JP6420190B2 - Power transmission device for vehicle - Google Patents

Description

  The present invention relates to a vehicle power transmission device.

  2. Description of the Related Art Conventionally, there is known a belt type continuously variable transmission that includes a drive (DR) pulley and a driven (DN) pulley each having a half body movable and a metal belt wound around these two pulleys. Patent Document 1 discloses a hydraulic circuit using a linear solenoid valve as a configuration for controlling the pressure of a belt pressing hydraulic control valve in a belt-type continuously variable transmission.

  In the hydraulic circuit in the prior art, when a failure of devices constituting the hydraulic circuit such as a linear solenoid valve is detected, all currents are mechanically set to zero (no energization) from the normal operation mode in which the hydraulic circuit is electrically controlled. Transition to the backup operation mode in which hydraulic control is performed.

  For example, as shown in FIG. 7, the output characteristic of the linear solenoid valve is set so that the signal pressure (DRC pressure) output from the linear solenoid valve decreases as the current increases, and the signal pressure increases as the current decreases. Has been. The relationship between the current and the signal pressure has output characteristics (inverse logic output characteristics) indicated by a linear function having a negative slope. As shown in FIG. 7, for example, as shown in FIG. 7, in the reverse logic output characteristics, in order to secure a signal pressure that enables power transmission of the belt-type continuously variable transmission when the operation mode shifts to a backup operation mode in which hydraulic control is mechanically performed. When the current is zero (non-energized), the linear solenoid valve outputs hydraulic oil having a maximum signal pressure 701 as the signal pressure (DRC pressure) on the drive (DR) pulley side. By making the output characteristics of the linear solenoid valve an output characteristic of inverse logic, a constant pressure (signal pressure) is secured to supply the DR pulley and DN pulley to the cylinder chamber at the time of failure, and the belt type continuously variable transmission Power transmission can be made possible.

JP 11-182666 A

  However, in the normal use state from the start of the vehicle to the high-speed traveling, the hydraulic pressure (signal pressure) that is normally used increases the frequency of use on the low pressure side, so the signal pressure in the normal region 702 (FIG. 7) that consumes a lot of current is frequently used. It will be. The hydraulic circuit in the prior art is configured to increase current consumption in the normal region 702 in order to ensure a backup function at the time of failure.

  In view of the above problems, the present invention provides a vehicular power transmission device that can ensure a backup function during a failure and reduce current consumption.

  The vehicle power transmission device according to the first aspect of the present invention changes the pulley width of the drive pulley and the driven pulley by changing the axial thrust applied to the drive pulley and the driven pulley, thereby changing the gear ratio. A vehicular power transmission device having a continuously variable belt-type continuously variable transmission and a hydraulic control circuit (40) for controlling generation of the axial thrust, wherein the hydraulic control circuit (40) includes: A pump (31) that supplies hydraulic oil, a first pressure regulating valve (41) that regulates the discharge pressure of the hydraulic oil to a line pressure (PH), and a control that regulates pressure using the line pressure (PH) as an original pressure A second pressure regulating valve (44) that outputs hydraulic oil having a pressure (CR), and a first adjustable pressure valve that outputs hydraulic oil having a signal pressure (DRC) regulated using the control pressure (CR) as an original pressure. 45) and the control A second controllable pressure valve (46) that outputs hydraulic fluid of a signal pressure (DNC) that has been adjusted using (CR) as an original pressure; hydraulic fluid of the control pressure (CR); hydraulic fluid of the signal pressure (DRC) And a plurality of input ports through which hydraulic fluid of the signal pressure (DNC) can be input, and a plurality of output ports connected to the plurality of input ports, the signal pressure (DRC) and the signal pressure (DNC) And the switching valve (200) for switching the connection between the input port and the output port according to the position where the urging force of the elastic member balances, and the first output port (211) of the switching valve (200). A first final pressure regulating valve that outputs hydraulic oil of supply pressure (DR) for generating axial thrust to be applied to the drive pulley by reducing the line pressure (PH) based on the pressure of hydraulic oil 42) and the switching valve (20 ) To reduce the line pressure (PH) based on the pressure of the hydraulic oil output from the second output port (212), and supply pressure (for generating axial thrust applied to the driven pulley) ( DN) and a second final pressure regulating valve (43) that outputs hydraulic fluid, and the first and second adjustable pressure valves (45) and (46) have a signal pressure in response to an increase in input current. The switching valve (200) has an output characteristic that decreases the signal pressure in response to a decrease in the input current, and the switching valve (200) supplies a current to the first adjustable pressure valve (45) and the second adjustable pressure valve (46). Is input and the hydraulic fluid having a signal pressure equal to or higher than the specified pressure corresponding to the output characteristics is output, the hydraulic fluid having the input signal pressure (DRC) is output from the first output port and input. The hydraulic fluid of the signal pressure (DNC) is sent from the second output port The switching valve (200) switches the connection between the input port and the output port, and the input control pressure (CR) The hydraulic oil is output from the first output port and the second output port.

  According to the second aspect of the vehicle power transmission device of the present invention, the plurality of input ports (213-216) include hydraulic oil for the control pressure (CR) and hydraulic oil for the signal pressure (DRC). And the hydraulic oil of the signal pressure (DNC) can be input, and the first output port (211) is the hydraulic oil of the control pressure (CR) input from the input port or the signal pressure (DRC). The second output port (212) outputs the hydraulic fluid of the control pressure (CR) or the hydraulic fluid of the signal pressure (DNC) input from the input port. When output is possible, the current is input to the first adjustable pressure valve (45) and the second adjustable pressure valve (46), and hydraulic fluid having a signal pressure equal to or higher than a specified pressure corresponding to the output characteristics is output. The first output port (211) is The hydraulic fluid of the signal pressure (DRC) is output, the second output port (212) outputs the hydraulic fluid of the signal pressure (DNC), the current becomes non-energized, and the signal pressure exceeds the specified pressure. When the output is stopped, the switching valve (200) switches the connection between the input port and the output port, and the first output port (211) and the second output port (212) are connected to the control pressure. (CR) hydraulic oil is output.

  Moreover, according to the 3rd side surface of the vehicle power transmission device of this invention, when the said current input into the said 1st modulation pressure valve (45) and the 2nd modulation pressure valve (46) becomes a non-energization, The first final pressure regulating valve (42) is configured to reduce the line pressure (PH) based on the control pressure (CR) to generate an axial thrust to be applied to the drive pulley (DR). The hydraulic oil is output.

  Moreover, according to the 4th side surface of the vehicle power transmission device of this invention, when the said current input into the said 1st modulation pressure valve (45) and a 2nd modulation pressure valve (46) becomes a non-energization, The second final pressure regulating valve (43) is configured to reduce the line pressure (PH) based on the control pressure (CR) to generate an axial thrust to be applied to the driven pulley (DN). The hydraulic oil is output.

  According to the fifth aspect of the vehicle power transmission device of the present invention, the current command means (72) for generating a current command, the current based on the current command, the first adjustable pressure valve (45) and A current supply means (73) for supplying to the second adjustable pressure valve (46), and a hydraulic pressure for detecting the signal pressure of the hydraulic oil output from the first adjustable pressure valve (45) and the second adjustable pressure valve (46). Detection means (84, 86), and the current command means includes a storage unit for storing a table indicating the output characteristics of the first adjustable pressure valve (45) and the second adjustable pressure valve (46). And comparing the table indicating the output characteristics and the detected signal pressure to determine whether or not there is an abnormality in the signal pressure corresponding to the current command, and the first modulatable pressure valve (45) and the second One of the adjustable pressure valves (46) When there is an abnormality in the signal pressure, the current command means (72) and the current supply means (73) make the current supplied to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) zero. It controls to do.

