JP6090363B2 - Automatic transmission lubrication system - Google Patents

Description

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

  In general, an automatic transmission mounted on a vehicle supplies hydraulic pressure generated by an oil pump to a frictional engagement element for fastening control of the frictional engagement element, and cools frictional heat generated between friction plates of the frictional engagement element. In order to prevent seizure of the bearing portion of the speed change mechanism 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 location and to suppress supply more than necessary.

  On the other hand, it is conceivable to control the amount of lubricating oil supplied by using a dedicated solenoid valve for each lubricating oil supply destination that is a lubricating point, but it is possible to control the amount of lubricating oil supplied using a solenoid valve. , Not only when changing the supply amount of lubricating oil but also when holding the supply amount of lubricating oil, it consumes power and the power consumption increases. It is desirable to supply the necessary amount of lubricating oil.

  In recent years, for example, as disclosed in Patent Document 1, there is a tendency to abolish the torque converter in response to demands for multi-stage automatic transmission and weight reduction. The friction fastening element that is fastened is sometimes slipped and fastened. In order to effectively suppress the heat generated by the friction fastening element that is fastened at the time of starting, a large amount of lubricating oil is supplied to the friction fastening element at the time of starting. For example, it is desirable to supply a necessary amount of lubricating oil to the lubricating oil supply destination.

Japanese Patent No. 4922224

  However, if a large amount of lubricating oil is to be supplied to the lubricating oil supply destination, the valves and actuators for controlling the lubricating oil are increased in size, which may increase the power consumption for controlling the valves.

  Therefore, an object of the present invention is to provide a lubricating structure for an automatic transmission that can control the amount of lubricating oil supplied to a lubricating oil supply destination while suppressing power consumption.

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

  The invention according to claim 1 of the present application is a lubricating device for an automatic transmission that supplies lubricating oil to a predetermined lubricating oil supply destination in the automatic transmission, and the supply of the lubricating oil to the lubricating oil supply destination And a supply amount variable mechanism that varies a supply amount of lubricant to the lubricant supply destination by the valve means, and an actuator that drives the supply amount variable mechanism, and the supply amount is variable The mechanism is connected to the actuator via a gear meshing portion, and is configured to vary the amount of lubricating oil supplied to the lubricating oil supply destination by the valve means by the actuator.

  According to a second aspect of the present invention, there is provided the lubricating device for an automatic transmission according to the first aspect, further comprising a transmission mechanism having a plurality of frictional engagement elements, wherein the lubricating oil supply destination is the plurality of frictional engagements. It is characterized by including a frictional engagement element that is fastened at the start of the element.

  According to a third aspect of the present invention, in the lubricating device for an automatic transmission according to the first or second aspect, a predetermined hydraulic control valve and a hydraulic variable mechanism that varies a control hydraulic pressure by the hydraulic control valve. The hydraulic variable mechanism is configured to vary the control hydraulic pressure by the hydraulic control valve by the actuator.

  According to a fourth aspect of the present invention, in the lubricating device for an automatic transmission according to the third aspect, the hydraulic control valve is different from the lubricating oil supply destination to which the lubricating oil is supplied from the valve means. It is a valve for controlling the oil pressure of the lubricating oil supplied to the lubricating oil supply destination.

  According to a fifth aspect of the present invention, in the lubricating device for an automatic transmission according to the third or fourth aspect, the hydraulic control valve controls an original pressure of the lubricating oil supplied to the valve means. It is a valve.

  According to a sixth aspect of the present invention, in the lubricating device for an automatic transmission according to any one of the first to fifth aspects, 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.

  With the above configuration, according to the first aspect of the present invention, the valve means for controlling the supply of the lubricating oil to the predetermined lubricating oil supply destination, and the supply of the lubricating oil to the lubricating oil supply destination by the valve means A supply amount variable mechanism that varies the amount and an actuator that drives the supply amount variable mechanism are provided. The supply amount variable mechanism is connected to the actuator via a gear meshing portion, and is supplied to the lubricant supply destination by the valve means by the actuator. The lubricating oil supply amount is configured to be variable.

