 are connected.

  In step S <b> 16, it is determined whether the time has passed the threshold value Ts <b> 2 since the timer started operating. If the threshold value Ts2 has elapsed since the timer started operating, the process proceeds to step S17. If the threshold value Ts2 has not elapsed, the determination in step S16 is repeated. The threshold value Ts2 will be described later.

  In step S17, the second solenoid valve 32 is brought into a preload supply state. Specifically, the controller 20 applies a current to switch the second solenoid valve 32 to the preload supply state. When the second solenoid valve 32 is switched to the preload supply state, the preload Prr regulated by the second solenoid valve 32 is supplied to the reverse brake REV / B through the second supply passage 43 (see FIG. 1).

  Thus, in this embodiment, when the shift range is switched to the D range, the preload Prr is applied to the reverse brake REV / B. As a result, when switching from the D range to the R range, it is possible to shorten the time during which the hydraulic pressure of the reverse brake REV / B rises to the engagement pressure Pr, so it is possible to improve the responsiveness when switching the R range.

  In the state shown in FIG. 1, the preload Prr is also supplied from the second supply channel 43 to the pilot chamber 52a of the second switching valve 52 through the second branch channel 45 and the second pilot channel 47. The switching valve 52 is maintained in an OFF state (a state in which the first branch flow path 44 is blocked) by the biasing force of the spring. For this reason, the engagement pressure Pf supplied to the forward clutch FWD / C is not discharged from the second switching valve 52 to the tank T through the relief valve 53.

  The preload Prr supplied from the second solenoid valve 32 acts on the relief valve 53 from the second supply channel 43 through the second branch channel 45 and the first switching valve 51. As described above, the relief valve Prr The valve opening pressure 53 is set to the same level as the preload Prr or slightly higher than the preload Prr, so that the preload Prr is not discharged into the tank T.

  Here, the threshold value Ts1 will be described. The threshold Ts1 is equal to or greater than the time T1 when the time from the start of operation of the timer until the second solenoid valve 32 is turned OFF and the time until the second switching valve 52 shuts off the first branch flow path 44 is defined as time T1. Is set to a value such that

  By setting the threshold value Ts1 to be equal to or longer than the time T1, the first solenoid valve 31 can be switched to the ON state after the second switching valve 52 blocks the first branch flow path 44. Thus, when the fastening pressure Pf is supplied from the first solenoid valve 31, the second switching valve 52 blocks the first branch flow path 44, so that the fastening pressure Pf supplied from the first solenoid valve 31 is Further, it is possible to prevent the second switching valve 52 from being discharged to the tank T through the relief valve 53.

  Next, the threshold value Ts2 will be described. When the time from when the timer starts to the state until the first switching valve 51 releases the second branch flow path 45 as described above is defined as time T2, the threshold Ts2 is set to be equal to or greater than time T2. Set to the correct value.

  By setting the threshold Ts2 to be equal to or greater than the time T2, the second solenoid valve 32 can be switched to the preload supply state after the first switching valve 51 releases the second branch flow path 45. As a result, for example, when the second solenoid valve 32 fails to be turned on and is turned on, the high pressure (fastening pressure Pr) supplied from the second solenoid valve 32 is changed to the second branch flow path 45. The first switching valve 51 and the relief valve 53 are discharged to the tank T. Thus, even when the forward clutch FWD / C is engaged, the engagement pressure Pr is not supplied to the reverse brake REV / B even if the second solenoid valve 32 fails to be turned on. Therefore, it can be avoided that the forward clutch FWD / C and the reverse brake REV / B are double-engaged to enter the interlock state.

  Next, the flow after step S21 will be described.

  In step S21, the controller 20 determines whether a shift operation from the D range to the R range has been performed. If a shift operation from the D range to the R range is performed, the process proceeds to step S22. If the shift operation is not performed from the D range to the R range, that is, if the shift operation from the D or R range to the N range is performed, the control is terminated.

  In step S22, the controller 20 turns off the first solenoid valve 31. Specifically, in the state shown in FIG. 1, the controller 20 sets the current applied to the first solenoid valve 31 to zero. When the first solenoid valve 31 is switched to the OFF state, the hydraulic pressure (fastening pressure Pf) in the forward clutch FWD / C is discharged to the tank T through the first supply passage 42 and the first solenoid valve 31. Thereby, the forward clutch FWD / C is released.