  According to the sixth aspect of the vehicle power transmission device of the present invention, the current detection means (the current detection means) detects the value of the current flowing through the coils of the first adjustable pressure valve (45) and the second adjustable pressure valve (46). 82), and the current command means (72) compares the current command with the detected current value to determine whether there is an abnormality in the current value corresponding to the current command, When there is an abnormality in the current value of one of the adjustable pressure valve (45) and the second adjustable pressure valve (46), the current command means (72) and the current supply means (73) Control is performed so that the current supplied to the adjustable pressure valve (45) and the second adjustable pressure valve (46) is zero.

  According to the configuration of the first aspect to the sixth aspect of the present invention, it is possible to provide a vehicle power transmission device that can ensure a backup function during a failure and reduce current consumption. Become.

  Further, according to the configurations of the second to fourth aspects of the present invention, even when the predetermined signal pressure is not output from the first and second adjustable pressure valves during the failure, By generating axial thrust applied to the pulley based on the control pressure output from the two pressure regulating valves, it is possible to secure a backup function of the first and second adjustable pressure valves at the time of failure. become.

  Further, according to the configuration of the fifth aspect of the present invention, based on the detection result of the signal pressure of the hydraulic oil output from the first and second modulatable pressure valves, the first and second modulatable pressure valves and It becomes possible to determine whether or not there is an abnormality in the signal pressure in the adjustable pressure valve.

  In addition, according to the configuration of the sixth aspect of the present invention, the first modulable pressure valve and the second modulable pressure valve are based on the detection result of the current value flowing through the coils of the first modulable pressure valve and the second modulable pressure valve. It is possible to determine whether or not there is an abnormality.

The figure which shows the structure of the belt-type continuously variable transmission which concerns on embodiment. The figure which shows the structure of the hydraulic control circuit which concerns on embodiment. The figure explaining switching operation | movement of a backup valve. The figure explaining switching operation | movement of a backup valve. The figure explaining the structure of the control part contained in the power transmission device for vehicles which concerns on embodiment. The figure explaining the output characteristic of a regulator valve, and the output characteristic of a linear solenoid valve. The figure which illustrates the output characteristic of the linear solenoid valve of a prior art example.

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

<Configuration of vehicle power transmission device>
Hereinafter, the configuration of the vehicle power transmission device according to the embodiment will be described. The vehicle power transmission device is a belt that changes the transmission gear steplessly by changing the pulley width of the drive pulley 5 and the driven pulley 8 by changing the axial thrust applied to the drive pulley 5 and the driven pulley 8. And a hydraulic control circuit 40 that controls generation of axial thrust. The belt type continuously variable transmission 1 controlled by the hydraulic control circuit 40 will be described with reference to the drawings. As shown in FIG. 1, a belt type continuously variable transmission 1 is arranged in parallel with a transmission input shaft 2 connected via an output shaft of an engine ENG as a driving source and a fluid type torque converter 26. From the transmission counter shaft 3, the metal belt mechanism 4 disposed between the transmission input shaft 2 and the transmission counter shaft 3, and the forward / reverse switching mechanism 20 disposed on the transmission input shaft 2. Composed.

  FIG. 2 is a diagram showing the configuration of the hydraulic control circuit 40, and the belt-type continuously variable transmission 1 is based on the original pressure of hydraulic oil that is pumped through the oil path 32 by the hydraulic pump 31 of the hydraulic control circuit 40. Be controlled.

  The metal belt mechanism 4 is disposed on the transmission counter shaft 3 so as to rotate integrally with the drive pulley 5 (DR pulley) rotatably disposed on the transmission input shaft 2 and the transmission counter shaft 3. A driven pulley 8 (DN pulley) and a drive belt 5 (DR pulley) and a metal belt 7 wound around the driven pulley 8 (DN pulley).

  The drive pulley 5 (DR pulley) has a fixed DR pulley half 5A and a movable DR pulley half 5B. Here, the fixed-side DR pulley half 5A is arranged on the transmission input shaft 2 so as not to move in the axial direction. The movable-side DR pulley half 5B is configured to be movable relative to the fixed-side DR pulley half 5A in the axial direction. A DR-side cylinder chamber (DR cylinder chamber) 6 of the drive pulley 5 (DR pulley) is formed on the side of the movable DR pulley half 5B, and the hydraulic pressure supplied via the oil passage 56 of the hydraulic control circuit 40 is used. An axial thrust (DR pulley axial thrust) that moves the movable DR pulley half 5B in the axial direction is generated.

  The driven pulley 8 (DN pulley) includes a fixed-side DN pulley half 8A and a movable-side DN pulley half 8B. Here, the fixed-side DN pulley half 8A is arranged on the transmission countershaft 3 so as not to move in the axial direction. The movable-side DN pulley half 8B is configured to be movable relative to the fixed-side DN pulley half 8A in the axial direction. A DN-side cylinder chamber (DN cylinder chamber) 9 is formed on the side of the movable-side DN pulley half 8B, and the movable-side DN pulley half 8B is formed by the hydraulic pressure supplied through the oil passage 57 of the hydraulic control circuit 40. An axial thrust force (DN pulley axial thrust force) that moves the shaft in the axial direction is generated.

  The hydraulic control circuit 40 controls the hydraulic pressure supplied to the DR cylinder chamber 6 and the DN cylinder chamber 9 (hydraulic pressures DRC ′ and DNC ′ in FIG. 2), thereby setting an axial thrust that does not cause the metal belt 7 to slip. The pulley widths of the drive pulley 5 (DR pulley) and the driven pulley 8 (DN pulley) can be set variably. As a result, the belt-type continuously variable transmission 1 can continuously change the wrapping radius of the metal belt 7 around the pulleys 5 and 8 to control the speed ratio continuously (continuously).

  The forward / reverse switching mechanism 20 includes a planetary gear mechanism PGS, a forward clutch 24, and a reverse brake 25. The planetary gear mechanism PGS rotates and revolves a sun gear 21 coupled to the transmission input shaft 2, a ring gear 23 coupled to the fixed DR pulley half 5A, and a pinion 22a meshing with the sun gear 21 and the ring gear 23. It is comprised by the single pinion type | formula which consists of the carrier 22 to support.

  The reverse brake 25 is configured so that the carrier 22 can be fixedly held in the casing Ca. The forward clutch 24 is configured to be able to connect the sun gear 21 and the ring gear 23. When the forward clutch 24 is engaged, the sun gear 21, the carrier 22 and the ring gear 23 rotate integrally with the transmission input shaft 2, and the drive pulley 5 (DR pulley) is in the same direction (forward) as the transmission input shaft 2. Direction). On the other hand, when the reverse brake 25 is engaged, the carrier 22 is fixedly held in the casing Ca, and the ring gear 23 is driven in the reverse direction (reverse direction) to the sun gear 21. The planetary gear mechanism PGS can also be configured as a double pinion type. In this case, the stationary DR pulley half 5A may be coupled to the carrier, and the reverse brake may be provided on the ring gear.

  The power of the engine ENG is shifted through the metal belt mechanism 4 and the forward / reverse switching mechanism 20 and transmitted to the transmission countershaft 3. The power transmitted to the transmission countershaft 3 is transmitted to the differential mechanism 29 via the gears 27a, 27b, 28a, 28b, and is divided and transmitted from here to left and right wheels (not shown).