  As a result, by using a gear meshing portion that suppresses reverse drive from the supply amount variable mechanism to the actuator, power is supplied to the actuator when the amount of lubricant supplied to the lubricant supply destination by the valve means is maintained. In addition, since the supply amount variable mechanism can be driven by supplying electric power to the actuator only when the supply amount of the lubricant to the lubricant supply destination by the valve means is changed, the lubrication is performed while suppressing the power consumption. The supply amount of the lubricating oil supplied to the oil supply destination can be controlled.

  Further, according to the invention described in claim 2, the lubricating oil supply destination to which the supply of the lubricating oil is controlled by the valve means includes a friction fastening element that is fastened at the start of the plurality of friction fastening elements. A large amount of lubricating oil can be supplied to the frictional engagement element that is engaged at the time of starting to cool the frictional engagement element, and the above-described effect can be obtained effectively. For example, in an automatic transmission that eliminates a torque converter, when a frictional engagement element that is engaged at the time of starting is to be engaged while slipping, a large amount of lubricating oil is supplied to the frictional engagement element at the time of starting to cool the frictional engagement element. can do.

  According to a third aspect of the present invention, a predetermined hydraulic control valve and a hydraulic variable mechanism that varies a control hydraulic pressure by the hydraulic control valve are provided, and the hydraulic variable mechanism is controlled by the hydraulic control valve by the actuator. The hydraulic pressure is variable. Accordingly, it is possible to perform drive control of the supply amount variable mechanism and drive control of the hydraulic variable mechanism using a single actuator, and the above-described effect can be more effectively achieved. The number of parts and assembly processes can be reduced and the automatic transmission can be reduced in size as compared with the case where actuators are used for drive control of the variable supply mechanism and drive control of the hydraulic variable mechanism, respectively. .

  According to the invention described in claim 4, the hydraulic control valve is a valve that controls the hydraulic pressure of the lubricating oil supplied to the lubricating oil supply destination different from the lubricating oil supply destination to which the lubricating oil is supplied from the valve means. By using a single actuator, the drive control of the supply amount variable mechanism for changing the supply amount of the lubricant oil to the lubricant supply destination by the valve means, and the lubricant oil supply by which the lubricant oil is supplied from the valve means It is possible to perform drive control of a hydraulic variable mechanism that varies the control hydraulic pressure by a valve that controls the hydraulic pressure of the lubricating oil supplied to a different lubricating oil supply destination, and the above effect can be obtained effectively.

  According to the fifth aspect of the present invention, the hydraulic control valve is a valve that controls the original pressure of the lubricating oil supplied to the valve means, so that the lubricating oil by the valve means can be obtained using a single actuator. Drive control of a supply variable mechanism that varies the supply amount of lubricant to the supply destination and drive control of a hydraulic variable mechanism that varies the control oil pressure by a valve that controls the original pressure of the lubricant supplied to the valve means And the effect can be obtained effectively.

  According to the sixth aspect of the present invention, the regulation mechanism that regulates the output part of the transmission mechanism to the locked state or the unlocked state is provided, and the regulation mechanism locks the output part of the transmission mechanism by the actuator. It is configured to restrict to an unlocked state. Thus, using a single actuator, the drive control of the supply variable mechanism that changes the supply amount of lubricant to the lubricant supply destination by the valve means and the output part of the transmission mechanism are restricted to the locked state or the unlocked state. It is possible to perform drive control of the restricting mechanism to perform the above-described effect more effectively. 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 drive control of the supply amount variable mechanism and drive control of the restriction mechanism, respectively.

