JP6245219B2 - Automatic transmission with rotary valve and rotary valve - Google Patents

Description

  The present invention relates to an automatic transmission with a rotary valve and a rotary valve mounted on a vehicle, and belongs to the technical field of an automatic transmission for a vehicle.

  An automatic transmission mounted on a vehicle generally includes a transmission mechanism having a plurality of planetary gear sets (planetary gear mechanisms) and a plurality of frictional engagement elements such as clutches and brakes, and selectively engages these frictional engagement elements. Thus, the power transmission path passing through each planetary gear set is switched to achieve a predetermined gear position according to the driving state of the vehicle.

  For example, in Patent Document 1, a rotary valve that switches between supply and discharge of hydraulic pressure to a plurality of friction engagement elements is used, and supply and discharge of hydraulic pressure to a plurality of friction engagement elements is performed by rotating a valve body according to a driving state of the vehicle. An automatic transmission is disclosed in which a plurality of frictional engagement elements are controlled to be switched to achieve a predetermined shift speed.

Japanese Patent Publication No. 8-20007

  In the automatic transmission, the hydraulic pressure generated by the oil pump is supplied to the frictional engagement element for the engagement control of the frictional engagement element, the frictional heat generated between the friction plates of the frictional engagement element is cooled, and the bearing portion of the transmission mechanism In order to prevent seizure of the steel and to lubricate the gear meshing portion, it is configured to be supplied to each lubrication location such as the friction plate, the bearing portion, and the gear meshing portion of the frictional engagement element.

  In the automatic transmission configured as described above, the line pressure for supplying the discharge pressure of the oil pump to the frictional engagement element as the lubricating oil to be supplied to each lubrication location such as the friction plate, the bearing portion, and the gear meshing portion of the frictional engagement element. There is known a hydraulic fluid that is discharged from a hydraulic pressure regulating valve or the like.

  However, the amount of lubricating oil supplied to each lubricating location varies depending on the operating conditions of the vehicle, etc. In order to suppress, it is required to supply a necessary amount of lubricating oil for each lubrication point.

  On the other hand, it is conceivable to control the supply amount of lubricating oil by using a dedicated hydraulic control valve for each lubricating oil supply destination that is a lubrication location, but use a dedicated hydraulic control valve for each lubricating oil supply destination. Therefore, it is desirable to variably control the supply amount of the lubricating oil for each lubricating oil supply destination without using a dedicated hydraulic control valve for each lubricating oil supply destination.

  Accordingly, the present invention provides an automatic transmission that variably controls the amount of lubricating oil supplied to a plurality of lubricating oil supply destinations without using a dedicated hydraulic control valve for each lubricating oil supply destination. The challenge is to be able to do so.

  In order to solve the above problems, the present invention is configured as follows.

First, the invention according to claim 1 of the present application is directed to an input port to which lubricating oil is input from a hydraulic supply source, and a plurality of outputs that respectively output the lubricating oil input to the input port to a plurality of lubricating oil supply destinations. A rotary valve-equipped automatic transmission comprising a rotary valve main body having a port, and a rotary valve having a valve body that selectively communicates the input port and the plurality of output ports by being rotationally driven. The rotary valve body has the input port and the plurality of output ports formed in a groove shape from a facing surface facing the valve body, and communicated with the plurality of output ports, respectively, and the valve body. A plurality of openings extending in the circumferential direction of the valve body and spaced apart in the radial direction of the valve body are formed in a groove shape from a facing surface facing the valve body. Disc Communication that selectively feeds the input port and the plurality of output ports through the opening of the rotary valve body by being rotationally driven to control the supply of lubricant to a plurality of lubricant supply destinations. The portion is formed in a groove shape from a facing surface facing the rotary valve body .

  According to a second aspect of the present invention, in the automatic transmission with a rotary valve according to the first aspect, a separate member is provided between the rotary valve main body and the valve body, and the separate member includes the A plurality of openings are formed which communicate with the plurality of output ports, extend in the circumferential direction of the valve body, and are spaced apart in the radial direction of the valve body.

  The invention according to claim 3 is the automatic transmission with a rotary valve according to claim 1 or claim 2, wherein the communicating portion of the valve body extends toward the radially outer side of the valve body. It is formed in a fan shape.

  According to a fourth aspect of the present invention, in the automatic transmission with a rotary valve according to the third aspect of the present invention, the automatic transmission with the rotary valve includes a speed change mechanism having a plurality of frictional engagement elements, and is the most of the plurality of openings of the rotary valve body. The lubricating oil supply destination to which lubricating oil is output from the output port communicating with the opening portion on the radially outer side of the valve body includes the friction engagement element that is fastened when starting.

  The invention according to claim 5 is the automatic transmission with a rotary valve according to any one of claims 1 to 4, wherein at least some of the plurality of openings of the rotary valve main body are It is formed by overlapping in the circumferential direction of the valve body.

  The invention according to claim 6 is the automatic transmission with a rotary valve according to any one of claims 1 to 5, further comprising an actuator that rotationally drives the valve body. The valve body is connected through a gear meshing portion.

  The invention according to claim 7 is the automatic transmission with a rotary valve according to claim 6, further comprising a predetermined hydraulic control valve, wherein the hydraulic control valve includes a spool and a spring that biases the spool. And an urging force adjusting mechanism for adjusting the urging force of the spring and controlling the hydraulic pressure output from the hydraulic control valve, and the urging force adjusting mechanism adjusts the urging force of the spring by the actuator. The hydraulic pressure output from the hydraulic control valve is configured to be controlled.

  The invention according to claim 8 is the automatic transmission with a rotary valve according to claim 7, wherein the hydraulic control valve controls the original pressure of the lubricating oil input to the input port of the rotary valve body. It is the valve which carries out.

  The invention according to claim 9 is the automatic transmission with a rotary valve according to any one of claims 6 to 8, wherein the output portion of the transmission mechanism of the automatic transmission is locked or not. A restricting mechanism for restricting to a locked state is provided, and the restricting mechanism is configured to restrict an output portion of the transmission mechanism to a locked state or an unlocked state by the actuator.

According to a tenth aspect of the present invention, there is provided a rotary valve body having an input port to which lubricating oil is input and a plurality of output ports for outputting the lubricating oil input to the input port, and rotationally driven. A rotary valve having a valve body for selectively communicating the input port and the plurality of output ports , wherein the input port and the plurality of output ports are opposed to the valve body. Are formed in a groove-like shape from the facing surface, communicated with the plurality of output ports, extend in the circumferential direction of the valve body, and are spaced apart in the radial direction of the valve body. a plurality of openings are formed recessed in a groove-like from the facing surface that faces the valve body, said valve body, fill front through the opening of the rotary valve body by the valve body is rotated Ports and said plurality of output ports by selectively communicating are formed recessed in a groove-like from the surface facing the communicating portion facing the rotary valve body for controlling the output of the lubricating oil from the plurality of output ports It is characterized by being.

  With the above configuration, according to the first aspect of the present invention, the automatic transmission has an input port to which lubricating oil is input from a hydraulic pressure supply source and a plurality of output ports that output to a plurality of lubricating oil supply destinations, respectively. A rotary valve main body, and a rotary valve having a valve body that selectively communicates with the input port and the plurality of output ports by being driven to rotate.