<Configuration of hydraulic control circuit>
Hereinafter, the hydraulic control circuit 40 included in the vehicle power transmission device of the embodiment will be described. As shown in FIG. 2, the hydraulic control circuit 40 includes a regulator valve 41 (first pressure regulating valve), a DR regulator valve 42 (first final pressure regulating valve), a DN regulator valve 43 (second final pressure regulating valve), a CR valve. 44 (second pressure regulating valve), four linear solenoid valves (electromagnetic valves) 45 to 48 (modulable pressure valves), a control valve 49, a manual valve 50, and a backup valve 200 (switching valve).

  The plurality of input ports (213 to 216) of the backup valve 200 are operated with hydraulic oil of the control pressure CR output from the CR valve 44 (second pressure regulating valve) and operation of the signal pressure DRC output from the DRC linear solenoid valve 45. Oil and hydraulic oil of signal pressure DNC output from the DNC linear solenoid valve 46 can be input.

  The first output port 211 that constitutes the plurality of output ports of the backup valve 200 can output the hydraulic fluid of the control pressure CR or the hydraulic fluid of the signal pressure DRC input from the input port. Further, the second output port 212 constituting the plurality of output ports of the backup valve 200 can output the hydraulic fluid of the control pressure CR or the hydraulic fluid of the signal pressure DNC input from the input port.

  The hydraulic oil pumped up from the oil tank by the hydraulic pump 31 driven by the engine ENG is pumped to the regulator valve 41 through the oil passage 32. The regulator valve 41 adjusts the discharge pressure of the hydraulic oil pumped from the hydraulic pump 31 to the line pressure PH. Further, the regulator valve 41 supplies hydraulic oil for lubricating the torque converter 26 via the oil passage 67.

  The hydraulic oil having the line pressure PH adjusted by the regulator valve 41 is supplied to the DR regulator valve 42 and the DN regulator valve 43 through the oil passage 51. Further, the hydraulic oil having the line pressure PH adjusted by the regulator valve 41 is supplied to the CR valve 44 via the oil passage 52. A part of the hydraulic fluid having the line pressure PH adjusted by the regulator valve 41 is fed back to the regulator valve 41. In FIG. 2, the hydraulic fluid fed back to the regulator valve 41 is indicated as PH '. In FIG. 2, in order to distinguish from the regulated line pressure PH, the pressure of the hydraulic oil fed back to the regulator valve 41 is PH ′, but both are the same pressure.

  The CR valve 44 reduces the line pressure PH of the hydraulic oil supplied from the oil passage 52 to generate a control pressure CR. The hydraulic fluid of the control pressure CR generated by the CR valve 44 is input to the four linear solenoid valves 45 to 48 and the input ports 214 and 216 of the backup valve 200 (switching valve) via the oil passage 53.

  Although not shown in detail, the DRC linear solenoid valve 45 is configured such that the spool valve is displaced according to the energization amount of the solenoid, and the DRC linear solenoid valve 45 is based on the control pressure CR generated by the CR valve 44 under reduced pressure. The valve 45 generates a signal pressure DRC corresponding to the energization amount, and supplies hydraulic oil having the signal pressure DRC to the backup valve 200 (switching valve) side through the oil passage 54. The output characteristics of the DRC linear solenoid valve 45 will be described in detail later with reference to FIG.

  The hydraulic fluid with the signal pressure DRC generated by the DRC linear solenoid valve 45 is input to the input port 213 of the backup valve 200 (switching valve) via the oil passage 63 branched from the oil passage 65. Further, the hydraulic oil having the signal pressure DRC is input to the input port of the regulator valve 41 via the oil passage 65.

  Although not shown in detail, the DNC linear solenoid valve 46 is configured such that the spool valve is displaced according to the energization amount of the solenoid, and the DNC linear solenoid valve is based on the control pressure CR generated by the CR valve 44 under reduced pressure. The valve 46 generates a signal pressure DNC corresponding to the energization amount, and supplies hydraulic oil having the signal pressure DNC to the backup valve 200 (switching valve) side through the oil passage 55. The output characteristics of the DNC linear solenoid valve 46 will be described in detail later with reference to FIG.

  The hydraulic fluid of the signal pressure DNC generated by the DNC linear solenoid valve 46 is input to the input port 215 of the backup valve 200 (switching valve) via the oil passage 64 branched from the oil passage 66. Further, the hydraulic oil having the signal pressure DNC is input to the input port of the regulator valve 41 through the oil passage 66.

  The hydraulic fluid of the signal pressure DRC and the hydraulic fluid of the signal pressure DNC supplied via the oil passages 54 and 55 act so as to oppose the urging force F of the elastic member 220 acting on the left side surface of the backup valve 200. To do. The output of the output ports 211 and 212 of the backup valve 200 (switching valve) is switched by switching the connection relationship between the input port and the output port according to the position where the urging force F is balanced with the signal pressure DRC and the signal pressure DNC. Is switched. FIG. 2 shows a state where the input port 213 and the output port 211 are connected, and shows a state where the input port 214 and the output port 211 are not connected. Similarly, the input port 215 and the output port 212 are connected, and the input port 216 and the output port 212 are not connected.

  In the backup valve 200 shown in FIG. 2, hydraulic fluid having a signal pressure DRC input from the input port 213 is output from the output port 211. In FIG. 2, in order to distinguish from the input hydraulic fluid of the signal pressure DRC, the hydraulic fluid signal pressure output from the output port 211 is DRC ′, but both are the same signal pressure. The hydraulic oil having the signal pressure DRC ′ output from the output port 211 is supplied to the DR regulator valve 42 via the oil passage 70.

  The DR regulator valve 42 supplied with the hydraulic fluid of the signal pressure DRC ′ reduces the line pressure PH to generate the supply pressure DR. The hydraulic oil having the supply pressure DR generated by the DR regulator valve 42 is supplied to the DR cylinder chamber 6 through the oil passage 56. With the supply of hydraulic oil at the supply pressure DR, an axial thrust (DR pulley axial thrust) that moves the movable DR pulley half 5B in the axial direction is generated.

  Further, in the backup valve 200 (switching valve) shown in FIG. 2, the hydraulic fluid of the signal pressure DNC input from the input port 215 is output from the output port 212. In FIG. 2, the signal pressure of the hydraulic fluid output from the output port 212 is DNC ′ in order to distinguish it from the hydraulic fluid of the input signal pressure DNC, but both are the same signal pressure. The hydraulic fluid having the signal pressure DNC ′ output from the output port 212 is supplied to the DN regulator valve 43 via the oil passage 71.

  The DN regulator valve 43 supplied with the hydraulic fluid of the signal pressure DNC ′ reduces the line pressure PH to generate the supply pressure DN. The hydraulic oil having the supply pressure DN generated by the DN regulator valve 43 is supplied to the DN cylinder chamber 9 through the oil passage 57. The supply of hydraulic oil at the supply pressure DN generates an axial thrust (DN pulley axial thrust) that moves the movable DN pulley half 8B in the axial direction.

  In this way, by controlling the energization amount to the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46, the signal pressures DRC ′ and DNC ′ of the hydraulic oil output from the output port of the backup valve 200 (switching valve) are controlled. It is possible to control. The generation of the supply pressures DR and DN can be controlled by reducing the line pressure PH based on the hydraulic oil signal pressures DRC ′ and DNC ′. The side pressures of the drive pulley 5 (DR pulley) and the driven pulley 8 (DN pulley) increase and decrease by the generation control of the supply pressure DR and the supply pressure DN, and the drive pulley 5 (DR pulley) and the driven pulley 8 (DN pulley). The pulley width changes, and the winding radius of the metal belt 7 is increased. As a result, the gear ratio for transmitting the output of the engine ENG to the drive wheels can be changed steplessly.