  At the same time, the hydraulic oil in the pilot chamber 51 a of the first switching valve 51 is discharged to the tank T through the first pilot passage 46, the first branch passage 44, the first supply passage 42 and the first solenoid valve 31. The When the pressure in the pilot chamber 51a becomes a predetermined value or less, the first switching valve 51 is switched to the OFF state by the biasing force of the spring and blocks the second branch flow path 45 (see FIG. 5).

  In step S23, the controller 20 starts the operation of a built-in timer (not shown).

  In step S24, it is determined whether the time has passed the threshold value Ts3 since the timer started operating. If the threshold value Ts3 has elapsed since the timer started operating, the process proceeds to step S25. If the threshold value Ts3 has not elapsed, the determination in step S24 is repeated. The threshold value Ts3 will be described later.

  In step S25, the controller 20 turns on the second solenoid valve 32. Specifically, the controller 20 applies current to switch the second solenoid valve 32 to the ON state. When the second solenoid valve 32 is switched to the ON state, the fastening pressure Pr adjusted by the second solenoid valve 32 is supplied to the reverse brake REV / B through the second supply passage 43. As a result, the reverse brake REV / B is engaged, and the shift range is switched to the R range.

  At this time, the fastening pressure Pr supplied from the second solenoid valve 32 acts on the pilot chamber 52a of the second switching valve 52 through the second supply passage 43, the second branch passage 45, and the second pilot passage 47. . Thereby, the 2nd switching valve 52 switches to an ON state, the 1st branch flow path 44 is open | released, and the 1st solenoid valve 31 and the relief valve 53 are connected.

  In step S26, it is determined whether or not the time has passed the threshold value Ts4 since the timer started operating. If the threshold Ts4 has elapsed since the timer started operating, the process proceeds to step S27. If the threshold Ts4 has not elapsed, the determination in step S26 is repeated. The threshold value Ts4 will be described later.

  In step S27, the first solenoid valve 31 is brought into a preload supply state. Specifically, the controller 20 applies a current to switch the first solenoid valve 31 to the preload supply state. When the first solenoid valve 31 is switched to the preload supply state, the preload Prf adjusted by the first solenoid valve 31 is supplied to the forward clutch FWD / C through the first supply passage 42 (see FIG. 2).

  Thus, in this embodiment, when the shift range is switched to the R range, the preload Prf is applied to the forward clutch FWD / C. Thereby, when switching from the R range to the D range, the time for the hydraulic pressure of the forward clutch FWD / C to rise to the engagement pressure Pf can be shortened, so that the responsiveness at the time of switching the D range can be improved.

  In the state shown in FIG. 2, the preload Prf is also supplied from the first supply channel 42 to the pilot chamber 51a of the first switching valve 51 through the first branch channel 44 and the first pilot channel 46. The switching valve 51 is maintained in an OFF state (a state in which the second branch flow path 45 is blocked) by the biasing force of the spring. Therefore, the engagement pressure Pr supplied to the reverse brake REV / B is not discharged from the first switching valve 51 to the tank T through the relief valve 53.

  The preload Prf supplied from the first solenoid valve 31 acts on the relief valve 53 from the first supply passage 42 through the first branch passage 44 and the second switching valve 52. As described above, the relief valve The valve opening pressure 53 is set to be approximately equal to the preload Prf or slightly higher than the preload Prf, so that the preload Prf is not discharged into the tank T.

  Here, the threshold value Ts3 will be described. The threshold Ts3 is equal to or greater than the time T3 when the time from the start of operation of the timer until the first solenoid valve 31 is turned OFF and the time until the first switching valve 51 shuts off the second branch flow path 45 is defined as time T3. Is set to a value such that

  By setting the threshold value Ts3 to be equal to or greater than the time T3, the second solenoid valve 32 can be switched to the ON state after the first switching valve 51 blocks the second branch flow path 45. Thus, when the fastening pressure Pr is supplied from the second solenoid valve 32, the first switching valve 51 blocks the second branch flow path 45, so that the fastening pressure Pr supplied from the second solenoid valve 32 is reduced. Further, the discharge from the first switching valve 51 to the tank T through the relief valve 53 can be prevented.

  Subsequently, the threshold value Ts4 will be described. When the time from when the timer starts to the time until the second switching valve 52 releases the first branch flow path 44 as described above is defined as time T4, the threshold Ts4 is set to be equal to or greater than time T4. Set to the correct value.