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 action | operation of the control mechanism which controls the output gear of a transmission mechanism in a locked state or an unlocked state. 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 2nd Embodiment of this invention. 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 also includes a controller 150 that controls the operation of the solenoid valve 101 for shifting, the actuator 102 for lubrication, the parking switching valve 103, and the like in the hydraulic control circuit 100. The controller 150 is operated by the operation of the driver. 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 150 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. 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 150 also outputs a control signal to the lubrication actuator 102 in the hydraulic control circuit 100 in accordance with 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 lubricant supply destinations 11, 12, and 13 are set, and a lubricant supply destination including a plurality of frictional engagement elements, a gear meshing portion, a bearing portion, and the like is set as the first lubricant supply destination 11. 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 150 outputs a control signal to the parking switching valve 103 based on the input signal, and when in the P range, sets the parking mechanism 55 to the first state of the locked state, and sets the N range, D range, and R range. When in the range, the parking mechanism 55 is controlled to be in the second state of the unlocked state. The controller 150 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 operation of the restriction mechanism that restricts the output gear of the speed change mechanism to a locked state or an unlocked state. As shown in FIG. 1, 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.

  As shown in FIGS. 1 and 3, the regulating mechanism 60 is a cam member that is integrally attached to a shaft member 113 that is coupled to the electric actuator 102 via a gear meshing portion 114 of a worm gear 111 and a worm wheel 112. 61 and a stopper member 63 having a substantially L-shaped cross section urged toward the parking rod 52 by a spring 62.

  The cam member 61 has an outer peripheral surface with a non-uniform distance from the center of the shaft member 113 corresponding to the rotation angle of the shaft member 113, and is rotated together with the shaft member 113 by the electric actuator 102. ing.

  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, and the parking rod 52 is moved in the axial direction. It comes to regulate that.

  The stopper member 63 is also in contact with the cam member 61 attached to the shaft member 113 at the other end of the stopper member 63, and resists the urging force of the spring 62 by contacting the protrusion 61 a of the cam member 61. Thus, it is moved to the side opposite to the parking rod 52, and the engagement between one end of the stopper member 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. 3 (a), when in the P range, the hydraulic pressure to the hydraulic cylinder 50 is discharged and the parking rod 52 is brought into 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. 3B, the worm wheel 112 is moved together with the shaft member 113 via the gear meshing portion 114 by operating the electric actuator 102 to rotationally drive the worm gear 111. Accordingly, the stopper member 63 is moved to the side opposite to the parking rod 52 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.

  Then, in the state where the engagement between the stopper member 63 and the second groove portion 56 of the parking rod 52 is released, the hydraulic pressure is supplied to the hydraulic cylinder 50 by controlling the parking switching valve 103 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. 3D, 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. 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 has an input port b to which the hydraulic pressure supplied by the oil pump 121 is input, an output port c that outputs to each of the lubricant supply destinations 11, 12, and 13 through the oil path 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.

  An orifice 137a is disposed in the oil passage 137 to the first lubricant supply destination 11, and the lubricant is supplied from the hydraulic control valve 105 to the first lubricant supply destination 11 via the orifice 137a. On the other hand, valve means for controlling the supply of the lubricating oil to the respective lubricating oil supply destinations 12 and 13 are respectively provided in 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. The flow rate control valves 106 and 107 are arranged, and the lubricating oil is supplied from the hydraulic control valve 105 to the second lubricating oil supply destination 12 and the third lubricating oil supply destination 13 via the flow rate control valves 106 and 107. The flow control valves 106 and 107 also have a pressure compensation function for maintaining the supply amount of the lubricating oil at a predetermined amount.

  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 has an input port f through which the lubricating oil is input from the hydraulic control valve 105 via the orifice 138 a provided in the oil passage 138, and an output that outputs the lubricating oil to the second lubricating oil supply destination 12. A port g and a drain port h are provided, a first control port e to which lubricating oil is supplied from the oil passage 138, and a second control port to which lubricating oil is supplied from the hydraulic control valve 105 via the orifice 138a. i is provided.

  The flow rate control valve 106 is supplied from the oil passage 138 by selectively connecting the output port g to the input port f and the drain port h when 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 d.

  When the hydraulic pressure of the lubricating oil supplied from the oil passage 138 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 e and the second control port i. The spool 106a moves in a direction to close the output port g, and the supply amount of the lubricating oil output from the output port g is controlled to a predetermined amount.