  The hydraulic oil having a signal pressure output from the output port 212 of the backup valve 200 (switching valve) is fed back to the regulator valve 41 via the oil passage 72. In the connection relationship between the input port 215 and the output port 212 shown in FIG. 2, the hydraulic fluid of the signal pressure DNC ′ is fed back to the regulator valve 41. Note that the hydraulic oil having a signal pressure fed back to the regulator valve 41 is not limited to the hydraulic oil having the signal pressure output from the output port 212, but the signal pressure (for example, the signal pressure DRC) output from the output port 211. ') Hydraulic oil may be fed back. In the configuration shown in FIG. 2, it is assumed that the hydraulic fluid of the signal pressure DNC ′ output from the output port 212 is fed back to the regulator valve 41 as an example.

  The hydraulic fluid of the signal pressure DRC input to the regulator valve 41 via the oil passage 65, the hydraulic fluid of the signal pressure DNC input via the oil passage 66, and the signal pressure output from the backup valve 200 DNC 'hydraulic fluid is fed back.

  Further, a part of the hydraulic oil having the line pressure PH adjusted by the regulator valve 41 is fed back to the regulator valve 41 as the hydraulic oil having the line pressure PH ′. The regulator valve 41 regulates the line pressure PH so that the line pressure PH ′ = the signal pressure DRC + the signal pressure DNC + the signal pressure DNC ′.

  A specific switching operation of the backup valve 200 will be described later in detail with reference to FIGS. 3 and 4.

  Although not shown in detail, the LCC linear solenoid valve 47 is configured such that the spool valve is displaced according to the energization amount to the solenoid. The LCC linear solenoid valve 47 generates a signal pressure LCC corresponding to the energization amount based on the control pressure CR generated by the CR valve 44, and supplies the hydraulic oil of the signal pressure LCC to the control valve 49 via the oil passage 58. Supply.

  The control valve 49 regulates the hydraulic fluid having the signal pressure LCC supplied via the oil passage 58 and supplies the regulated hydraulic fluid to the lockup clutch 26 a via the oil passage 59. Engagement and release of the lockup clutch 26a are controlled based on the regulated hydraulic fluid.

  Although not shown in detail, the CPC linear solenoid valve 48 is configured such that the spool valve is displaced according to the energization amount to the solenoid. The CPC linear solenoid valve 48 generates a signal pressure CPC corresponding to the energization amount based on the control pressure CR generated by the CR valve 44, and supplies the hydraulic oil of the signal pressure CPC via the oil passage 60 to the manual valve 50. To supply. The spool valve of the manual valve 50 moves according to the operation of a shift lever (not shown) by the driver.

  When the shift lever is operated to the D (forward) range, hydraulic oil is discharged from the reverse brake 25 and hydraulic pressure is supplied to the forward clutch 24 to engage the forward clutch 24. On the other hand, when the shift lever is operated to the R (reverse) range, the hydraulic oil is discharged from the forward clutch 24 and the hydraulic pressure is supplied to the reverse brake 25 so that the reverse brake 25 is engaged. Thus, the hydraulic fluid of the signal pressure CPC supplied from the CPC linear solenoid valve 48 is used for engagement / release control of the forward clutch 24 and the reverse brake 25.

(Switching operation of backup valve 200)
The switching operation of the backup valve 200 (switching valve) will be described with reference to FIGS. FIG. 3 shows a switching operation of the backup valve 200 (switching valve) when the hydraulic fluid with the signal pressure DRC is output from the DRC linear solenoid valve 45 and the hydraulic fluid with the signal pressure DNC is output from the DNC linear solenoid valve 46. FIG.

  The backup valve 200 (switching valve) includes a plurality of input ports capable of inputting hydraulic fluid of control pressure CR, hydraulic fluid of signal pressure DRC, and hydraulic fluid of signal pressure DNC, and a plurality of output ports connected to the plurality of input ports. And have. The backup valve 200 (switching valve) switches the connection between the input port and the output port according to a position where the signal pressure DRC and the signal pressure DNC are balanced with the urging force of the elastic member 220.

  In FIG. 3, the hydraulic fluid of the signal pressure DRC and the hydraulic fluid of the signal pressure DNC supplied through the oil passages 54 and 55 are urging force F of the elastic member 220 acting on the left side surface of the backup valve 200 (switching valve). Acts so as to face each other. The back-up valve at the equilibrium position where the hydraulic fluid of the signal pressure DRC and the hydraulic fluid of the signal pressure DNC and the biasing force F of the elastic member 220 balance (the biasing force F (biasing pressure) of the elastic member 220 = signal pressure DRC + signal pressure DNC) The position of 200 (switching valve) is maintained.

  When the hydraulic oil signal pressure DRC and the signal pressure DNC decrease and the urging force F of the elastic member 220 (biasing pressure)> signal pressure DRC + signal pressure DNC, the backup valve 200 (switching valve) Due to the urging force F (biasing pressure), the sheet moves in the direction pushed from left to right on the paper surface of FIG. The connection relationship between the input port and the output port is switched according to the equilibrium position where the urging force F (the urging pressure) is balanced with the signal pressure DRC and the signal pressure DNC. In the position of the backup valve 200 (switching valve) shown in FIG. 3, the input port 241 and the output port 221 are connected as to the connection relationship between the input port and the output port. Further, the input port 245 and the output port 225 are connected. The input port 249 and the output port 229 are connected.

(Input to backup valve 200)
Here, the input port 240 of the backup valve 200 (switching valve) is an input port corresponding to the input port 214 of FIG. 2, and hydraulic oil of the control pressure CR is input through the oil passage 53. An input port 241 of the backup valve 200 (switching valve) is an input port corresponding to the input port 213 in FIG. 2, and hydraulic fluid with a signal pressure DRC is input through the oil passage 63.

  An input port 244 of the backup valve 200 (switching valve) is an input port corresponding to the input port 216 in FIG. 2, and hydraulic fluid of the control pressure CR is input through the oil passage 53. An input port 245 of the backup valve 200 (switching valve) is an input port corresponding to the input port 215 in FIG. 2, and hydraulic fluid having a signal pressure DNC is input through the oil passage 64.

  An input port 248 of the backup valve 200 (switching valve) is an input port (not shown) in FIG. 2, and hydraulic oil of the control pressure CR is input through the oil passage 53. An input port 249 of the backup valve 200 (switching valve) is an input port (not shown) in FIG. 2, and hydraulic fluid of the signal pressure DNC is input through the oil passage 64.

(Output from backup valve 200)
An output port 221 of the backup valve 200 (switching valve) is an output port corresponding to the output port 211 in FIG. 2 and is connected to the input port 241. The hydraulic fluid of the signal pressure DRC input from the input port 241 is output from the output port 221 (signal pressure DRC ′). The hydraulic fluid having the signal pressure DRC ′ output from the output port 221 is supplied to the DR regulator valve 42 via the oil passage 70. In addition, in order to distinguish from the hydraulic fluid of the input signal pressure DRC, the signal pressure of the hydraulic fluid output from the output port 221 is set to DRC ', but both are the same signal pressure. The DR regulator valve 42 to which the hydraulic oil having the signal pressure DRC ′ is supplied reduces the line pressure PH based on the signal pressure DRC ′ to generate the supply pressure DR. The hydraulic oil having the supply pressure DR generated by the DR regulator valve 42 is supplied to the DR cylinder chamber 6 through the oil passage 56. The supply of hydraulic oil at the supply pressure DR generates an axial thrust that moves the movable DR pulley half 5B in the axial direction.