  By setting the threshold value Ts4 to the time T4 or more, the first solenoid valve 31 can be switched to the preload supply state after the second switching valve 52 releases the first branch flow path 44. As a result, for example, when the first solenoid valve 31 fails to be turned on and is turned on, the high pressure (fastening pressure Pf) supplied from the first solenoid valve 31 is changed to the first branch flow path 44. Then, it is discharged to the tank T through the second switching valve 52 and the relief valve 53. Thus, even when the reverse brake REV / B is engaged, even if the first solenoid valve 31 fails to be turned on, the engagement pressure Pf is not supplied to the forward clutch FWD / C. Therefore, it can be avoided that the forward clutch FWD / C and the reverse brake REV / B are double-engaged to enter the interlock state.

  Next, how control by the control device 100 is executed will be described with reference to time charts shown in FIGS. 6 and 7.

  First, a case where a shift operation from the R range to the D range is performed will be described with reference to FIG. FIG. 6 is a time chart when a shift operation from the R range to the D range is performed.

  When the driver performs a shift operation to change from the R range to the D range, the controller 20 determines that the shift range has been changed from the R range to the D range (time t1).

  When the controller 20 determines that the shift range has been changed from the R range to the D range, the controller 20 immediately turns off the second solenoid valve 32 and starts the operation of the timer.

  When the second solenoid valve 32 is turned off, the hydraulic pressure (fastening pressure Pr) in the reverse brake REV / B is discharged to the tank T through the second supply passage 43 and the second solenoid valve 32. As a result, the reverse brake REV / B is released.

  At the same time, the hydraulic oil in the pilot chamber 52 a of the second switching valve 52 is discharged to the tank T through the second pilot passage 47, the second branch passage 45, the second supply passage 43 and the second solenoid valve 32. The When the pressure in the pilot chamber 52a becomes a predetermined value or less, the second switching valve 52 is switched to the OFF state by the urging force of the spring and shuts off the first branch flow path 44 (time t2).

  Then, the controller 20 turns on the first solenoid valve 31 (time t3).

  When the first solenoid valve 31 is switched to the ON state, the fastening pressure Pf regulated by the first solenoid valve 31 is supplied to the forward clutch FWD / C through the first supply passage 42. As a result, the forward clutch FWD / C is engaged, and the transmission range is switched to the D range. At this time, the fastening pressure Pf supplied from the first solenoid valve 31 is supplied to the pilot chamber 51a of the first switching valve 51 through the first branch passage 44 and the first pilot passage 46, and the first switching valve 51 is turned on. The state is switched (time t4). Thereby, the 1st switching valve 51 releases the 2nd branch flow path 45, and the 2nd solenoid valve 32 and the relief valve 53 are connected.

  Thereafter, the controller 20 switches the second solenoid valve 32 to the preload supply state (time t5). When the second solenoid valve 32 is switched to the preload supply state, the preload Prr regulated by the second solenoid valve 32 is supplied to the reverse brake REV / B through the second supply passage 43.

  In the present embodiment, as indicated by a thick solid line in FIG. 6, when the shift range is located in the R range, the preload Prf is applied in advance to the forward clutch FWD / C. As a result, when the R range is switched to the D range, the hydraulic pressure of the forward clutch FWD / C is higher than the engagement pressure Pf as compared to the case where the preload Prf is not applied in advance to the forward clutch FWD / C indicated by the thick dotted line in FIG. The time to climb up can be shortened. Therefore, the responsiveness at the time of D range switching can be improved.

  Next, a case where a shift operation from the D range to the R range is performed will be described with reference to FIG. FIG. 7 is a time chart when a shift operation from the D range to the R range is performed.

  When the driver performs a shift operation to change from the D range to the R range, the controller 20 determines that the shift range has been changed from the D range to the R range (time t6).

  When the controller 20 determines that the shift range has been changed from the D range to the R range, the controller 20 immediately turns off the first solenoid valve 31 and starts the operation of the timer.

  When the first solenoid valve 31 is turned off, the hydraulic pressure (fastening pressure Pf) in the forward clutch FWD / C is discharged to the tank T through the first supply passage 42 and the first solenoid valve 31. Thereby, the forward clutch FWD / C is released.