  In addition, when the hydraulic pressure of the lubricating oil supplied from the oil passage 138 becomes low, the spool 106a outputs as the differential pressure of the lubricating oil supplied to the first control port e and the second control port i decreases. The port g is moved in the opening direction, and the supply amount of the lubricating oil output from the output port g is controlled to a predetermined amount.

  The flow control valve 106 also includes a supply amount variable mechanism 120 that adjusts the biasing force of the spring 106b to vary the supply amount of the lubricant to the lubricant supply destination 12, and the supply amount variable mechanism 120 is a spool of the spring 106b. A spring receiving member 106c disposed on the side opposite to the side on which 106a is disposed, and a cam member 106d that contacts the spring receiving member 106c.

  The cam member 106d is integrally attached to a shaft member 113 connected to the electric actuator 102, which is a lubrication actuator, via a gear engaging portion 114, and is rotationally driven together with the shaft member 113 by the electric actuator 102. Yes.

  The cam member 106d has an outer peripheral surface with a non-uniform distance from the center of the shaft member 113 corresponding to the rotation angle of the shaft member 113. The cam member 106d is driven to rotate together with the shaft member 113 by the electric actuator 102. The receiving member 106c is moved in the axial direction of the spool 106a to adjust the urging force of the spring 106b.

  As described above, the urging force adjusting mechanism 120 is connected to the actuator 102 via the gear meshing portion 114, adjusts the urging force of the spring 106 b by the actuator 102, and supplies the lubricating oil to the lubricating oil supply destination 12 by the flow control valve 106. The supply amount is variable.

  The flow control valve 107 disposed in the oil passage 139 to the third lubricating oil supply destination 13 is also configured similarly to the flow control valve 106 disposed in the oil passage 138 to the second lubricating oil supply destination 12. . The flow rate control valve 107 is a lubrication that is supplied from an oil passage 139 with the output port selectively communicating with the input port and the drain port as the spool 107a moves in the axial direction against the urging force of the spring 107b. When the oil pressure of the oil becomes higher than a set pressure set by the urging force of the spring 107b, the oil is communicated with the drain port.

  When the hydraulic pressure of the lubricating oil supplied from the oil passage 139 increases, the flow rate control valve 107 moves in a direction in which the spool 107a closes the output port, and the hydraulic pressure of the lubricating oil supplied from the oil passage 139 decreases. In this case, the spool 107a moves in the direction to open the output port, and the supply amount of the lubricating oil output from the output port is controlled to a predetermined amount.

  The flow rate control valve 107 also includes a supply amount variable mechanism 130 that adjusts the biasing force of the spring 107b to vary the supply amount of the lubricant to the lubricant supply destination 13, and the supply amount variable mechanism 130 is a spool of the spring 107b. The spring receiving member 107c is disposed on the opposite side to the side on which the 107a is disposed, and the cam member 107d is in contact with the spring receiving member 107c.

  The cam member 107d is integrally attached to a shaft member 113 connected to the electric actuator 102, which is a lubrication actuator, via a gear engaging portion 114, and is rotationally driven together with the shaft member 113 by the electric actuator 102. Yes.

  The cam member 107d has an outer peripheral surface in which the distance from the center of the shaft member 113 is non-uniform corresponding to the rotation angle of the shaft member 113, and is rotated by the electric actuator 102 together with the shaft member 113 as a spring. The receiving member 107c is moved in the axial direction of the spool 107a to adjust the urging force of the spring 107b.

  In this way, the urging force adjusting mechanism 130 is connected to the actuator 102 via the gear meshing portion 114, adjusts the urging force of the spring 107 b by the actuator 102, and supplies the lubricating oil to the lubricating oil supply destination 13 by the flow rate control valve 107. The supply amount is variable.

  In the present embodiment, the flow control valve 106 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 lubrication. The flow control valve 107 disposed in the oil passage 139 to the oil 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.