  An output port 225 of the backup valve 200 (switching valve) is an output port corresponding to the output port 212 of FIG. 2 and is connected to the input port 245. The hydraulic fluid of the signal pressure DNC input from the input port 245 is output from the output port 225 (hydraulic fluid of the signal pressure DNC ′). The hydraulic fluid of the signal pressure DNC ′ output from the output port 225 is supplied to the DN regulator valve 43 via the oil passage 71. The DN regulator valve 43 to which the hydraulic oil having the signal pressure DNC ′ is supplied reduces the line pressure PH based on the signal pressure DNC ′ to generate the supply pressure DN. The hydraulic oil having the supply pressure DN generated by the DN regulator valve 43 is supplied to the DN cylinder chamber 9 through the oil passage 57. The supply of hydraulic oil at the supply pressure DN generates axial thrust that moves the movable DN pulley half 8B in the axial direction.

  The output port 229 of the backup valve 200 (switching valve) is an output port not shown in FIG. 2 and is connected to the input port 249. The hydraulic fluid of the signal pressure DNC input from the input port 249 is output from the output port 229 (hydraulic fluid of the signal pressure DNC ′). The hydraulic fluid of the signal pressure DNC ′ output from the output port 229 is fed back to the regulator valve 41 via the oil passage 72. In addition, in order to distinguish from the input signal pressure DNC feedback, the signal pressure of the hydraulic fluid output from the output port 225 and the output port 229 is DNC ', but both are the same signal pressure.

(Signal pressure DRC and signal pressure DNC are zero: backup operation state)
Next, the operation of the backup valve 200 (switching valve) when the current input to each linear solenoid valve becomes zero (non-energized) and the signal pressure output from each linear solenoid valve becomes zero is shown in FIG. This will be described by reference. FIG. 4 shows the operation of the backup valve 200 (switching valve) when the signal pressure DRC output from the DRC linear solenoid valve 45 becomes zero and the signal pressure DNC output from the DNC linear solenoid valve 46 becomes zero. It is a figure explaining. In FIG. 4, the hydraulic fluid having the signal pressure DRC and the hydraulic fluid having the signal pressure DNC that are zero are indicated by broken lines.

  In FIG. 4, the hydraulic fluid of the signal pressure DRC and the hydraulic fluid of the signal pressure DNC supplied via the oil passages 54 and 55 become zero, and the urging force F of the elastic member 220> the signal pressure DRC + the signal pressure DNC. In this case, the backup valve 200 is urged by the urging force F of the elastic member 220 and moves from the equilibrium state shown in FIG. 3 to the direction pushed from left to right on the paper surface of FIG. The connection relationship between the input port and the output port is switched according to the movement of the backup valve 200 (switching valve). In the position of the backup valve 200 (switching valve) shown in FIG. 4, the input port 242 and the output port 223 are connected in the connection relationship between the input port and the output port. Further, the input port 246 and the output port 227 are connected. Then, the input port 250 and the output port 231 are connected.

(Input to backup valve 200)
Here, the input port 242 of the backup valve 200 (switching valve) is an input port corresponding to the input port 214 of FIG. 2, and hydraulic fluid of the control pressure CR is input through the oil passage 53. The input port 243 of the backup valve 200 (switching valve) is an input port corresponding to the input port 213 in FIG. 2, but since the hydraulic oil signal pressure DRC is zero, the input port 243 via the oil path 63 is input. The hydraulic fluid of the signal pressure DRC is not input.

  An input port 246 of the backup valve 200 (switching valve) is an input port corresponding to the input port 216 in FIG. 2, and hydraulic oil with a control pressure CR is input through the oil passage 53. The input port 247 of the backup valve 200 (switching valve) is an input port corresponding to the input port 215 in FIG. 2, but since the hydraulic oil signal pressure DNC is zero, the input port 247 via the oil path 64 is input. The hydraulic fluid of the signal pressure DNC is not input.

  An input port 250 of the backup valve 200 (switching valve) is an input port (not shown) in FIG. 2, and hydraulic oil of the control pressure CR is input through the oil passage 53. The input port 251 of the backup valve 200 (switching valve) is an input port not shown in FIG. Since the hydraulic oil signal pressure DNC is zero, the hydraulic oil of the signal pressure DNC is not input to the input port 251 via the oil passage 64.

(Output from backup valve 200)
An output port 223 of the backup valve 200 (switching valve) is an output port corresponding to the output port 211 in FIG. 2 and is connected to the input port 242. The hydraulic fluid having the control pressure CR input from the input port 242 is output from the output port 223 (the hydraulic fluid having the control pressure CR ′). The hydraulic oil having the control pressure CR ′ output from the output port 223 is supplied to the DR regulator valve 42 via the oil passage 70. In addition, in order to distinguish from the input hydraulic fluid of the control pressure CR, the control of the hydraulic fluid output from the output port 223 is CR ′, but both are the same control pressure. The DR regulator valve 42 supplied with the hydraulic oil of the control pressure CR ′ reduces the line pressure PH to generate the supply pressure DR. The hydraulic oil having the supply pressure DR generated by the DR regulator valve 42 is supplied to the DR cylinder chamber 6 through the oil passage 56. The supply of hydraulic oil at the supply pressure DR generates an axial thrust that moves the movable DR pulley half 5B in the axial direction.

  An output port 227 of the backup valve 200 (switching valve) is an output port corresponding to the output port 212 in FIG. 2 and is connected to the input port 246. The hydraulic fluid of the control pressure CR input from the input port 246 is output from the output port 227 (the hydraulic fluid of the control pressure CR ′). The hydraulic fluid having the control pressure CR ′ output from the output port 227 is supplied to the DN regulator valve 43 via the oil passage 71. The DN regulator valve 43 supplied with the hydraulic oil of the control pressure CR ′ reduces the line pressure PH to generate the supply pressure DN. The hydraulic oil having the supply pressure DN generated by the DN regulator valve 43 is supplied to the DN cylinder chamber 9 through the oil passage 57. The supply of hydraulic oil at the supply pressure DN generates axial thrust that moves the movable DN pulley half 8B in the axial direction.

  An output port 231 of the backup valve 200 (switching valve) is an output port (not shown) in FIG. 2 and is connected to the input port 249. The hydraulic fluid of the control pressure CR input from the input port 249 is output from the output port 231 (the hydraulic fluid of the control pressure CR ′). The hydraulic fluid having the control pressure CR ′ output from the output port 231 is fed back to the regulator valve 41 via the oil passage 72. In addition, in order to distinguish from the input hydraulic fluid of the control pressure CR, the control pressure of the hydraulic fluid output from the output port 227 and the output port 231 is CR ′, but both are the same signal pressure.

(Characteristics of linear solenoid valve)
The output characteristics of the DR regulator valve 42 and the DN regulator valve 43 and the output characteristics of the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46 will be described with reference to FIG.

  FIG. 6A shows, as output characteristics of the DR regulator valve 42, the hydraulic oil signal pressure DRC ′ (DRC ′ pressure) input to the DR regulator valve 42 and the hydraulic oil supply pressure output from the DR regulator valve 42. It is a figure which shows the relationship of DR (DR pressure). FIG. 6B shows, as output characteristics of the DRC linear solenoid valve 45, a current input to the DRC linear solenoid valve 45 and a signal pressure DRC (DRC pressure) of the hydraulic fluid output from the DRC linear solenoid valve 45. It is a figure which shows the relationship.

  As shown in FIG. 6A, in a region 603 where the signal pressure DRC ′ is low, hydraulic oil having a constant supply pressure 601 (fixed pressure) is output from the DR regulator valve 42 as the supply pressure DR.