  At the same time, the hydraulic oil in the pilot chamber 51 a of the first switching valve 51 is discharged to the tank T through the first pilot passage 46, the first branch passage 44, the first supply passage 42 and the first solenoid valve 31. The When the pressure in the pilot chamber 51a becomes a predetermined value or less, the first switching valve 51 is switched to the OFF state by the urging force of the spring and shuts off the second branch flow path 45 (time t7).

  Then, the controller 20 turns on the second solenoid valve 32 (time t8).

  When the second solenoid valve 32 is switched to the ON state, the fastening pressure Pr adjusted by the second solenoid valve 32 is supplied to the reverse brake REV / B through the second supply passage 43. As a result, the reverse brake REV / B is engaged, and the range of the transmission is switched to the R range. At this time, the fastening pressure Pr supplied from the second solenoid valve 32 is supplied to the pilot chamber 52a of the second switching valve 52 through the second branch passage 45 and the second pilot passage 47, and the second switching valve 52 is turned on. The state is switched (time t9). Thereby, the 2nd switching valve 52 releases the 1st branch flow path 44, and the 1st solenoid valve 31 and the relief valve 53 are connected.

  Thereafter, the controller 20 switches the first solenoid valve 31 to the preload supply state (time t10). When the first solenoid valve 31 is switched to the preload supply state, the preload Prf adjusted by the first solenoid valve 31 is supplied to the forward clutch FWD / C through the first supply passage 42.

  In the present embodiment, as shown by a thick solid line in FIG. 7, when the shift range is located in the D range, the preload Prr is applied in advance to the reverse brake REV / B. Thus, when the D range is switched to the R range, the hydraulic pressure of the reverse brake REV / B is higher than the engagement pressure Pr compared to the case where the preload Prr is not applied in advance to the reverse brake REV / B indicated by the thick dotted line in FIG. The time to climb up can be shortened. Therefore, the responsiveness at the time of R range switching can be improved.

  In the first embodiment, a preload may be applied only to either the forward clutch FWD / C or the reverse brake REV / B. In this case, the switching valve (the first switching valve 51 and the second switching valve 52) on the side where no preload is applied is not necessary.

  According to the control apparatus 100 of 1st Embodiment comprised as mentioned above, there exist the following effects.

  In the control device 100, when the first solenoid valve 31 supplies the fastening pressure Pf that the forward clutch FWD / C is fastened to the forward clutch FWD / C, the valve unit 50 (relief valve 53) The hydraulic pressure supplied to the reverse brake REV / B by the solenoid valve 32 is limited. Accordingly, when the forward clutch FWD / C is engaged, even if the second solenoid valve 32 fails to be turned on, the pressure in the second supply flow path 43 does not rise to the engagement pressure Pr. The brake REV / B is not engaged. Further, in the control device 100, when the first solenoid valve 31 is supplying the fastening pressure Pf that the forward clutch FWD / C is fastened to the forward clutch FWD / C, the second solenoid valve 32 is the reverse brake REV / Hydraulic pressure (preload Prr) is supplied to B. As a result, when the D range is switched to the R range, it is possible to shorten the time during which the hydraulic pressure of the reverse brake REV / B rises to the engagement pressure Pr.

  Therefore, according to the control device 100, when the second solenoid valve 32 fails to turn ON, the forward clutch FWD / C and the reverse brake REV / B are prevented from being double-coupled, and the reverse brake at the time of switching the R range. Responsiveness of the REV / B fastening operation is improved (effect corresponding to claims 1 and 2).

  Further, in the control device 100, when the second solenoid valve 32 is supplying the fastening pressure Pr for fastening the reverse brake REV / B to the reverse brake REV / B, the valve unit 50 (relief valve 53) is The hydraulic pressure supplied to the forward clutch FWD / C by the first solenoid valve 31 is limited. Thus, when the reverse brake REV / B is engaged, even if the first solenoid valve 31 is lost, the pressure in the first supply flow path 42 does not rise to the engagement pressure Pf. Clutch FWD / C is not engaged. Further, in the control device 100, when the second solenoid valve 32 supplies the engagement pressure Pr that the reverse brake REV / B is engaged to the reverse brake REV / B, the first solenoid valve 31 is the forward clutch FWD / B. Hydraulic pressure (preload Prf) is supplied to C. Thereby, when switching from the R range to the D range, it is possible to shorten the time for the hydraulic pressure of the forward clutch FWD / C to rise to the engagement pressure Pf.