The rotary valve body is formed with an input port and a plurality of output ports recessed in a groove shape from the opposing surface facing the valve body, and communicated with the plurality of output ports and arranged in the circumferential direction of the valve body. And a plurality of openings spaced apart in the radial direction of the valve body are formed in a groove shape from a facing surface facing the valve body, and the valve body is driven to rotate by the valve body. Opposite surface where the communication portion that selectively connects the input port and the plurality of output ports through the opening of the rotary valve main body to control the supply of the lubricating oil to a plurality of lubricating oil supply destinations faces the rotary valve main body To be recessed in a groove shape .

  As a result, without using a dedicated hydraulic control valve for each of a plurality of lubricant supply destinations, a single rotary valve can be used to supply the lubricant supplied to a plurality of lubricant supply destinations according to the rotation angle of the valve body. The supply amount can be variably controlled for each lubricant supply destination. For example, the frictional engagement element that is fastened at the time of start-up can be supplied with a larger amount of lubricating oil at the time of start-up to cool the frictional engagement element, or the frictional engagement element that can be fastened at the time of speed-change can be increased. Thus, the frictional engagement element can be cooled.

  According to the second aspect of the present invention, the separation member is provided between the rotary valve body and the valve body, and the separation member communicates with the plurality of output ports and extends in the circumferential direction of the valve body. A plurality of openings that are present and spaced apart in the radial direction of the valve body are formed. Thereby, supply control of the lubricating oil supplied to a plurality of lubricating oil supply destinations can be precisely performed by the opening formed in the separate member.

  According to the invention described in claim 3, the communicating portion of the valve body is formed in a substantially fan shape that expands outward in the radial direction of the valve body. As a result, when the opening is formed in the rotary valve body so as to extend along the circumferential direction of the valve body, the lubricating oil is simultaneously supplied from the output port communicating with the opening respectively disposed on the inside and outside in the radial direction of the valve body. And a larger amount of lubricating oil than an output port communicating with the opening disposed radially inside the valve body from an output port communicating with the opening disposed radially outside the valve body Can be supplied.

  According to the invention of claim 4, the lubricating oil supply destination to which the lubricating oil is output from the output port communicating with the opening on the radially outer side of the valve body among the plurality of openings of the rotary valve main body is When the opening is formed in the rotary valve body so as to extend along the circumferential direction of the valve body by including the frictional engagement element that is fastened at the start, a large amount of the frictional engagement element that is fastened at the start Lubricating heat generated between the friction plates of the frictional engagement element can be cooled by supplying lubricating oil.

  According to the invention described in claim 5, at least a part of the plurality of openings of the rotary valve body is formed in the valve body by being overlapped in the circumferential direction of the valve body. The amount of lubricating oil supplied to a plurality of lubricating oil supply destinations can be variably controlled using the two communicating portions, and the above-described effects can be effectively achieved.

  According to the sixth aspect of the present invention, the actuator for rotating the valve body is provided, and the actuator and the valve body are connected via the gear meshing portion. As a result, by using a gear meshing portion that suppresses reverse drive from the valve body to the actuator, when holding the valve body at a predetermined rotation angle, when rotating the valve body without supplying power to the actuator Since power can be supplied only to the actuator, the above-mentioned effect can be obtained effectively while suppressing power consumption.

  According to the seventh aspect of the present invention, the predetermined hydraulic control valve is provided, and the hydraulic control valve adjusts the urging force for controlling the hydraulic pressure by adjusting the urging force of the spring and the spring for urging the spool. A biasing force adjusting mechanism configured to control the hydraulic pressure by adjusting the biasing force of the spring by the actuator. Thus, the rotation control of the valve body of the rotary valve and the drive control of the urging force adjusting mechanism of the hydraulic control valve can be performed using a single actuator, and the actuator for the rotation control and the drive control, respectively. Compared with the case of using the number of parts, the number of parts and the assembly process can be reduced, and the automatic transmission can be downsized.

  According to the invention described in claim 8, the hydraulic control valve is a valve that controls the original pressure of the lubricating oil that is input to the input port of the rotary valve body. The body rotation control and the drive control of the urging force adjusting mechanism of the valve for controlling the original pressure of the lubricating oil input to the input port of the rotary valve main body can be performed, and the above-mentioned effect can be obtained effectively.

  According to the ninth aspect of the present invention, the regulation mechanism that regulates the output portion of the transmission mechanism to the locked state or the unlocked state is provided, and the regulation mechanism locks the output portion of the transmission mechanism by the actuator. It is configured to restrict to an unlocked state. Thus, the rotation control of the valve body and the drive control of the restriction mechanism for restricting the output part of the transmission mechanism to the locked state or the unlocked state can be performed using a single actuator. Compared to the case where actuators are used for control, the number of parts and the assembly process can be reduced, and the automatic transmission can be downsized.

Further, according to the invention described in claim 10, the rotary valve includes a rotary valve body having a plurality of output ports for outputting input port and the lubricating oil lubricating oil is supplied respectively, by being driven to rotate And a valve body that selectively communicates the input port with the plurality of output ports.

The rotary valve body is formed with an input port and a plurality of output ports recessed in a groove shape from the opposing surface facing the valve body, and communicates with the plurality of output ports and extends in the circumferential direction of the valve body. And a plurality of openings that are spaced apart in the radial direction of the valve body are formed in a groove shape from a facing surface facing the valve body, and the valve body is rotationally driven by the valve body. The communication portion that selectively communicates the input port and the plurality of output ports through the opening of the rotary valve body to control the output of the lubricating oil from the plurality of output ports from the facing surface that faces the rotary valve body It is formed in a groove shape .

  Accordingly, the supply amount of the working liquid supplied to the plurality of working liquid supply destinations according to the rotation angle of the valve body by a single rotary valve without using a dedicated hydraulic control valve for each of the plurality of working liquid supply destinations. Can be variably controlled for each working liquid supply destination.

1 is a circuit diagram illustrating a configuration of a main part of a hydraulic control circuit of an automatic transmission according to a first embodiment of the present invention. It is a control system figure of an automatic transmission. It is explanatory drawing for demonstrating the drive of the control mechanism which controls the output gear of a transmission mechanism in a locked state or an unlocked state. It is explanatory drawing for demonstrating the action | operation of the said control mechanism. It is sectional drawing which shows the rotary valve with which the automatic transmission was equipped. It is a top view which shows the rotary valve main body of the said rotary valve, a separate member, and a valve body. FIG. 6 is a cross-sectional view of the rotary valve along line Y7-Y7 in FIG. It is explanatory drawing for demonstrating the output side opening part provided in the said separate member. It is sectional drawing which shows the rotary valve with which the automatic transmission which concerns on 2nd Embodiment of this invention was equipped. It is a top view which shows the rotary valve main body of the said rotary valve, a separate member, and a valve body. It is sectional drawing of the rotary valve along the Y11-Y11 line in FIG. It is explanatory drawing for demonstrating the output side opening part provided in the said separate member. It is a circuit diagram which shows the structure of the principal part of the hydraulic control circuit of the automatic transmission which concerns on 3rd Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is a circuit diagram showing a configuration of a main part of a hydraulic control circuit of an automatic transmission according to the first embodiment of the present invention, and FIG. 2 is a control system diagram of the automatic transmission. The automatic transmission according to the first embodiment of the present invention includes, in a transmission case, an input shaft as an input unit connected to a drive source such as an engine, and a plurality of components disposed on the axis of the input shaft. A planetary gear set and a plurality of frictional engagement elements such as clutches and brakes, and an output gear as an output portion of the transmission mechanism.