  In the output characteristics of the DRC linear solenoid valve 45 corresponding to the region 603, as shown in FIG. 6B, the current input to the DRC linear solenoid valve 45 is zero in the region 605, and the signal pressure from the DRC linear solenoid valve 45 is DRC is not output. That is, when the current input to the DRC linear solenoid valve 45 is de-energized, hydraulic fluid (signal pressure DRC) having a signal pressure equal to or higher than the specified pressure is not output from the DRC linear solenoid valve 45 (region 605). At this time, the control pressure CR ′ is output from the backup valve 200 (switching valve) instead of the signal pressure DRC ′ corresponding to the signal pressure DRC (FIG. 4), and the hydraulic fluid of the output control pressure CR ′ is output. Input to the DR regulator valve 42 (backup operation state).

  When the input current to the DRC linear solenoid valve 45 becomes zero (non-energized) (region 605), the DR regulator valve 42 reduces the line pressure PH based on the control pressure CR ′ of the hydraulic oil, and supplies the supply pressure. A constant supply pressure 601 (fixed pressure) is generated as DR (region 603). The hydraulic oil having the supply pressure DR (fixed pressure) generated by the DR regulator valve 42 is supplied to the DR cylinder chamber 6 through the oil passage 56. With the supply of hydraulic oil at a supply pressure DR (fixed pressure), axial thrust (DR pulley axial thrust) that moves the movable DR pulley half 5B in the axial direction is generated.

  Further, in the output characteristic 609 of the DR regulator valve 42 corresponding to the region 604, the supply pressure DR also increases / decreases according to the increase / decrease of the hydraulic oil signal pressure DRC '. In the output characteristics of the DRC linear solenoid valve 45 corresponding to the region 604, the signal pressure DRC also increases / decreases as the current input to the DRC linear solenoid valve 45 increases / decreases as shown in FIG. That is, when a current is input to the DRC linear solenoid valve 45, hydraulic oil having a signal pressure equal to or higher than a specified pressure corresponding to the output characteristics is output from the DRC linear solenoid valve 45 (region 611). In the region 611 in FIG. 6B, the relationship between the current and the signal pressure is an output characteristic indicated by a linear function with a positive slope. In other words, the relationship between the current and the signal pressure has an output characteristic in which the signal pressure is increased as the input current increases and the signal pressure is decreased as the input current decreases (positive logic output characteristics). The output characteristics of the positive logic shown in FIG. 6B are the increase and decrease of the current and the increase and decrease of the signal pressure compared with the output characteristics (reverse logic output characteristics) of the conventional linear solenoid valve described in FIG. This is an output characteristic whose relationship is reversed. In the usage state from the start of the vehicle to the high-speed traveling, the hydraulic pressure (signal pressure) that is regularly used is frequently used on the low pressure side. In the positive logic output characteristic, the signal pressure in a region where current consumption is small is frequently used, so that the current consumption can be reduced as compared with the prior art.

  In the region 611, when the DRC linear solenoid valve 45 operates, the backup valve 200 (switching valve) outputs the signal pressure DRC ′ corresponding to the signal pressure DRC instead of the control pressure CR ′, and the output signal The hydraulic oil having the pressure DRC ′ is input to the DR regulator valve 42 (normal operation state).

  The DR regulator valve 42 reduces the line pressure PH based on the signal pressure DRC ′ to generate hydraulic oil having a supply pressure DR corresponding to the hydraulic oil having the signal pressure DRC ′. The hydraulic fluid of the supply pressure DR generated here corresponds to the signal pressure DRC that increases and decreases according to the increase and decrease of the current input to the DRC linear solenoid valve 45, and the supply pressure DR in the region 604 is a variable pressure. . The hydraulic oil having the supply pressure DR (variable pressure) generated by the DR regulator valve 42 is supplied to the DR cylinder chamber 6 through the oil passage 56. With the supply of hydraulic oil at a supply pressure DR (variable pressure), axial thrust (DR pulley axial thrust) that moves the movable DR pulley half 5B in the axial direction is generated.

  As shown in FIGS. 6A and 6B, in the backup operation state corresponding to the region 603, the movable side DR is supplied by supplying hydraulic oil at a supply pressure DR (fixed pressure) based on the hydraulic oil control pressure CR ′. An axial thrust that moves the pulley half 5B in the axial direction can be generated. Further, in the normal operation state corresponding to the region 604, the axial direction in which the movable-side DR pulley half 5B is moved in the axial direction by supplying hydraulic oil with a supply pressure DR (variable pressure) based on the hydraulic oil with the signal pressure DRC ′. Thrust can be generated.

  The above description has been given of the DR regulator valve 42 and the DRC linear solenoid valve 45, but the same applies to the DN regulator valve 43 and the DNC linear solenoid valve 46.

  FIG. 6C shows, as output characteristics of the DN regulator valve 43, the hydraulic oil signal pressure DNC ′ (DNC ′ pressure) input to the DN regulator valve 43 and the hydraulic oil supply pressure output from the DN regulator valve 43. It is a figure which shows the relationship of DN (DN pressure). FIG. 6D shows the output characteristics of the DNC linear solenoid valve 46. The current input to the DNC linear solenoid valve 46 and the hydraulic oil signal pressure DNC (DNC pressure) output from the DNC linear solenoid valve 46 are shown in FIG. It is a figure which shows the relationship.

  As shown in FIG. 6C, hydraulic oil having a constant supply pressure 602 (fixed pressure) is output from the DN regulator valve 43 as the supply pressure DN in a region 606 where the signal pressure DNC ′ is low.

  In the output characteristics of the DNC linear solenoid valve 46 corresponding to the region 606, the current input to the DNC linear solenoid valve 46 is zero in the region 608 as shown in FIG. DNC is not output. That is, when the current input to the DNC linear solenoid valve 46 is de-energized, hydraulic oil (signal pressure DNC) having a signal pressure equal to or higher than the specified pressure is not output from the DNC linear solenoid valve 46 (region 608). At this time, the control pressure CR ′ is output from the backup valve 200 (switching valve) instead of the signal pressure DNC ′ corresponding to the signal pressure DNC, and the hydraulic fluid of the output control pressure CR ′ is output to the DN regulator valve 43. Is input (backup operation status).

  When the input current to the DNC linear solenoid valve 46 becomes zero (non-energized) (region 608), the DN regulator valve 43 reduces the line pressure PH based on the control pressure CR ′ of the hydraulic oil, and supplies the supply pressure. A constant supply pressure 602 (fixed pressure) is generated as DN (area 606). The hydraulic oil having the supply pressure DN (fixed pressure) generated by the DN regulator valve 43 is supplied to the DN cylinder chamber 9 via the oil passage 57. With the supply of hydraulic fluid of supply pressure DN (fixed pressure), axial thrust (DN pulley axial thrust) that moves the movable DN pulley half 8B in the axial direction is generated.

  Further, in the output characteristic 610 of the DN regulator valve 43 corresponding to the region 607, the supply pressure DN also increases / decreases in accordance with the increase / decrease of the hydraulic oil signal pressure DNC '. In the output characteristics of the DNC linear solenoid valve 46 corresponding to the region 607, the signal pressure DNC also increases / decreases as the current input to the DNC linear solenoid valve 46 increases / decreases as shown in FIG. 6 (d). That is, when a current is input to the DNC linear solenoid valve 46, hydraulic oil having a signal pressure equal to or higher than a specified pressure corresponding to the output characteristics is output from the DNC linear solenoid valve 46 (region 612). In the region 612 of FIG. 6D, the relationship between the current and the signal pressure is an output characteristic indicated by a linear function with a positive slope. In other words, the relationship between the current and the signal pressure has an output characteristic in which the signal pressure is increased as the input current increases and the signal pressure is decreased as the input current decreases (positive logic output characteristics). At this time, instead of the control pressure CR ′, a signal pressure DNC ′ corresponding to the signal pressure DNC is output from the backup valve 200 (switching valve), and the hydraulic fluid of the output signal pressure DNC ′ is output to the DN regulator valve 43. (Normal operation state).