  Therefore, according to the control device 100, the forward clutch FWD / C and the reverse brake REV / B are prevented from being double-coupled when the first solenoid valve 31 is lost, and the forward clutch is switched at the time of D range switching. The responsiveness of the FWD / C fastening operation is improved (effect corresponding to claims 1 and 2).

  In the control device 100, when the engagement pressures Pf and Pr are applied to one of the forward clutch FWD / C and the reverse brake REV / B, the other of the forward clutch FWD / C and the reverse brake REV / B communicates with the relief valve 53. Therefore, even if the solenoid valve on the other side fails to be turned on, the pressure on the other side of the forward clutch FWD / C and the reverse brake REV / B is relieved by the relief valve 53 and can be increased to the engagement pressures Pf and Pr. Absent. Therefore, it is possible to prevent the forward clutch FWD / C and the reverse brake REV / B from being double-coupled (effect corresponding to claim 3).

  In the control device 100, when the first and second solenoid valves 31 and 32 are OFF, the hydraulic pressure in the pilot chambers 51a and 51b of the first and second switching valves 51 and 52 is also changed to the forward clutch FWD / C and the reverse brake. The oil is discharged into the tank T together with the hydraulic pressure in the REV / B. Accordingly, the speed at which the hydraulic pressure is discharged from the forward clutch FWD / C and the reverse brake REV / B can be slowed, so that the shock when the forward clutch FWD / C and the reverse brake REV / B are released can be reduced. Corresponding effect).

Second Embodiment
With reference to FIG.8 and FIG.9, the control apparatus 200 which concerns on 2nd Embodiment of this invention is demonstrated. Below, it demonstrates centering on a different point from 1st Embodiment mentioned above, the same code | symbol is attached | subjected to the structure same as 1st Embodiment, and description is abbreviate | omitted.

  In the control device 100 of the first embodiment, the valve unit 50 includes the first switching valve 51, the second switching valve 52, and the relief valve 53, whereas in the control device 200 of the second embodiment, the valve unit 150 is the third. The difference is that a switching valve 151 and a fourth switching valve 152 are provided. This will be specifically described below.

  FIG. 8 shows a state where the control device 200 realizes the first position (D range), and FIG. 9 shows a state where the control device 100 realizes the second position (R range).

  The valve unit 150 in the control device 200 includes a third switching valve 151 that shuts off the second solenoid valve 32 and the reverse brake REV / B, and a reverse brake REV when the engagement pressure Pf to the forward clutch FWD / C acts. The fourth switching valve 152 that shuts off the first solenoid valve 31 and the forward clutch FWD / C by the engagement pressure Pr to / B acts.

  The third switching valve 151 is provided between the second solenoid valve 32 and the reverse brake REV / B in the second supply flow path 43.

  The fourth switching valve 152 is provided between the first solenoid valve 31 and the forward clutch FWD / C in the first supply flow path 42.

  The third switching valve 151 includes a pilot chamber 151a. The pilot chamber 151a communicates between the fourth switching valve 152 and the forward clutch FWD / C in the first supply passage 42 through the first pilot passage 146. The third switching valve 151 releases the second supply flow path 43 and communicates the second solenoid valve 32 and the reverse brake REV / B when the pressure in the pilot chamber 151a is equal to or lower than a predetermined value.

  When the fastening pressure Pf is supplied from the first solenoid valve 31 to the forward clutch FWD / C through the first supply passage 42, the fastening pressure Pf is also supplied to the pilot chamber 151a through the first pilot passage 146. Thereby, the 3rd switching valve 151 interrupts | blocks the 2nd supply flow path 43, and interrupts | blocks the 2nd solenoid valve 32 and reverse brake REV / B (refer FIG. 8).

  The fourth switching valve 152 includes a pilot chamber 152a. The pilot chamber 152a communicates between the third switching valve 151 and the reverse brake REV / B in the second supply passage 43 through the second pilot passage 147. The fourth switching valve 152 releases the first supply flow path 42 and connects the first solenoid valve 31 and the forward clutch FWD / C when the pressure in the pilot chamber 152a is equal to or lower than a predetermined value.