  As described above, in the lubricating device for an automatic transmission according to the present embodiment, the valve means 106 and 107 for controlling the supply of the lubricating oil to the predetermined lubricating oil supply destinations 12 and 13 and the lubricating oil by the valve means 106 and 107. Supply amount variable mechanisms 120 and 130 that vary the supply amount of lubricating oil to the supply destinations 12 and 13 and an actuator 102 that drives the supply amount variable mechanisms 120 and 130 are provided. The actuator 102 is connected to the actuator 102 via a gear meshing portion 114, and the actuator 102 is configured to vary the supply amount of the lubricant oil to the lubricant oil supply destinations 12 and 13 by the valve means 106 and 107.

  Thus, the amount of lubricating oil supplied to the lubricating oil supply destinations 12 and 13 by the valve means 106 and 107 can be reduced by using the gear meshing portion 114 that suppresses the reverse drive from the supply amount variable mechanisms 120 and 130 to the actuator 102. When holding, without supplying electric power to the actuator 102, only when changing the supply amount of the lubricating oil to the lubricating oil supply destinations 12, 13 by the valve means 106, 107, the electric power is supplied to the actuator 102 and supplied. Since the variable mechanisms 106 and 107 can be driven, the supply amount of the lubricating oil supplied to the lubricating oil supply destinations 12 and 13 can be controlled while suppressing the power consumption.

  Further, the lubricant supply destination 12 to which the supply of the lubricating oil is controlled by the valve means 106 includes a friction fastening element that is fastened at the start of the plurality of friction fastening elements. A large amount of lubricating oil can be supplied when starting to cool the frictional engagement element. For example, in an automatic transmission that eliminates a torque converter, when a frictional engagement element that is engaged at the time of starting is to be engaged while slipping, a large amount of lubricating oil is supplied to the frictional engagement element at the time of starting to cool the frictional engagement element. can do.

  In addition, 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 uses the actuator 102 to regulate the output part of the transmission mechanism to a locked state or an unlocked state. Composed. Accordingly, the drive control of the supply amount variable mechanisms 120 and 130 for changing the supply amount of the lubricant oil to the lubricant oil supply destinations 12 and 13 by the valve means 106 and 107 and the output of the transmission mechanism using the single actuator 102. It is possible to perform drive control of the restriction mechanism 60 that restricts the portion to the locked state or the unlocked state. 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 driving control of the supply amount variable mechanisms 120 and 130 and driving control of the regulating mechanism 60, respectively. be able to.

  Next, an automatic transmission according to a second embodiment of the present invention will be described. The automatic transmission according to the second embodiment differs from the automatic transmission according to the first embodiment only in that a flow rate adjustment valve is used instead of the flow rate control valve, and only the flow rate adjustment valve will be described. The description of the same configuration as that of the automatic transmission according to the embodiment is omitted.

  FIG. 4 is a circuit diagram showing a configuration of a main part of the hydraulic control circuit of the automatic transmission according to the second embodiment of the present invention. As shown in FIG. 4, also in the hydraulic control circuit 200 of the automatic transmission according to the second embodiment of the present invention, the hydraulic pressure supplied from the oil pump 121 is controlled to a predetermined hydraulic pressure by the hydraulic control valve 105 and the lubricating oil To the lubricant supply destinations 11, 12, and 13.

  In the present embodiment, the supply of the lubricating oil to the respective lubricating oil supply destinations 12 and 13 is controlled in 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. As the valve means, the flow rate adjusting valves 206 and 207 for adjusting the supply amount of the lubricating oil by reducing the pressure to a predetermined pressure are arranged, and the second lubricating oil supply destination 12 is supplied from the hydraulic control valve 105 via the flow rate adjusting valves 206 and 207. The lubricating oil is supplied to the third lubricating oil supply destination 13.

  The flow rate adjusting valve 206 includes a spool 206a and a spring 206b that is disposed on one end side of the spool 206a and biases the spool 206a. The flow rate adjusting valve 206 also has an input port k through which oil pressure supplied by the oil pump 121 is input through the oil passage 138, an output port l that outputs the lubricating oil to the lubricating oil supply destination 12 through the oil passage 140, and a drain And a return port j to which lubricating oil is supplied from an oil passage 140 connected to the output port 1 through an orifice 140a.