  The automatic transmission is configured to obtain a predetermined shift stage by changing the gear ratio of the transmission mechanism by switching the power transmission path through the plurality of planetary gear sets by combining the engagement states of the plurality of friction engagement elements. ing. For example, there are four planetary gear sets and five frictional engagement elements, and the D (forward travel) range of the shift lever operated by the driver by selectively engaging three of these frictional engagement elements. 1 to 8th speed and a reverse speed in the R (reverse running) range are formed.

  In the automatic transmission, none of the frictional engagement elements among the plurality of frictional engagement elements is engaged in the P (parking) range and the N (neutral) range. It is also possible to fasten one or two frictional fastening elements fastened at

  In the automatic transmission, a parking gear is provided so as to rotate integrally with the output gear of the transmission mechanism. The parking gear swings so that the pawl portion engages with the parking gear to lock the parking gear, and the parking rod 52 presses the parking pawl to engage with the parking gear (see FIG. 1), and a parking mechanism 55 that is switched between a first state in which the output gear of the transmission mechanism is locked and a second state in which the output gear is unlocked.

  As shown in FIGS. 1 and 2, the automatic transmission has a hydraulic control circuit 100 for selectively supplying fastening hydraulic pressure to a plurality of frictional engagement elements to realize a predetermined shift speed. The hydraulic control circuit 100 shown in FIG. 1 is shown in a P range state.

  As shown in FIG. 2, the hydraulic control circuit 100 includes a shift solenoid valve 101 that controls the hydraulic pressure supplied to the plurality of friction engagement elements for fastening the plurality of friction engagement elements, and the friction plates of the plurality of friction engagement elements. The lubricating actuator 102 for controlling the supply of lubricating oil to be supplied to a plurality of lubricating oil supply destinations in the automatic transmission, such as the gear meshing portion and the bearing portion, and the parking mechanism 55 are in the locked state and the non-locking state. A parking switching valve 103 or the like that switches between the locked state and the second state is provided.

  The automatic transmission is also provided with a controller 200 that controls the operation of the shift solenoid valve 101, the lubrication actuator 102, the parking switching valve 103, and the like in the hydraulic control circuit 100. The controller 200 is operated by a driver's operation. A signal from the range sensor 201 that detects the range of the selected shift lever, a signal from the vehicle speed sensor 202 that detects the vehicle speed of the vehicle, a signal from the accelerator sensor 203 that detects the driver's accelerator pedal operation amount, and the like are input. It has come to be.

  Based on the input signal, the controller 200 outputs a control signal to the shift solenoid valve 101 in the hydraulic control circuit 100 in accordance with the selected range and the driving state of the vehicle, so that the shift solenoid valve 101 The opening / closing or opening degree is controlled to control the engagement of the plurality of frictional engagement elements to form a predetermined gear stage. In the P range and the N range, the shift solenoid valve 101 is controlled so that none of the plurality of friction engagement elements is engaged.

  The controller 200 also outputs a control signal to the lubrication actuator 102 in the hydraulic control circuit 100 according to the selected range and the driving state of the vehicle based on the input signal, and a plurality of lubrications in the automatic transmission. Controls the supply of lubricating oil to the oil supply destination.

  In the automatic transmission, three lubricating oil supply destinations 11, 12, and 13 are provided, and the first lubricating oil supply destination 11 is set with a lubricating oil supply destination including a plurality of frictional engagement elements, a gear meshing portion, a bearing portion, and the like. In addition, a frictional engagement element that is fastened at the start is set as the second lubricant supply destination 12, and a frictional engagement element that is fastened and released at the time of shifting is set as the third lubricant supply destination 13.

  At the time of start, the frictional engagement element that is fastened at the time of start is supplied with the lubricating oil supplied to the second lubricating oil supply destination 12 in addition to the lubricating oil supplied to the first lubricating oil supply destination 11. In addition to the lubricating oil supplied to the first lubricating oil supply destination 11, the lubricating oil supplied to the third lubricating oil supply destination 13 is supplied to the frictional engagement elements that are sometimes fastened and released.

  Further, the controller 200 outputs a control signal to the parking switching valve 103 based on the input signal. When the controller 200 is in the P range, the parking mechanism 55 is set to the first state in the locked state, and the N range, D range, and R range are set. When in the range, the parking mechanism 55 is controlled to be in the second state of the unlocked state. The controller 200 includes a microcomputer as a main part.

  As shown in FIG. 1, the hydraulic control circuit 100 is configured such that the hydraulic pressure supplied by an oil pump 121 as a hydraulic pressure supply source that supplies hydraulic pressure is supplied to a predetermined hydraulic circuit 20 through an oil passage 131. . The predetermined hydraulic circuit 20 includes a shift solenoid valve 101 so as to selectively supply engagement hydraulic pressure to a plurality of friction engagement elements to perform engagement control of the plurality of friction engagement elements to form a predetermined shift stage. It has become.

  The hydraulic pressure supplied by the oil pump 121 is also supplied to the parking switching valve 103 through the oil passage 132. The parking switching valve 103 opens or shuts off the upstream oil passage 132 and the downstream oil passage 133, and when opened, supplies the hydraulic pressure supplied by the oil pump 121 to the downstream oil passage 133 to shut off. Sometimes the hydraulic pressure in the downstream oil passage 133 is discharged.

  The oil passage 133 on the downstream side of the parking switching valve 103 is connected to a hydraulic cylinder 50 having a piston that functions as the parking rod 52, and supply / discharge of hydraulic pressure to the hydraulic cylinder 50 is switched by the parking switching valve 103. The hydraulic cylinder 50 includes a cylinder body 51, a parking rod 52 that is movably attached to the cylinder body 51, and a spring 53 that biases the parking rod 52 in a direction in which the parking rod 52 protrudes from the cylinder body 51.

  The parking rod 52 is positioned at a set position that is urged by the spring 53 to protrude from the cylinder body 51 when the hydraulic pressure to the hydraulic cylinder 50 is discharged, and the spring 53 when the hydraulic pressure is supplied to the hydraulic cylinder 50. It is located at a stroke position that is retracted toward the cylinder body 51 against the urging force.

  When the parking rod 52 is in the set position, the parking pawl is engaged with the parking gear to lock the output gear of the speed change mechanism. When the parking rod 52 is in the stroke position, the parking pole is separated from the parking gear. The output gear of the speed change mechanism is unlocked.

  Thus, the parking rod 52 of the hydraulic cylinder 50 is switched to the first state in which the output gear of the transmission mechanism is locked and the second state in which the output gear of the transmission mechanism is unlocked together with the parking pole and the parking gear. A mechanism 55 is configured.

  Further, the parking switching valve 103 switches the supply and discharge of the hydraulic pressure supplied to the hydraulic cylinder 50 to move the parking rod 52 so that the parking mechanism 55 is switched between the locked first state and the unlocked second state. It is configured.

  The automatic transmission also includes a regulating mechanism 60 that regulates the output gear of the transmission mechanism to a locked state or an unlocked state. The regulating mechanism 60 is a first mechanism in which the parking mechanism 55 is in the unlocked state from the locked state. The switching to the two state is restricted, and the parking mechanism 55 is restricted from being switched from the unlocked second state to the locked first state.

  FIG. 3 is an explanatory diagram for explaining the driving of the regulating mechanism that regulates the output gear of the speed change mechanism to the locked state or the unlocked state, and FIG. 4 is an explanatory diagram for explaining the operation of the regulating mechanism. is there.

  As shown in FIG. 3, the automatic transmission includes an electric actuator that functions as a lubrication actuator 102, a worm gear 111 provided at the tip of the drive shaft of the electric actuator 102, and a worm wheel 112 that meshes with the worm gear 111. And a shaft member 113 fixed to the worm wheel 112 and rotatably supported in the automatic transmission. Note that a stepping motor, a servo motor, or the like can be used as the electric actuator 102.