  When the engagement pressure Pr is supplied from the second solenoid valve 32 to the reverse brake REV / B through the second supply passage 43, the engagement pressure Pr is also supplied to the pilot chamber 152a through the second pilot passage 147. Thereby, the 4th switching valve 152 interrupts | blocks the 1st supply flow path 42, and interrupts | blocks the 1st solenoid valve 31 and the forward clutch FWD / C (refer FIG. 9).

  The control device 200 configured as described above performs control based on the flowchart shown in FIG. 3 in the same manner as the control device 100. In the present embodiment, the threshold values Ts1 to Ts4 are set as follows.

  First, the threshold value Ts1 will be described. When the time from when the timer starts to operate until the reverse brake REV / B is released is time T5, the threshold Ts1 is set to a value that is equal to or greater than time T5.

  If the first solenoid valve 31 is switched to the ON state before the reverse brake REV / B is released, if the fourth switching valve 152 releases the first supply flow path 42, the first solenoid The fastening pressure Pf supplied from the valve 31 acts on the pilot chamber 151 a of the third switching valve 151 through the fourth switching valve 152 and the first pilot passage 146. Thereby, the 3rd switching valve 151 may switch to an ON state, and there exists a possibility that the 2nd supply flow path 43 may be interrupted | blocked. When the third switching valve 151 is switched to the ON state in this way, the engagement pressure Pr is not discharged from the reverse brake REV / B, and the state where the reverse brake REV / B is engaged is maintained. Therefore, the reverse brake REV / B can be reliably released by setting the threshold value Ts1 to a value that is equal to or greater than the time T5.

  Next, the threshold value Ts2 will be described. When the time from when the timer starts to the state until the third switching valve 151 shuts off the second supply passage 43 as described above is defined as time T6, the threshold Ts2 is set to be equal to or greater than time T6. Set to the correct value.

  By setting the threshold Ts2 to the time T6 or more, the second solenoid valve 32 can be switched to the preload supply state after the third switching valve 151 blocks the second supply flow path 43. As a result, for example, when the second solenoid valve 32 has failed to be turned ON, the hydraulic pressure supplied from the second solenoid valve 32 is changed to the reverse brake REV / B by the third switching valve 151. Can be prevented. Therefore, when the forward clutch FWD / C is engaged, even if the second solenoid valve 32 fails to be turned on, the engagement pressure Pr is not supplied to the reverse brake REV / B. Therefore, it can be avoided that the forward clutch FWD / C and the reverse brake REV / B are double-engaged to enter the interlock state.

  Next, the threshold value Ts3 will be described. The threshold Ts3 is set to a value that is equal to or greater than the time T7, where time T7 is the time from when the timer starts to operate until the forward clutch FWD / C is released.

  If the second solenoid valve 32 is switched to the ON state before the forward clutch FWD / C is released, if the third switching valve 151 releases the second supply flow path 43, the second solenoid The fastening pressure Pr supplied from the valve 32 acts on the pilot chamber 152a of the fourth switching valve 152 through the third switching valve 151 and the second pilot passage 147. Thereby, the 4th switching valve 152 may switch to an ON state, and there exists a possibility that the 2nd supply flow path 43 may be interrupted | blocked. Thus, when the fourth switching valve 152 is switched to the ON state, the engagement pressure Pf is not discharged from the forward clutch FWD / C, and the state where the forward clutch FWD / C is engaged is maintained. Therefore, the forward clutch FWD / C can be reliably released by setting the threshold value Ts3 to a value that is equal to or greater than the time T7.

  Next, the threshold value Ts4 will be described. When the time from when the timer starts to the time until the fourth switching valve 152 blocks the first supply flow path 42 as described above is defined as time T8, the threshold Ts4 is set to be equal to or greater than time T8. Set to the correct value.

  By setting the threshold Ts4 to the time T8 or more, the first solenoid valve 31 can be switched to the preload supply state after the fourth switching valve 152 blocks the first supply flow path 42. As a result, for example, when the first solenoid valve 31 fails to be turned ON and is turned ON, the hydraulic pressure supplied from the first solenoid valve 31 is changed by the fourth switching valve 152 by the forward clutch FWD / C. Can be prevented. Therefore, even when the reverse brake REV / B is engaged, even if the first solenoid valve 31 is lost, the engagement pressure Pf is not supplied to the forward clutch FWD / C. Therefore, it is possible to avoid the forward clutch FWD / C and the reverse brake REV / B from being double-coupled to enter the interlock state.