  The DN regulator valve 43 reduces the line pressure PH based on the signal pressure DNC ′ to generate hydraulic oil with a supply pressure DN corresponding to the hydraulic oil with the signal pressure DNC ′. The hydraulic fluid of the supply pressure DN generated here corresponds to the signal pressure DNC that increases or decreases according to the increase or decrease of the current input to the DNC linear solenoid valve 46, and the supply pressure DN in the region 607 is a variable pressure. . The hydraulic oil having the supply pressure DN (variable pressure) generated by the DN regulator valve 43 is supplied to the DN cylinder chamber 9 via the oil passage 57. With the supply of hydraulic fluid of supply pressure DN (variable pressure), axial thrust (DN pulley axial thrust) that moves the movable DN pulley half 8B in the axial direction is generated.

  As shown in FIGS. 6C and 6D, in the backup operation state corresponding to the region 606, the movable side DN is supplied by supplying the hydraulic oil with the supply pressure DN (fixed pressure) based on the control pressure CR ′ of the hydraulic oil. An axial thrust that moves the pulley half 8B in the axial direction can be generated. Further, in the normal operation state corresponding to the region 607, the axial direction in which the movable DN pulley half body 8B is moved in the axial direction by supplying hydraulic oil with a supply pressure DN (variable pressure) based on the signal pressure DNC ′ of the hydraulic oil. Thrust can be generated.

  When current is input to the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46 and hydraulic fluid with a signal pressure higher than a specified pressure corresponding to the output characteristics is output, the backup valve 200 (switching valve) receives the input signal. The hydraulic oil having the pressure DRC is output from the output port 211 (signal pressure DRC ′), and the hydraulic oil having the input signal pressure DNC is output from the output port 212 (signal pressure DNC ′).

  On the other hand, when the current input to the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46 is de-energized and the signal pressure is not output more than the specified pressure, the backup valve 200 (switching valve) has an input port and an output port. And the hydraulic fluid of the input control pressure CR is output from the output port 211 and the output port 212.

<Configuration of control unit>
Next, the control unit 80 included in the vehicle power transmission device of the present embodiment will be described. As shown in FIG. 5, the control unit 80 is an electronic circuit configured by a CPU or the like (not shown), and includes a current command unit 81 and a current supply unit 83. The current command unit 81 generates and outputs a current command for controlling the linear solenoid valve. Various signals such as an engine rotation signal, an engine throttle opening signal, and a vehicle speed signal are input to the control unit 80, and the current command unit 81 generates a current command based on the various signals.

(Control in normal operation state)
The current supply unit 83 can supply a current having a current value corresponding to the current command input from the current command unit 81 to each solenoid coil of the linear solenoid valves 45 to 48. The current supply unit 83 is a transistor, for example, and is connected to a power source (not shown). FIG. 5 exemplarily shows a DRC linear solenoid valve 45 and a DNC linear solenoid valve 46 as linear solenoid valves. The current supply unit 83 can supply current corresponding to the current command to the LCC linear solenoid valve 47 and the CPC linear solenoid valve 48 as well. In the following description, the function of the control unit 80 will be described using the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46 as representative examples as examples of the linear solenoid valve.

  Based on the current command output from the current command unit 81, the current supply unit 83 supplies a current having a current value corresponding to the current command to each solenoid coil of the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46.

  Based on the current supplied by the current supply unit 83, the DRC linear solenoid valve 45 outputs hydraulic oil having a signal pressure DRC. The relationship between the current input to the DRC linear solenoid valve 45 and the hydraulic oil signal pressure DRC is as shown in FIG. Further, based on the current supplied by the current supply unit 83, the DNC linear solenoid valve 46 outputs hydraulic fluid having a signal pressure DNC. The relationship between the current input to the DNC linear solenoid valve 46 and the hydraulic oil signal pressure DNC is as shown in FIG.

(Supply pressure control when the current detection result is abnormal)
The control of the supply pressure DR and the supply pressure DN when there is an abnormality in the current detection result as the backup operation state will be described. The control unit 80 is connected to a current detection unit 82, and the current detection unit 82 detects a current value that actually flows through each solenoid coil of the DRC linear solenoid valve 45 and the DNC linear solenoid valve 46. The current detection unit 82 inputs this detection result to the current command unit 81.

  The current command unit 81 determines whether the current value input from the current detection unit 82 is a current value corresponding to the current command. When a current value corresponding to the generated current command is input from the current detection unit 82, the current command unit 81 outputs a current command based on various signals such as an engine rotation signal, an engine throttle opening signal, and a vehicle speed signal. Generate.

  On the other hand, a current value different from the current command is detected by the current detection unit 82 from the solenoid coil of any one of the plurality of linear solenoid valves, and is input from the current detection unit 82 to the current command unit 81. In the case where the current value has been detected, the current command unit 81 determines that an abnormality has occurred in the current value, and outputs a current command for setting the current value to zero. The current supply unit 83 sets the current supply to all the linear solenoid valves to zero based on this current command. In the linear solenoid valve, the input current becomes zero corresponding to a region 605 in FIG. 6B and a region 608 in FIG. 6D. When an abnormality in the current value is detected in any one of the linear solenoid valves, the current command unit 81 and the current supply unit 83 perform control so that the current input to the linear solenoid valve is zero. By the current control of the current command unit 81 and the current supply unit 83, the hydraulic control circuit 40 is a hydraulic fluid having a constant supply pressure 601 (fixed pressure) as the supply pressure DR for controlling the movement of the movable DR pulley half 5B. Is output from the DR regulator valve 42. The hydraulic oil is supplied to the DR cylinder chamber 6 through the oil passage 56.

  Further, the hydraulic control circuit 40 outputs from the DN regulator valve 43 hydraulic oil having a constant supply pressure 602 (fixed pressure) as the supply pressure DN for controlling the movement of the movable DN pulley half 8B. The hydraulic oil is supplied to the DN cylinder chamber 9 through the oil passage 57.

  In addition to the case where the current is not energized due to the failure of the linear solenoid valve, when the failure of other devices constituting the hydraulic control circuit 40 is detected, the control unit 80 causes the backup valve 200 (switching). As a fail action for switching the valve, it is possible to control so that the current input to the linear solenoid valve is zero.

(Control of supply pressure when there is an abnormality in the hydraulic pressure detection result)
The control of the supply pressures DR and DN when there is an abnormality in the detection result of the signal pressure as the backup operation state will be described. The control unit 80 is connected to the DRC hydraulic pressure detection unit 84 and the DNC hydraulic pressure detection unit 86. The DRC hydraulic pressure detection unit 84 detects the hydraulic oil signal pressure DRC output from the DRC linear solenoid valve 45, and inputs the detection result to the current command unit 81. The DNC oil pressure detection unit 86 detects the hydraulic oil signal pressure DNC output from the DNC linear solenoid valve 46 and inputs the detection result to the current command unit 81.

  The current command unit 81 of the control unit 80 stores, for example, a table showing output characteristics as shown in FIGS. 6B and 6D in a storage unit (memory) (not shown). The current command unit 81 compares the stored output characteristic table with the signal pressure (DRC, DNC) input from the DRC hydraulic pressure detection unit 84 and the DNC hydraulic pressure detection unit 86, and a signal corresponding to the current command. The presence or absence of an abnormality in the pressure (DRC, DNC) is determined. For example, when the input signal pressure (DRC, DNC) exceeds a predetermined allowable error range, the current command unit 81 determines that the input signal pressure (DRC, DNC) is an abnormal value.