  When the spool 206a moves in the axial direction against the urging force of the spring 206b, the output port l selectively communicates with the input port k and the drain port m, and the flow rate adjusting valve 206 outputs from the output port l. When the hydraulic pressure to be applied becomes higher than the set pressure set by the urging force of the spring 206b, etc., it communicates with the drain port m and supplies the lubricating oil under a predetermined hydraulic pressure.

  The flow rate adjustment valve 206 also includes a supply amount variable mechanism 220 that adjusts the biasing force of the spring 206b to vary the supply amount of the lubricant to the lubricant supply destination 12, and the supply amount variable mechanism 220 is a spool of the spring 206b. A spring receiving member 206c disposed on the side opposite to the side on which 206a is disposed, and a cam member 206d that contacts the spring receiving member 206c.

  The cam member 206d is integrally attached to a shaft member 113 connected to the electric actuator 102 via a gear meshing portion 114, and is rotated together with the shaft member 113 by the electric actuator 102.

  The cam member 206d has an outer peripheral surface with a non-uniform distance from the center of the shaft member 113 corresponding to the rotation angle of the shaft member 113. The cam member 206d is driven to rotate together with the shaft member 113 by the electric actuator 102. The receiving member 206c is moved in the axial direction of the spool 206a to adjust the urging force of the spring 206b.

  As described above, the urging force adjusting mechanism 220 is connected to the actuator 102 via the gear meshing portion 114, and adjusts the urging force of the spring 206 b by the actuator 102, and the lubricating oil supplied to the lubricating oil supply destination 12 by the flow rate adjusting valve 206. The supply amount is variable.

  The flow rate adjusting valve 207 disposed in the oil passage 139 to the third lubricating oil supply destination 13 is also configured in the same manner as the flow rate adjusting valve 206 disposed in the oil passage 138 to the second lubricating oil supply destination 12. . The flow rate adjusting valve 207 selectively communicates with the input port and the drain port when the spool 207a moves in the axial direction against the urging force of the spring 207b, and the hydraulic pressure output from the output port is reduced. When the pressure becomes higher than the set pressure set by the urging force of the spring 207b, etc., it communicates with the drain port and supplies the lubricating oil under a predetermined oil pressure.

  The flow rate adjustment valve 207 also includes a supply amount variable mechanism 230 that adjusts the biasing force of the spring 207b to vary the supply amount of the lubricant to the lubricant supply destination 13, and the supply amount variable mechanism 230 is a spool of the spring 207b. A spring receiving member 207c disposed on the side opposite to the side on which 207a is disposed, and a cam member 207d that contacts the spring receiving member 207c.

  The cam member 207 d is integrally attached to a shaft member 113 connected to the electric actuator 102 via a gear meshing portion 114, and is driven to rotate together with the shaft member 113 by the electric actuator 102.

  The cam member 207d also has an outer peripheral surface with a non-uniform distance from the center of the shaft member 113 corresponding to the rotation angle of the shaft member 113, and is rotated together with the shaft member 113 by the electric actuator 102. The spring receiving member 207c is moved in the axial direction of the spool 207a to adjust the urging force of the spring 207b.

  In this way, the urging force adjusting mechanism 230 is connected to the actuator 102 via the gear meshing portion 114, and adjusts the urging force of the spring 207 b by the actuator 102, and the lubricating oil supplied to the lubricating oil supply destination 13 by the flow rate adjusting valve 207. The supply amount is variable.

  As described above, also in the lubricating device for the automatic transmission according to the present embodiment, the valve means 206 and 207 for controlling the supply of the lubricating oil to the predetermined lubricating oil supply destinations 12 and 13 and the lubrication by the valve means 206 and 207 are performed. Supply amount variable mechanisms 220 and 230 that change the supply amount of lubricating oil to the oil supply destinations 12 and 13 and an actuator 102 that drives the supply amount variable mechanisms 220 and 230 are provided. The actuator 102 is connected to the actuator 102 via the gear meshing portion 114, and is configured to vary the supply amount of the lubricating oil to the lubricating oil supply destinations 12 and 13 by the valve means 206 and 207 by the actuator 102.