  The restricting mechanism 60 is a trapezoidal cam member 61 attached to the end surface of the worm wheel 112 so as to extend in an arc shape in the circumferential direction of the worm wheel 112, and an approximately biased force toward the parking rod 52 by a spring 62. And a stopper member 63 having an L-shaped cross section.

  The stopper member 63 has one end of the stopper member 63 engaged with the first groove portion 55 or the second groove portion 56 provided in the axial direction at the rear end portion of the parking rod 52 so that the parking rod 52 moves in the axial direction. To be controlled.

  The stopper member 63 is also moved toward the anti-parking rod 52 against the urging force of the spring 62 when the other end of the stopper member 63 contacts the cam member 61 attached to the worm wheel 112, and the stopper member The engagement between one end of 63 and the first groove portion 55 or the second groove portion 56 of the parking rod 52 is released.

  In the automatic transmission, as shown in FIG. 4A, when in the P range, the hydraulic pressure to the hydraulic cylinder 50 is discharged and the parking rod 52 is set to the set position protruding from the cylinder body 51. The stopper member 63 engages with the second groove portion 56 of the parking rod 52 to restrict the parking rod 52 to the set position and restrict the output gear of the transmission mechanism to the locked state.

  At the time of operation from the P range to the D range, as shown in FIG. 4B, the electric actuator 102 is operated to rotate the worm gear 111, thereby rotating the worm gear 111 and the worm wheel 112 via the gear meshing portion 114. The worm wheel 112 is rotated together with the shaft member 113, and accordingly, the stopper member 63 is moved to the anti-parking rod 52 side by the cam member 61, and the engagement between the stopper member 63 and the second groove portion 56 of the parking rod 52 is released. To do.

  Then, in a state where the engagement between the stopper member 63 and the second groove portion 56 of the parking rod 52 is released, the parking switch valve 103 is controlled to supply the hydraulic pressure to the hydraulic cylinder 50 as shown in FIG. As a result, the parking rod 52 is set to the stroke position retracted toward the cylinder body 51 side.

  Next, as shown in FIG. 4D, the worm wheel 112 is rotated together with the shaft member 113 by operating the electric actuator 102 to rotationally drive the worm gear 111, and accordingly, the stopper member 63 and the cam member 61 are rotated. Is released, the stopper member 63 is moved to the parking rod 52 side, and the stopper member 63 and the first groove 55 of the parking rod 52 are engaged to restrict the parking rod 52 to the stroke position, thereby changing the speed change mechanism. The output gear is regulated to the unlocked state.

  As described above, the restriction mechanism 60 is connected to the electric actuator 102 via the gear meshing portion 114, and is configured to restrict the output gear of the speed change mechanism to the locked state or the unlocked state by the electric actuator 102.

  It should be noted that the operation from the P range to the N range and the R range is performed by operating the electric actuator 102 and the stopper member 63 and the second groove portion 56 of the parking rod 52 as in the operation from the P range to the D range. After releasing the engagement, the parking rod 52 is set to the stroke position, and then the electric actuator 102 is operated to engage the stopper member 63 and the first groove portion 55 of the parking rod 52 to bring the parking rod 52 to the stroke position. regulate. About the operation from D range, N range, and R range to P range, operation opposite to the operation from P range to D range, N range, and R range is performed.

  Returning to FIG. 1, the hydraulic pressure control circuit 100 also controls the hydraulic pressure supplied by the oil pump 121 to the first lubricating oil supply destination 11, the second lubricating oil supply destination 12, and the third lubricating oil supply destination 13. A hydraulic control valve 105 that controls the hydraulic pressure supplied as the lubricating oil is provided.

  The hydraulic control valve 105 includes a spool 105a and a spring 105b that is disposed on one end side of the spool 105a and biases the spool 105a. The hydraulic control valve 105 also includes an input port b through which the hydraulic pressure supplied by the oil pump 121 is input through the oil passage 134, and an output port c that outputs the lubricating oil supply destinations 11, 12, and 13 through the oil passage 135. And a drain port d, and a return port a to which an oil passage 136 branched from an oil passage 135 connected to the output port c is connected via an orifice 136a.

  In the hydraulic control valve 105, when the spool 105a moves in the axial direction against the urging force of the spring 105b, the output port c selectively communicates with the input port b and the drain port d, and is output from the output port c. When the hydraulic pressure to be increased becomes higher than the set pressure set by the urging force of the spring 105b, the hydraulic pressure communicates with the drain port d and is controlled to a predetermined hydraulic pressure.

  The oil passage 135 connected to the output port c of the hydraulic control valve 105 includes an oil passage 137 to the first lubricant supply destination 11, an oil passage 138 to the second lubricant supply destination 12, and a third lubricant supply destination 13. The hydraulic pressure supplied from the oil pump 121 is controlled to a predetermined hydraulic pressure by the hydraulic control valve 105 and supplied to the lubricating oil supply destinations 11, 12, and 13 as lubricating oil.

  The oil passage 137 to the first lubricating oil supply destination 11, the oil passage 138 to the second lubricating oil supply destination 12, and the oil passage 139 to the third lubricating oil supply destination 13, respectively, Variable throttle valves 21, 22, and 23 that control the amount of lubricant supplied to the second lubricant supply destination 12 and the third lubricant supply destination 13 are arranged, and the variable throttle valves 21, 22, and 23 are single The rotary valve 30 is formed.

  Further, a predetermined amount of lubricant is supplied to the oil passage 138 to the second lubricant supply destination 12 and the oil passage 139 to the third lubricant supply destination 13 on the downstream side of the variable throttle valves 22 and 23, respectively. The flow rate control valves 106 and 107 having the pressure compensation function to be held in the position are arranged.

  FIG. 5 is a cross-sectional view showing a rotary valve provided in the automatic transmission. As shown in FIG. 5, the rotary valve 30 is disposed between the rotary valve body 31, the valve body 32 that is rotatably supported with respect to the rotary valve body 31, and the rotary valve body 31 and the valve body 32. And a support member 34 that is attached to the rotary valve main body 31 via the separate member 33 and supports the valve element 32 rotatably.

  6 is a plan view showing a rotary valve main body, a separating member, and a valve body of the rotary valve. FIG. 6A shows the rotary valve main body viewed from the Y6a direction in FIG. 5, and FIG. FIG. 5 shows a separate member viewed from the Y6b direction in FIG. 5, and FIG. 6C shows the valve body viewed from the Y6c direction in FIG.

  The rotary valve body 31 has an input port e to which lubricating oil is input from an oil pump 121 serving as a hydraulic pressure supply source via a hydraulic control valve 105 that controls the original pressure of the lubricating oil, and lubrication input to the input port e. There are provided a first output port f, a second output port g, and a third output port h for outputting oil to the first lubricant supply destination 11, the second lubricant supply destination 12, and the third lubricant supply destination 13, respectively. ing.

  As shown in FIGS. 5 and 6 (a), the input port e, the first output port f, the second output port g, and the third output port h are each a valve body through a separate member 33 in the rotary valve body 31. 32 is formed to be recessed in a groove shape from the facing surface facing 32.

  The input port e, the first output port f, the second output port g, and the third output port h are each formed to extend from the outer peripheral side of the rotary valve body 31 to the center side of the rotary valve body 31. The input port e includes an input side opening 31 a formed in a circular shape at a position where the center side end of the rotary valve main body 31 corresponds to the center of the valve body 32.