  According to the control device 200 of the second embodiment described above, as with the control device 100, the first and second solenoid valves 31, 32 corresponding to one of the forward clutch FWD / C and the reverse brake REV / B are provided. Improving the responsiveness of the engagement operation of the other of the forward clutch FWD / C and the reverse brake REV / B while preventing the forward clutch FWD / C and the reverse brake REV / B from being double-coupled when the ON failure occurs. can do. Further, since the valve unit 150 does not need to include the relief valve 53, the number of parts can be reduced (effect corresponding to claim 4).

  Further, according to the control device 200, similarly to the control device 100, by providing the third switching valve 151 and the fourth switching valve 152, the speed at which the hydraulic pressure is discharged from the forward clutch FWD / C and the reverse brake REV / B. Therefore, the shock when the forward clutch FWD / C and the reverse brake REV / B are released can be reduced (effect corresponding to claim 4).

  Further, in the control device 200, when the first and second solenoid valves 31 and 32 are in the preload supply state, the third and fourth switching valves 151 and 152 block the first and second supply passages 42 and 43, respectively. Therefore, the preload Prf and the preload Prr can be set higher than the preload Prf and the preload Prr in the first embodiment.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

  The first engagement element may be the reverse brake REV / B, and the second engagement element may be the forward clutch FWD / C. In this case, the second solenoid valve 32 corresponds to the first actuator, and the first solenoid valve 31 corresponds to the second actuator.

  The transmission may be a CVT with an auxiliary transmission. In this case, as a combination of the first and second fastening elements, for example, a first speed forward fastening element and a reverse fastening element, a second speed forward fastening element and a backward fastening element, or a first speed forward fastening element And a combination of two-speed forward fastening elements.

  The transmission may be a stepped transmission. In this case, if the two shift speeds are double-coupled, an interlock state may occur or the shift speed may be changed. For this reason, what is necessary is just to select suitably the combination which may produce such a problem as a 1st, 2nd fastening element.

  Switching of control in the control devices 100 and 200 is performed based on time (threshold values Ts1 to Ts4). Instead of this, for example, the valve bodies of the first to fourth switching valves 51, 52, 151, and 152 are changed. The position may be detected, and control may be performed based on the detected position. Furthermore, the pressure in the forward clutch FWD / C and the reverse brake REV / B or the positions of the forward clutch FWD / C and the reverse brake REV / B may be detected, and control may be performed based on these.

  Further, when the engagement pressures Pf and Pr are discharged from the forward clutch FWD / C and the reverse brake REV / B, the preloads Prf and Prr may be reduced to the preloads Prf and Prr.

100, 200 Control device 20 Controller 31 First solenoid valve (first actuator)
32 Second solenoid valve (second actuator)
50, 150 Valve unit 51 First switching valve 52 Second switching valve 53 Relief valve 151 Third switching valve 152 Fourth switching valve FWD / C Forward clutch (first or second engagement element)
REV / B Reverse brake (second or first engagement element)

Claims (4)

A control device for controlling the operation of a first fastening element and a second fastening element disposed between a driving source for driving and a driving wheel,
A first actuator that regulates the oil discharged from the hydraulic pump and supplies the oil to the first fastening element;
A second actuator that regulates the oil discharged from the hydraulic pump and supplies the oil to the second fastening element;
When the first actuator is supplying the fastening pressure that the first fastening element fastens to the first fastening element, the hydraulic pressure that the second actuator supplies to the second fastening element is limited. A valve unit;
A control device comprising: The control device according to claim 1,
The valve unit is supplied from the first actuator to the first fastening element when the second actuator is supplying a fastening pressure at which the second fastening element is fastened to the second fastening element. A control device characterized by limiting the hydraulic pressure. The control device according to claim 2,
The valve unit is
A relief valve,
A first switching valve that communicates the second actuator and the relief valve by the fastening pressure acting on the first fastening element;
A control device comprising: a second switching valve that communicates the first actuator and the relief valve when the fastening pressure is applied to the second fastening element. The control device according to claim 2,
The valve unit is
It is provided in an oil passage between the second actuator and the second fastening element, and the fastening pressure to the first fastening element acts to shut off the second actuator and the second fastening element. A third switching valve;
It is provided in an oil passage between the first actuator and the first fastening element, and the fastening pressure to the second fastening element acts to shut off the first actuator and the first fastening element. And a fourth switching valve.

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