  Thus, when the amount of lubricating oil supplied to the lubricating oil supply destinations 12 and 13 by the valve means 206 and 207 is held, the lubricating oil supply destination 12 and the valve means 206 and 207 by the valve means 206 and 207 are supplied without supplying power to the actuator 102. Only when the supply amount of the lubricating oil to 13 is changed, power can be supplied to the actuator 102 to drive the supply amount variable mechanisms 206 and 207, so that the lubricating oil supply destination 12 can be controlled while suppressing the power consumption. , 13 can be controlled.

  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. 5 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. 5, the hydraulic pressure control circuit 300 of the automatic transmission according to the third embodiment of the present invention also controls the hydraulic pressure supplied by the oil pump 121, and the first lubricating oil supply destination 11 and the second lubricating oil are supplied. 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 has a spool 305 a and a spring 305 b that biases the spool 305 a, an input port b to which the hydraulic pressure supplied by the oil pump 121 is input, and each of the lubricant supply destinations 11, 12, 13. Are provided with an output port c for outputting through the oil passage 135 and a drain port d, and a return port a to which an oil passage branched from the oil passage 135 connected to the output port c is connected via an orifice 136a. 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 a hydraulic variable mechanism 310 that adjusts the urging force of the spring 305b to vary the hydraulic pressure controlled by the hydraulic control valve 305. The hydraulic variable mechanism 310 is on the side where the spool 305a of the spring 305b is disposed. And a cam member 305d that abuts against the spring receiving member 305c.

  The cam member 305 d is integrally attached to a shaft member 113 connected to the electric actuator 102 via a gear meshing portion 114, and is rotated together with the shaft member 113 by the electric actuator 102.

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

  Thus, the hydraulic pressure variable mechanism 310 is connected to the actuator 102 via the gear meshing portion 114, and is configured to adjust the urging force of the spring 305b by the actuator 102 to vary the control hydraulic pressure by the hydraulic control valve 305. Yes.

  Also in the present embodiment, the oil passage 135 connected to the output port c of the hydraulic control valve 305 has an oil passage 137 to the first lubricant supply destination 11 and a second lubricant supply destination 12 as shown in FIG. The oil passage 138 and the oil passage 139 to the third lubricating oil supply destination 13 are branched, and the oil pressure supplied from the oil pump 121 is controlled to a predetermined oil pressure by the oil pressure control valve 305 to supply each lubricating oil as lubricating oil. It is supplied to the destinations 11, 12, and 13.

  Lubricating oil is supplied from the hydraulic control valve 305 to the first lubricating oil supply destination 11 through the oil passage 137, and the original pressure of the lubricating oil is supplied from the hydraulic control valve 305 to the second lubricating oil supply destination 12 through the oil passage 138. Lubricating oil is supplied via the supplied flow control valve 106, and the third lubricating oil supply destination 13 is supplied via the flow control valve 107, which is supplied with the original pressure of the lubricating oil from the hydraulic control valve 305 through the oil passage 139. Lubricating oil is supplied.

  As described above, the lubricating device for the automatic transmission according to this embodiment also includes the valve means 106 and 107 for controlling the supply of the lubricating oil to the lubricating oil supply destinations 12 and 13 and the lubricating oil supply by the valve means 106 and 107. Supply amount variable mechanisms 120 and 130 that vary the supply amount of lubricating oil to the tips 12 and 13 and an actuator 102 that drives the supply amount variable mechanisms 120 and 130 are provided. The supply amount variable mechanisms 120 and 130 are actuators. 102 is connected via a gear meshing portion 114, and is configured to vary the amount of lubricating oil supplied to the lubricating oil supply destinations 12 and 13 by the valve means 106 and 107 by the actuator 102.

  Thus, when the amount of lubricating oil supplied to the lubricating oil supply destinations 12 and 13 by the valve means 106 and 107 is held, the lubricating oil supply destination 12 and the valve means 106 and 107 by the valve means 106 and 107 are not supplied without supplying power to the actuator 102. Only when the supply amount of the lubricating oil to 13 is changed, power can be supplied to the actuator 102 to drive the variable supply amount mechanisms 106 and 107, so that the lubricating oil supply destination 12 can be reduced while suppressing the power consumption. , 13 can be controlled.