  Each of the first output port f, the second output port g, and the third output port h is an output side that is formed in an arc shape so that the center side end of the rotary valve body 31 extends in the circumferential direction of the valve body 32. Openings 31b, 31c and 31d are provided. The output side openings 31b, 31c, 31d of the first output port f, the second output port g, and the third output port h are sequentially spaced from the radially inner side to the outer side of the valve body 32.

  As shown in FIG. 6B, the separation member 33 is formed with an input side opening 33 a that penetrates the separation member 33, and the input side opening 33 a is connected to the input side opening 31 a of the rotary valve main body 31. Similarly, it is formed in a circular shape at a position corresponding to the central portion of the valve body 32.

  The separation member 33 is also formed with a first output side opening 33b, a second output side opening 33c, and a third output side opening 33d that penetrate the separation member 33, and the first output side opening 33b, Similarly to the output side openings 31b, 31c, 31d of the rotary valve body 31, each of the second output side opening 33c and the third output side opening 33d has an arc shape so as to extend in the circumferential direction of the valve body 32. The valve body 32 is formed and spaced from the inside in the radial direction to the outside.

  The valve body 32 is integrally attached to a shaft member 113 fixed to a worm wheel 112 that meshes with a worm gear 111 provided at the tip of a drive shaft of the electric actuator 102, and is rotated by the electric actuator 102 together with the shaft member 113. It has become.

  When the valve body 32 is rotationally driven, the valve body 32 is connected to the input port e, the first output port f, the second output port g, the second output port g via the output side openings 33b, 33c, 33d of the separation member 33. A communication portion 32a for controlling the supply of lubricant to the first lubricant supply destination 11, the second lubricant supply destination 12, and the third lubricant supply destination 13 by selectively communicating with the three output ports h is formed. ing.

  The communication part 32 a is formed in a groove shape from a facing surface facing the rotary valve main body 31 via the separation member 33 in the valve body 32. The communication portion 32a of the valve body 32 is formed in a substantially fan shape that expands outward in the radial direction of the valve body 32, and the center side end portion 32b of the communication portion 32a is connected to the input side opening 31a and the rotary valve body 31. Similar to the input side opening 33 a of the separating member 33, it is formed in a circular shape at a position corresponding to the central portion of the valve body 32.

  FIG. 7 is a cross-sectional view of the rotary valve along the line Y7-Y7 in FIG. 5, and FIG. 8 is an explanatory diagram for explaining an output side opening provided in the separate member. At the angular position of the rotary valve 30 shown in FIG. 7, as shown in FIGS. 7 and 8, the first output side opening 33 b of the separation member 33 opens between 0 degrees and 150 degrees. The second output side opening 33c opens between 30 degrees and 90 degrees, and the third output side opening 33d of the separating member 33 opens between 60 degrees and 120 degrees. On the other hand, the communication part 32a of the valve body 32 is opened so that the central angle becomes 30 degrees. Note that the output side openings 33b, 33c, 33d of the separation member 33 and the communication portion 32a of the valve body 32 are appropriately set.

  The first output side opening 31b, the second output side opening 31c, and the third output side opening 31d of the rotary valve body 31 are respectively the first output side opening 33b and the second output side opening 33c of the separate member 33. The third output side opening 33d is formed in the same manner.

  Accordingly, when the valve body 32 is driven to rotate, the input port e and the output ports f, g, and h are selectively communicated with each other via the output side openings 33b, 33c, and 33d of the separating member 33 to supply hydraulic pressure. The supply of lubricating oil from the element 121 to the lubricating oil supply destinations 11, 12, 13 is controlled.

  For example, when the communicating portion 32a of the valve body 32 is in the state shown in FIGS. 7 and 8, the lubricating oil input from the input port e is passed through the communicating portion 32a to the first output port f, the second output port g, The supply amount of the lubricating oil is controlled according to the opening areas of the output side openings 33b, 33c, and 33d of the separation member 33 that is output from the three output ports h and opens to the communication portion 32a.

  Further, the valve body 32 is controlled so as to output lubricating oil from the first output port f and the second output port g when starting, and to output lubricating oil from the first output port f and the third output port h at the time of shifting. The

  In the present embodiment, at least a part of the first output side opening 33b, the second output side opening 33c, and the third output side opening 33d of the separating member 33 is formed to overlap in the circumferential direction of the valve body 32. Has been. The first output side opening 33b and the second output side opening 33c overlap between 30 degrees and 90 degrees, and the first output side opening 33b and the third output side opening 33d are between 60 degrees and 120 degrees. The second output side opening 33c and the third output side opening 33d overlap each other between 60 degrees and 90 degrees.

  Thus, at least a part of the plurality of output side openings 33b, 33c, 33d of the separating member 33 is formed in the valve body 32 by being overlapped in the circumferential direction of the valve body 32. The supply amount of the lubricating oil to the plurality of lubricating oil supply destinations 11, 12, 13 can be variably controlled using the two communication portions 32a.

  In the automatic transmission, as shown in FIG. 1, the lubricating oil output from the first output port f of the rotary valve 30 is supplied to the first lubricating oil supply destination 11 through the oil passage 137. The lubricating oil output from the 30 second output port g is supplied to the second lubricating oil supply destination 12 via the flow rate control valve 106 having a pressure compensation function.

  The flow control valve 106 includes a spool 106a and a spring 106b that is disposed on one end side of the spool 106a and biases the spool 106a. The flow rate control valve 106 also includes an input port j that receives lubricating oil from the second output port g of the rotary valve 30, an output port k that outputs lubricating oil to the second lubricating oil supply destination 12, and a drain port l. Are provided, and a first control port i to which lubricating oil is supplied from the oil passage 135 and a second control port m to which lubricating oil is supplied from the second output port g of the rotary valve 30 are provided. .

  The flow rate control valve 106 is supplied from the oil passage 135 by selectively connecting the output port k to the input port j and the drain port 1 as the spool 106a moves in the axial direction against the urging force of the spring 105b. When the hydraulic pressure of the lubricating oil is higher than the set pressure set by the urging force of the spring 106b or the like, it communicates with the drain port l.

  When the hydraulic pressure of the lubricating oil supplied from the oil passage 135 increases, the flow control valve 106 is accompanied by an increase in the differential pressure of the lubricating oil supplied to the first control port i and the second control port m. The spool 106a moves in a direction to close the output port k, and the supply amount of the lubricating oil output from the output port k is controlled to a predetermined amount.

  Further, when the hydraulic pressure of the lubricating oil supplied from the oil passage 135 becomes low, the spool 106a outputs as the differential pressure of the lubricating oil supplied to the first control port i and the second control port m decreases. The port k is moved in the opening direction, and the supply amount of the lubricating oil output from the output port k is controlled to a predetermined amount.

  Similarly to the lubricating oil output from the second output port g, the lubricating oil output from the third output port h of the rotary valve 30 is supplied to the third lubricating oil supply destination 13 via the flow rate control valve 107 having a pressure compensation function. Supplied to.

  In the present embodiment, the rotary valve 30 disposed in the oil passage 138 to the second lubricating oil supply destination 12 is configured to supply the lubricating oil to the second lubricating oil supply destination 12 at the start, and the third lubricating oil The rotary valve 30 disposed in the oil passage 139 to the supply destination 13 is configured to supply the lubricant to the third lubricant supply destination 13 at the time of shifting.