  Alternatively, when the current command unit 81 outputs a current command so as to generate a current, but the signal pressure (DRC, DNC) corresponding to the current command is zero, the input signal The current command unit 81 determines that the pressure (DRC, DNC) is an abnormal value.

  In any one of the linear solenoid valves, when it is determined that the signal pressure is an abnormal value, the current command unit 81 and the current supply unit 83 control the current input to all the linear solenoid valves to be zero. . By the current control of the current command unit 81 and the current supply unit 83, the hydraulic control circuit 40 is a hydraulic fluid having a constant supply pressure 601 (fixed pressure) as the supply pressure DR for controlling the movement of the movable DR pulley half 5B. Is output from the DR regulator valve 42. The hydraulic oil is supplied to the DR cylinder chamber 6 through the oil passage 56.

  Further, the hydraulic control circuit 40 outputs from the DN regulator valve 43 hydraulic oil having a constant supply pressure 602 (fixed pressure) as the supply pressure DN for controlling the movement of the movable DN pulley half 8B. The hydraulic oil is supplied to the DN cylinder chamber 9 through the oil passage 57.

  In the embodiment, the belt-type continuously variable transmission 1 has been described as a configuration controlled by the hydraulic control circuit 40. However, the transmission controlled by the hydraulic control circuit 40 is not limited to the belt-type continuously variable transmission 1, and may be a continuously variable transmission having another known configuration, a stepped transmission, or the like. According to the configuration of the present embodiment, it is possible to provide a vehicle power transmission device that can ensure a backup function during a failure and reduce current consumption.

1: belt type continuously variable transmission, 5: DR pulley, 6: DR cylinder chamber,
8: DN pulley, 9: DN cylinder chamber, 40 ... hydraulic control circuit,
42 ... DR regulator valve, 43 ... DN regulator valve,
45 ... DRC linear solenoid valve, 46 ... DNC linear solenoid valve

Claims (6)

A belt-type continuously variable transmission that changes the gear ratio steplessly by changing the pulley width of the drive pulley and the driven pulley by changing the axial thrust applied to the drive pulley and the driven pulley, and the shaft A vehicle power transmission device having a hydraulic control circuit (40) for controlling generation of directional thrust, wherein the hydraulic control circuit (40) includes:
A pump (31) for supplying hydraulic oil;
A first pressure regulating valve (41) for regulating the discharge pressure of the hydraulic oil to a line pressure (PH);
A second pressure regulating valve (44) that outputs hydraulic fluid of a control pressure (CR) that is regulated using the line pressure (PH) as a source pressure;
A first adjustable pressure valve (45) that outputs hydraulic fluid of a signal pressure (DRC) that is regulated using the control pressure (CR) as an original pressure;
A second adjustable pressure valve (46) that outputs hydraulic fluid of a signal pressure (DNC) that is regulated using the control pressure (CR) as an original pressure;
A plurality of input ports capable of inputting hydraulic oil of the control pressure (CR), hydraulic oil of the signal pressure (DRC) and hydraulic oil of the signal pressure (DNC), and a plurality of outputs connected to the plurality of input ports A switching valve (200) for switching the connection between the input port and the output port according to a position where the signal pressure (DRC) and the signal pressure (DNC) are balanced with the biasing force of the elastic member ,
Based on the pressure of the hydraulic oil output from the first output port (211) of the switching valve (200), the line pressure (PH) is reduced to generate axial thrust applied to the drive pulley. A first final pressure regulating valve (42) that outputs hydraulic oil having a supply pressure (DR) of
Based on the pressure of the hydraulic oil output from the second output port (212) of the switching valve (200), the line pressure (PH) is reduced to generate an axial thrust applied to the driven pulley. A second final pressure regulating valve (43) that outputs hydraulic oil at a supply pressure (DN) for
The first adjustable pressure valve (45) and the second adjustable pressure valve (46) have output characteristics that increase the signal pressure in response to an increase in input current and decrease the signal pressure in response to a decrease in input current. ,
The switching valve (200)
In the case where current is input to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) and hydraulic fluid having a signal pressure equal to or higher than a specified pressure corresponding to the output characteristics is output, the input signal pressure (DRC) hydraulic oil is output from the first output port, and the input hydraulic fluid of the signal pressure (DNC) is output from the second output port;
When the current becomes non-energized and the signal pressure is not output more than a specified pressure, the switching valve (200) switches the connection between the input port and the output port, and the input hydraulic fluid of the control pressure (CR) is supplied. Output from the first output port and the second output port. A vehicular power transmission device. The plurality of input ports (213-216) can input hydraulic fluid of the control pressure (CR), hydraulic fluid of the signal pressure (DRC), and hydraulic fluid of the signal pressure (DNC),
The first output port (211) can output hydraulic fluid of the control pressure (CR) or hydraulic fluid of the signal pressure (DRC) input from the input port,
The second output port (212) can output hydraulic fluid of the control pressure (CR) or hydraulic fluid of the signal pressure (DNC) input from the input port,
When the current is input to the first modulatable pressure valve (45) and the second modulatable pressure valve (46) and hydraulic fluid having a signal pressure higher than a specified pressure corresponding to the output characteristics is output, the first output The port (211) outputs hydraulic fluid of the signal pressure (DRC), the second output port (212) outputs hydraulic fluid of the signal pressure (DNC),
When the current becomes non-energized and the signal pressure is not output more than a specified pressure, the switching valve (200) switches the connection between the input port and the output port, and the first output port (211) and the The power transmission device for a vehicle according to claim 1, wherein the second output port (212) outputs hydraulic oil of the control pressure (CR). When the current input to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) is not energized,
The first final pressure regulating valve (42) is configured to reduce the line pressure (PH) based on the control pressure (CR) to generate an axial thrust to be applied to the drive pulley (DR). The vehicle power transmission device according to claim 1, wherein the hydraulic oil is output. When the current input to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) is not energized,
The second final pressure regulating valve (43) is configured to reduce the line pressure (PH) based on the control pressure (CR) to generate an axial thrust to be applied to the driven pulley (DN). The vehicle power transmission device according to claim 1, wherein the hydraulic oil is output. Current command means (72) for generating a current command;
Current supply means (73) for supplying current to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) based on the current command;
Hydraulic pressure detecting means (84, 86) for detecting the signal pressure of the hydraulic oil output from the first adjustable pressure valve (45) and the second adjustable pressure valve (46);
The current command means has a storage unit for storing a table indicating the output characteristics of the first adjustable pressure valve (45) and the second adjustable pressure valve (46),
Compare the table showing the output characteristics and the detected signal pressure, determine the presence or absence of abnormality in the signal pressure corresponding to the current command,
If any one of the signal pressures of the first modulable pressure valve (45) and the second modulable pressure valve (46) is abnormal, the current command means (72) and the current supply means (73) 5. The vehicle according to claim 1, wherein the current supplied to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) is controlled to be zero. 6. Power transmission device. Current detection means (82) for detecting a current value flowing through the coils of the first and second adjustable pressure valves (45) and (46);
The current command means (72) compares the current command with the detected current value to determine whether there is an abnormality in the current value corresponding to the current command,
When there is an abnormality in the current value of one of the first adjustable pressure valve (45) and the second adjustable pressure valve (46), the current command means (72) and the current supply means (73) 6. The vehicle power transmission device according to claim 5, wherein a current supplied to the first adjustable pressure valve (45) and the second adjustable pressure valve (46) is controlled to be zero.

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