  Further, a predetermined hydraulic control valve 305 and a hydraulic variable mechanism 310 that varies the hydraulic pressure controlled by the hydraulic control valve 305 are provided. The hydraulic variable mechanism 310 varies the control hydraulic pressure by the hydraulic control valve 305 by the actuator 102. Composed. Accordingly, it is possible to perform drive control of the supply amount variable mechanisms 120 and 130 and drive control of the hydraulic variable mechanism 310 using a single actuator 102. Compared to the case where actuators are used for drive control of the supply amount variable mechanisms 120 and 130 and drive control of the hydraulic variable mechanism 310, respectively, the number of parts and the assembly process can be reduced, and the automatic transmission can be downsized. Can be planned.

  The hydraulic control valve 305 is a valve that controls the hydraulic pressure of the lubricating oil supplied to the lubricating oil supply destination 11 different from the lubricating oil supply destinations 12 and 13 to which the lubricating oil is supplied from the valve means 106 and 107. , Drive control of the supply amount variable mechanisms 120 and 130 for changing the supply amount of the lubricating oil to the lubricating oil supply destinations 12 and 13 by the valve means 106 and 107 using the single actuator 102, and the valve means 106 and 107. Drive control of the hydraulic variable mechanism 310 that varies the control hydraulic pressure by a valve that controls the hydraulic pressure of the lubricating oil supplied to the lubricating oil supply destination 11 different from the lubricating oil supply destinations 12 and 13 to which the lubricating oil is supplied from Can do.

  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, it is possible to control the supply amount of lubricating oil supplied to a predetermined lubricating oil supply destination in the automatic transmission while suppressing power consumption. Or, there is a possibility of being suitably used in the field of manufacturing industries of vehicles equipped with the same.

11, 12, 13 Lubricating oil supply destination 60 Restriction mechanism 100, 200, 300 Hydraulic control circuit 101 Shift solenoid valve 102 Lubricating actuator 105, 305 Hydraulic control valve 106, 107, 207, 207 Flow control valve 114 Gear meshing portion 120 , 130, 220, 230 Supply amount variable mechanism 310 Hydraulic variable mechanism

Claims (6)

A lubricating device for an automatic transmission that supplies lubricating oil to a predetermined lubricating oil supply destination in the automatic transmission,
Valve means for controlling the supply of lubricating oil to the lubricating oil supply destination;
A supply amount variable mechanism that varies the supply amount of lubricant to the lubricant supply destination by the valve means;
An actuator for driving the supply amount variable mechanism;
With
The supply amount variable mechanism is connected to the actuator via a gear meshing portion, and is configured to vary the supply amount of the lubricant to the lubricant supply destination by the valve means by the actuator.
A lubricating device for an automatic transmission. A transmission mechanism having a plurality of frictional engagement elements;
The lubricating oil supply destination includes a friction fastening element that is fastened at the start of the plurality of friction fastening elements.
The lubricating device for an automatic transmission according to claim 1. A predetermined hydraulic control valve;
A hydraulic variable mechanism that varies the hydraulic pressure controlled by the hydraulic control valve;
With
The hydraulic variable mechanism is configured to vary a control hydraulic pressure by the hydraulic control valve by the actuator.
3. The lubricating device for an automatic transmission according to claim 1, wherein the lubricating device is an automatic transmission. The hydraulic control valve is a valve that controls the hydraulic pressure of the lubricating oil supplied to the lubricating oil supply destination different from the lubricating oil supply destination to which the lubricating oil is supplied from the valve means.
The lubricating device for an automatic transmission according to claim 3. The hydraulic control valve is a valve that controls an original pressure of lubricating oil supplied to the valve means.
The lubricating device for an automatic transmission according to claim 3 or 4, wherein the lubricating device is an automatic transmission. 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 lubricating device for an automatic transmission according to any one of claims 1 to 5, wherein the lubricating device is an automatic transmission.

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