  Further, the rotational drive is transmitted from the electric actuator 102 to the shaft member 113 through the speed reduction mechanism including the worm gear 111 and the worm wheel 112 as the gear meshing portion 114, but the reverse drive from the shaft member 113 to the electric actuator 102 is suppressed. The rotational drive may be transmitted from the electric actuator 102 to the shaft member 113 through a gear meshing part such as a planetary gear mechanism.

  Further, in the present embodiment, the rotary valve 30 has the rotary valve main body 31 and the separation member 33 formed separately, but the separate member 33 can also be formed integrally with the rotary valve main body 31. .

  Thus, in the automatic transmission according to the present embodiment, the input port e to which lubricating oil is input from the hydraulic supply source 121 and the plurality of output ports f that output to the plurality of lubricating oil supply destinations 11, 12, and 13, respectively. , G, and h, and a rotary valve 30 having a valve body 32 that selectively drives the input port e and the plurality of output ports f, g, and h by being driven to rotate. It is done.

  The rotary valve body 31 communicates with the plurality of output ports f, g, and h, and is disposed in the circumferential direction of the valve body 32 and is spaced apart in the radial direction of the valve body 32. Parts 33b, 33c, and 33d are formed, and the valve body 32 is driven to rotate, whereby the input port e and the plurality of output ports f are provided via the openings 33b, 33c, and 33d of the rotary valve body 31. , G, and h are selectively communicated to form a communication portion 32a that controls the supply of the lubricating oil to the plurality of lubricating oil supply destinations 11, 12, and 13.

  Thereby, without using a dedicated hydraulic control valve for each of a plurality of lubricating oil supply destinations, a plurality of lubricating oil supply destinations 11, 12, according to the rotation angle of the valve body 32, using a single rotary valve 30. The supply amount of the lubricating oil supplied to 13 can be variably controlled for each of the lubricating oil supply destinations 11, 12, and 13. For example, the frictional engagement element that is fastened at the time of start-up can be supplied with a larger amount of lubricating oil at the time of start-up to cool the frictional engagement element, or the frictional engagement element that can be fastened at the time of speed-change can be increased. Thus, the frictional engagement element can be cooled.

  Further, the communication portion 32 a of the valve body 32 is formed in a substantially fan shape that expands toward the radially outer side of the valve body 32. Thus, when the openings 33b, 33c, and 33d are formed in the rotary valve body 31 so as to extend along the circumferential direction of the valve body 32, the openings are respectively disposed on the radially inner side and the outer side of the valve body 32. Lubricating oil can be supplied simultaneously from the communicating output port, and from the output port communicating with the opening disposed radially outside the valve body 32 to the opening disposed radially inside the valve body 32 A larger amount of lubricating oil can be supplied than the communicating output port.

  In addition, an actuator 102 that rotationally drives the valve body 32 is provided, and the actuator 102 and the valve body 32 are connected via a gear meshing portion 114. Thus, by using the gear meshing portion 114 that suppresses the reverse drive from the valve body 32 to the actuator 102, the valve body 32 is supplied without supplying power to the actuator 102 when the valve body 32 is held at a predetermined rotation angle. Since electric power can be supplied to the actuator 102 only when 32 is rotationally driven, power consumption can be suppressed.

  Further, a regulation mechanism 60 that regulates the output part of the transmission mechanism to a locked state or an unlocked state is provided, and the regulation mechanism 60 is configured to regulate the output part of the transmission mechanism to a locked state or an unlocked state by the actuator 102. Is done. Thereby, the rotation control of the valve body 32 and the drive control of the restriction mechanism 60 for restricting the output part of the speed change mechanism to the locked state or the unlocked state can be performed using the single actuator 102. In addition, the number of parts and the assembly process can be reduced and the automatic transmission can be downsized as compared with the case where actuators are used for the drive control.

  In the present embodiment, a friction engagement element that is fastened at the start is set as the second lubricant supply destination 12, and a friction engagement element that is fastened and released at the time of shifting is set as the third lubricant supply destination 13. A frictional engagement element that is engaged and released at the time of shifting may be set as the second lubricant supply destination 12, and a frictional engagement element that is engaged at the start may be set as the third lubricant supply destination 13.

  As described above, the lubricating oil supply destination 13 to which the lubricating oil is output from the output port h communicating with the opening 33 d radially outside the valve body 32 among the plurality of openings 33 b, 33 c, 33 d of the rotary valve main body 31. Includes a frictional engagement element that is fastened when starting, so that when the openings 33b, 33c, and 33d are formed in the rotary valve body 31 so as to extend along the circumferential direction of the valve body 32, they are fastened when starting. It is possible to supply a large amount of lubricating oil to the frictional engagement element when starting to cool the frictional heat generated between the friction plates of the frictional engagement element.

  A separate member 33 is provided between the rotary valve main body 31 and the valve body 32. The separate member 33 communicates with the plurality of output ports f, g, and h and extends in the circumferential direction of the valve body 32. In addition, a plurality of openings 33b, 33c, and 33d that are spaced apart in the radial direction of the valve body 32 are formed. Thereby, supply control of the lubricating oil supplied to the plurality of lubricating oil supply destinations 11, 12, and 13 can be precisely performed by the openings 33 b, 33 c, and 33 d formed in the separate member 33.

  Next, an automatic transmission according to a second embodiment of the present invention will be described. Since the automatic transmission according to the second embodiment is different from the automatic transmission according to the first embodiment only in the rotary valve, only the rotary valve will be described and the same configuration as the automatic transmission according to the first embodiment will be described. Description of is omitted.

  FIG. 9 is a cross-sectional view showing a rotary valve provided in an automatic transmission according to the second embodiment of the present invention. FIG. 10 is a plan view showing a rotary valve main body, a separating member and a valve body of the rotary valve. FIG. 10 (a) shows the rotary valve main body viewed from the Y10a direction in FIG. Shows a separate member as seen from the Y10b direction in FIG. 9, and FIG. 10 (c) shows the valve body as seen from the Y10c direction in FIG.

  As shown in FIGS. 9 and 10, also for the rotary valve 230 of the automatic transmission according to the second embodiment of the present invention, the rotary valve 230 is rotatable with respect to the rotary valve main body 31 and the rotary valve main body 31. The valve body 32 to be supported, the separation member 233 disposed between the rotary valve body 31 and the valve body 32, and the rotary valve body 31 attached to the rotary valve body 31 via the separation member 233 and rotatably supporting the valve body 32. And a supporting member 34.

  In the rotary valve 230, the rotary valve main body 31, the valve body 32, and the support member 34 are formed in the same manner as the rotary valve 30, but the first output side opening 33 b and the second output side opening formed in the separate member 233. The portion 33c and the third output side opening 33d are configured by at least one circular through hole.

  As for the separation member 233, as shown in FIG. 10B, the separation member 233 is further provided with an input side opening 33a penetrating the separation member 233, a first output side opening 33b, and a second output side opening. 33c and a third output side opening 33d are formed.

  The first output side opening 33b, the second output side opening 33c, and the third output side opening 33d are each in the circumferential direction of the valve body 32, similarly to the output side openings 31b, 31c, 31d of the rotary valve body 31. The valve body 32 is formed in a circular arc shape so as to extend from the radially inner side to the outer side.

  In the present embodiment, the first output side opening 33b has a second opening area larger than the circular first through hole 233e and first communication hole 233e having a first opening area disposed in the circumferential direction of the valve body 32. And a circular second through-hole 233f, and as shown in FIG. 10 (b), the first through-hole 233e and two second through-holes 233f.

  The second output side opening 33c is also composed of a first through hole 233e and a second through hole 233f arranged in the circumferential direction of the valve body 32. The second output side opening 33c is shown in FIG. As shown in FIG. 1, the first through hole 233e and the second through hole 233f are configured.

  The third output side opening 33d is also composed of a first through hole 233e and a second through hole 233f arranged in the circumferential direction of the valve body 32. The third output side opening 33d is shown in FIG. As shown in FIG. 1, the first through hole 233e and the second through hole 233f are configured.

  11 is a cross-sectional view of the rotary valve along the line Y11-Y11 in FIG. 9, and FIG. 12 is an explanatory view for explaining an output side opening provided in the separate member. In FIG. 12, the first output side opening 33b, the second output side opening 33c, and the third output side opening 33d of the separating member 233 are rotated every 30 degrees at the angular position of the rotary valve 230 shown in FIG. A case where the first through hole 233e is arranged is indicated by hatching, and a portion where the second through hole 233f is provided is indicated by cross hatching.

  In the rotary valve 230, the valve body 32 is rotated every 30 degrees. As for the rotary valve 230 as well, at the angular position of the rotary valve 230 shown in FIG. 11, as shown in FIGS. 11 and 12, the first output side opening 33b of the separation member 233 opens between 0 degrees and 150 degrees. The second output side opening 33c of the separating member 233 opens between 30 degrees and 90 degrees, and the third output side opening 33d of the separating member 233 opens between 60 degrees and 120 degrees.

  11, the first output side opening 31b, the second output side opening 31c, and the third output side opening 31d of the rotary valve body 31 are respectively the first output side opening of the separating member 33. 33b, the second output side opening 33c, and the third output side opening 33 are formed so as to open to the first through hole 233e and the second through hole 233f.

  Accordingly, when the valve body 32 is driven to rotate, the input port e and the output ports f, g, and h are selectively communicated with each other via the output side openings 33b, 33c, and 33d of the separating member 233 to supply hydraulic pressure. The supply of lubricating oil from the element 121 to the lubricating oil supply destinations 11, 12, 13 is controlled.

  For example, when the communicating portion 32a of the valve body 32 is in the state shown in FIGS. 11 and 12, the lubricating oil input from the input port e is output from the first output port f and the second output port g through the communicating portion 32a. According to the opening area of the output side openings 33b and 33c of the separation member 233 that opens to the communication part 32a, specifically, according to the opening area of the first through hole 233e and the second through hole 233f, lubrication is performed. The oil supply is controlled.

  Also in the automatic transmission according to the present embodiment, the valve body 32 of the rotary valve 230 outputs the lubricating oil from the first output port f and the second output port g when starting, and the first output port f and the third output when shifting. It is controlled to output the lubricating oil from the output port h.

  Also in the present embodiment, the rotary valve 230 has the rotary valve main body 31 and the separate member 233 formed separately, but the separate member 233 can also be formed integrally with the rotary valve main body 31. is there.

  As described above, the rotary valve 230 provided in the automatic transmission according to the present embodiment is also communicated with the rotary valve main body 31 to the plurality of output ports f, g, and h and arranged in the circumferential direction of the valve body 32. And a plurality of openings 33b, 33c, 33d that are spaced apart from each other in the radial direction of the valve body 32 are formed, and the valve body 32 is driven to rotate by rotating the valve body 32 to the valve body 32. Controlling supply of lubricating oil to the plurality of lubricating oil supply destinations 11, 12, 13 by selectively communicating the input port e and the plurality of output ports f, g, h through the openings 33b, 33c, 33d A communicating portion 32a is formed.

  Thereby, without using a dedicated hydraulic control valve for each of a plurality of lubricating oil supply destinations, a plurality of lubricating oil supply destinations 11, 12, The supply amount of the lubricating oil supplied to 13 can be variably controlled for each of the lubricating oil supply destinations 11, 12, and 13.

  A separate member 233 is provided between the rotary valve main body 31 and the valve body 32. The separate member 233 communicates with the plurality of output ports f, g, and h and extends in the circumferential direction of the valve body 32. In addition, a plurality of openings 33b, 33c, and 33d that are spaced apart in the radial direction of the valve body 32 are formed. Thereby, the supply control of the lubricating oil supplied to the plurality of lubricating oil supply destinations 11, 12, and 13 can be precisely performed by the openings 33 b, 33 c and 33 d formed in the separating member 233.

  In this embodiment, the communication part 32a formed in the valve body 32 is formed in a substantially fan shape, but is not limited to this, and can be formed in other shapes.

  In the first embodiment, the output side openings 33b, 33c, 33d of the separation member 33 are formed by one opening formed in an arc shape, and in the second embodiment, the output side opening of the separation member 233 is formed. The parts 33b, 33c, 33d are composed of at least one circular through hole 233e, 233f, but the output side opening of the separate member is formed by combining an arcuate opening and a circular through hole. A part may be formed.

  Next, an automatic transmission according to a third embodiment of the present invention will be described. Since the automatic transmission according to the third embodiment is different from the automatic transmission according to the first embodiment only in the hydraulic control valve that controls the hydraulic pressure supplied by the oil pump 121, only the hydraulic control valve will be described. The description of the same configuration as that of the automatic transmission according to the first embodiment is omitted.

  FIG. 13 is a circuit diagram showing a configuration of a main part of the hydraulic control circuit of the automatic transmission according to the third embodiment of the present invention. As shown in FIG. 13, the hydraulic pressure control circuit 300 for the automatic transmission according to the third embodiment of the present invention also controls the hydraulic pressure supplied by the oil pump 121 to provide the first lubricating oil supply destination 11 and the second lubricating oil. A hydraulic control valve 305 that controls the hydraulic pressure supplied as the lubricating oil to the oil supply destination 12 and the third lubricating oil supply destination 13 is provided.

  The hydraulic control valve 305 includes a spool 305 a and a spring 305 b that biases the spool 305 a, an input port b through which the hydraulic pressure supplied by the oil pump 121 is input through the oil passage 134, and each lubricating oil supply destination 11. , 12 and 13 are provided with an output port c for outputting through an oil passage 135 and a drain port d, and an oil passage 136 branched from the oil passage 135 connected to the output port c is connected via an orifice 136a. A return port a is provided.

  As for the hydraulic control valve 305, the spool 305a moves in the axial direction against the urging force of the spring 305b, so that the output port c is selectively communicated with the input port b and the drain port d. When the output hydraulic pressure becomes higher than the set pressure set by the urging force of the spring 305b or the like, it communicates with the drain port d and is controlled to a predetermined hydraulic pressure.

  The hydraulic control valve 305 also includes an urging force adjustment mechanism 310 that adjusts the urging force of the spring 305b and controls the hydraulic pressure output from the hydraulic control valve 305. The urging force adjustment mechanism 310 includes a spool 305a of the spring 305b. A spring receiving member 305c disposed on the opposite side of the spring receiving member 305c, and a cam member 305d contacting the spring receiving member 305c.

  The cam member 305d is integrally attached to a shaft member 113 fixed to a worm wheel 112 that meshes with a worm gear 111 provided at the tip of the drive shaft of the electric actuator 102, and is rotated by the electric actuator 102 together with the shaft member 113. It has become.

  The cam member 305d also has an outer peripheral surface whose distance from the center of the shaft member 113 is non-uniform corresponding to the rotation angle of the shaft member 113, and the cam member 305d is driven to rotate together with the shaft member 113 by the electric actuator 102. As a result, the spring receiving member 305c is moved in the axial direction of the spool 305a to adjust the urging force of the spring 305b.

  Thus, the urging force adjusting mechanism 310 is configured to control the hydraulic pressure output from the hydraulic control valve 305 by adjusting the urging force of the spring 305 c by the actuator 102.

  Thereby, the rotation control of the valve body 32 of the rotary valve 30 and the drive control of the urging force adjusting mechanism 310 of the hydraulic control valve 305 can be performed using the single actuator 102, and the rotation control and the drive control can be performed. Therefore, the number of parts and the assembly process can be reduced and the automatic transmission can be reduced in size as compared with the case where each actuator is used.

  In addition, the hydraulic control valve 305 is a valve that controls the original pressure of the lubricating oil input to the input port e of the rotary valve main body 31, so that the rotation control of the valve body 32 and the rotary are performed using a single actuator 102. It is possible to perform drive control of the urging force adjusting mechanism 310 of the hydraulic control valve 305 for controlling the original pressure of the lubricating oil input to the input port e of the valve body 31.

  In this embodiment, in FIG. 1, the hydraulic pressure is supplied from the oil pump 121 to the rotary valve 30 via the hydraulic control valve 105, but the hydraulic pressure is supplied from the oil pump 121 to the rotary valve 30 without passing through the hydraulic control valve 105. You may make it supply.

  In this embodiment, the rotary valve 30 is configured to output the lubricating oil from the hydraulic supply source 121 to the plurality of lubricating oil supply destinations 11, 12, and 13. However, the rotary valve 30 is limited to the lubricating oil. In addition, it is possible to configure so that a working liquid such as lubricating oil is output to a plurality of working liquid supply destinations.

  In such a case, the rotary valve selects the input port and the plurality of output ports by being driven to rotate, and the rotary valve body having an input port to which the working liquid is input and a plurality of output ports for outputting the working liquid, respectively. And a valve body that communicates with each other.

  The rotary valve body is formed with a plurality of openings that communicate with the plurality of output ports, extend in the circumferential direction of the valve body, and are spaced apart in the radial direction of the valve body. In addition, the valve body is driven to rotate, the input port and the plurality of output ports are selectively communicated with each other through the opening of the rotary valve body, and communication for controlling the output of the working liquid from the plurality of output ports is controlled. Part is formed.

  By configuring the rotary valve in this manner, a plurality of working liquids can be supplied according to the rotation angle of the valve body by a single rotary valve without using a dedicated hydraulic control valve for each of a plurality of working liquid supply destinations. The supply amount of the working liquid supplied first can be variably controlled for each working liquid supply destination.

  The present invention is not limited to the illustrated embodiments, and various improvements and design changes can be made without departing from the scope of the present invention.

  As described above, according to the present invention, in an automatic transmission, a lubricating oil supply amount can be supplied using a single rotary valve without using a dedicated hydraulic control valve for each lubricating oil supply destination. Since variable control can be performed for each destination, this type of automatic transmission or a vehicle in which the automatic transmission is mounted may be suitably used.

11, 12, 13 Lubricating oil supply destination 30, 230 Rotary valve 31 Rotary valve body 31b, 31c, 31d Output side opening 32 of rotary valve body 32 Valve body 32a Communication portion 33, 233 Separating member 33b, 33c, 33d Separating member Output side opening 55 Parking mechanism 60 Restriction mechanism 100, 300 Hydraulic control circuit 101 Shifting solenoid valve 102 Lubricating actuator 105, 305 Hydraulic control valve 105a, 106a, 305a Spool 105b, 106b, 305b Spring 200 Controller 310 Energizing force adjustment mechanism

Claims (10)

A rotary valve body having an input port to which lubricating oil is input from a hydraulic pressure supply source, and a plurality of output ports for outputting the lubricating oil input to the input port to a plurality of lubricating oil supply destinations, respectively, and rotationally driven An automatic transmission with a rotary valve comprising a rotary valve having a valve body that selectively communicates the input port and the plurality of output ports,
In the rotary valve body, the input port and the plurality of output ports are formed in a groove shape from a facing surface facing the valve body, and communicated with the plurality of output ports, respectively. A plurality of openings extending in the circumferential direction and spaced apart in the radial direction of the valve body are formed to be recessed in a groove shape from a facing surface facing the valve body ,
When the valve body is rotationally driven to the valve body, the input port and the plurality of output ports are selectively communicated with each other through the opening of the rotary valve body to a plurality of lubricant supply destinations. The communication portion for controlling the supply of the lubricating oil is formed in a groove shape from the facing surface facing the rotary valve body ,
An automatic transmission with a rotary valve. A separate member is provided between the rotary valve body and the valve body,
The separate member is formed with a plurality of openings that communicate with the plurality of output ports, extend in the circumferential direction of the valve body, and are spaced apart in the radial direction of the valve body. ,
The automatic transmission with a rotary valve according to claim 1. The communication part of the valve body is formed in a substantially fan shape that expands radially outward of the valve body.
The automatic transmission with a rotary valve according to claim 1 or 2, characterized by the above-mentioned. A transmission mechanism having a plurality of frictional engagement elements;
The lubricating oil supply destination to which the lubricating oil is output from the output port communicating with the opening on the radially outer side of the valve body among the plurality of openings of the rotary valve main body is fastened at the time of start-up. Including elements,
The automatic transmission with a rotary valve according to claim 3. At least some of the plurality of openings of the rotary valve body are formed to overlap in the circumferential direction of the valve body,
The automatic transmission with a rotary valve according to any one of claims 1 to 4, wherein the automatic transmission has a rotary valve. An actuator for rotationally driving the valve body;
The actuator and the valve body are connected via a gear meshing portion,
The automatic transmission with a rotary valve according to any one of claims 1 to 5, wherein the automatic transmission has a rotary valve. With a predetermined hydraulic control valve,
The hydraulic control valve includes a spool, a spring that biases the spool, and a biasing force adjusting mechanism that controls a hydraulic pressure output from the hydraulic control valve by adjusting a biasing force of the spring.
The biasing force adjustment mechanism is configured to control the hydraulic pressure output from the hydraulic control valve by adjusting the biasing force of the spring by the actuator.
The automatic transmission with a rotary valve according to claim 6. The hydraulic control valve is a valve that controls an original pressure of lubricating oil that is input to the input port of the rotary valve body.
The automatic transmission with a rotary valve according to claim 7. A regulation mechanism for regulating the output portion of the transmission mechanism of the automatic transmission to a locked state or an unlocked state;
The restriction mechanism is configured to restrict the output portion of the transmission mechanism to a locked state or an unlocked state by the actuator.
The automatic transmission with a rotary valve according to any one of claims 6 to 8, wherein the automatic transmission has a rotary valve. An input port lubricant is inputted, the plurality of output ports with the input port and the rotary valve main body by being rotated and a plurality of output ports which output the lubricating oil inputted to the input port A rotary valve having a valve body for selectively communicating with each other,
In the rotary valve body, the input port and the plurality of output ports are formed in a groove shape from a facing surface facing the valve body, and communicated with the plurality of output ports, respectively. A plurality of openings extending in the circumferential direction and spaced apart in the radial direction of the valve body are formed to be recessed in a groove shape from a facing surface facing the valve body ,
When the valve body is rotationally driven to the valve body, the input port and the plurality of output ports are selectively communicated with each other through the opening of the rotary valve body, and the plurality of output ports are connected to the valve body. The communication portion for controlling the output of the lubricating oil is formed in a groove shape from the facing surface facing the rotary valve body ,
A rotary valve characterized by that.

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