JP2006052766A - Hydraulic pressure controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hydraulic pressure controller capable of improving efficiency of supply of oil supplied to a predetermined section from an oil holding device. <P>SOLUTION: In this hydraulic oil controller provided with a power transmission device 6 arranged in a path from a driving force source to a wheel, oil receiving devices 26, 37, 38 for controlling a power transmission condition in the power transmission device 6, and the oil holding device for supplying oil to the oil receiving devices 26, 37, 38, a plurality of oil holding devices 56 have first oil chambers 59, 72 connected with the oil receiving devices 26, 37, 38 and second oil chambers 60, 73 provided with pistons 61, 74 capable of operating among the first oil chambers 59, 72 and them. A first pressure receiving face and a second pressure receiving face are formed in the piston, and area of the second pressure receiving face is smaller than area of the first pressure receiving face. The piston has an oil supply amount controller 46 for increasing oil pressure in the second oil chamber to operate the piston and supply oil in the first oil chambers 59, 72 into the oil receiving devices 26, 37, 38. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a hydraulic control device that controls the state of a power transmission device of a vehicle by hydraulic pressure.

  Conventionally, a power transmission device is provided in a path from a driving force source of a vehicle to a wheel, and a hydraulic control device, an electromagnetic control device, and the like are known as a mechanism for controlling the state of the power transmission device. An example of a hydraulic control device for a vehicle is described in Patent Document 1. The vehicle described in Patent Document 1 has an engine, and the engine torque is transmitted to wheels via a torque converter, an automatic transmission, and a differential. The automatic transmission has a stepped gear transmission mechanism that can set a plurality of forward speeds and one reverse speed. Further, a C1 clutch that is engaged when the forward gear is selected and a C2 clutch that is engaged when the reverse gear is selected are provided. The C1 clutch and the C2 clutch are engaged when the supplied hydraulic pressure is increased, and are released when the hydraulic pressure is decreased.

  In addition, a hydraulic control device that controls the state of hydraulic oil supplied to the C1 clutch, the C2 clutch, the torque converter, and the like is provided, and the hydraulic control device includes an oil pump. The oil pump is configured to be driven by engine power, and hydraulic oil discharged from the oil pump is configured to be supplied to the manual valve via the primary regulator valve. An oil passage branched in two directions from the manual valve is formed. One oil passage is connected to the hydraulic chamber of the C1 clutch, and the other oil passage is connected to the hydraulic chamber of the C2 clutch. Further, a first oil passage and a second oil passage are arranged in parallel on a route from the manual valve to the hydraulic chamber of the C1 clutch. A switching valve is provided in the first oil passage, and an orifice is provided in the second oil passage. Further, a line pressure control solenoid for controlling the primary regulator valve is provided. Further, a clutch oil passage for connecting the primary regulator valve and the manual valve is provided, and an accumulator connected to the clutch oil passage is provided. This accumulator has a piston and a spring. Furthermore, an accumulator control solenoid is provided in a path from the clutch oil path to the accumulator.

  In the hydraulic control apparatus having the above configuration, the oil pump is driven by the engine power, and the hydraulic oil discharged from the oil pump is supplied to the clutch oil passage via the primary regulator valve. The hydraulic oil pressure in the clutch oil passage is controlled by a line pressure control solenoid. If any of the D position, 4 position, 3 position, 2 position, and L position is selected as the shift position, the hydraulic oil in the clutch oil passage passes through the manual valve to the hydraulic chamber of the C1 clutch. When supplied, the C1 clutch is engaged, and the hydraulic oil is discharged from the hydraulic chamber of the C2 clutch, and the C2 clutch is released. When eco-run control, which will be described later, is not executed, when the hydraulic oil is supplied to the hydraulic chamber of the C1 clutch, the switching valve is closed and the hydraulic oil passes through the second oil passage relatively slowly. Is supplied to the hydraulic chamber. On the other hand, when the R position is selected, the hydraulic oil in the clutch oil passage is supplied to the hydraulic chamber of the C2 clutch via the manual valve, the C2 clutch is engaged, and the C1 clutch The hydraulic oil is discharged from the hydraulic chamber, and the C1 clutch is released.

  In the vehicle described in Patent Document 1, eco-run control can be executed. For example, when the D position is selected and the vehicle is traveling in an urban area, an automatic stop condition, specifically, accelerator-off and brake-on, vehicle speed zero, etc. are detected while waiting for a signal at an intersection. The engine is automatically stopped. On the other hand, when the automatic stop condition cannot be satisfied, the engine is restarted. Thus, the eco-run control is a control for automatically stopping and restarting the engine when the automatic stop condition is satisfied or not satisfied. Here, when the eco-run control is executed, the engine is automatically stopped, so that the oil pump stops and no oil is supplied to the C1 clutch. For this reason, when the C1 clutch is engaged again after the engine is started, the engagement responsiveness may be lowered.

Therefore, in Patent Document 1, when the hydraulic oil is supplied to the C1 clutch when the engine is restarted, the rapid pressure increase control is executed. That is, by releasing the switching valve, the hydraulic oil is quickly supplied to the hydraulic chamber of the C1 clutch via the first oil passage, and the engagement of the C1 clutch is promoted. In addition to the rapid pressure increase control, the accumulator control solenoid is released, and the hydraulic oil stored in the accumulator is supplied to the hydraulic chamber of the C1 clutch via the clutch oil passage, and the hydraulic chamber of the C1 clutch The flow rate of the hydraulic oil supplied to the cylinder further increases.
JP 2002-115755 A

  Incidentally, in Patent Document 1 described above, the operating characteristics of the accumulator that promotes the increase in the amount of hydraulic oil supplied to the hydraulic chamber of the C1 clutch depend on the spring constant of the spring. For this reason, there is still room for improvement in terms of improving the supply efficiency of hydraulic oil to the hydraulic chamber of the C1 clutch.

  The present invention has been made against the background of the above circumstances, and an object of the present invention is to provide a hydraulic control device capable of improving the supply efficiency of oil supplied to a predetermined part from an oil holding device. is there.

  In order to achieve the above object, the invention of claim 1 is directed to a power transmission device arranged in a path from a driving force source to a wheel, to which oil is supplied, and based on the oil supply state, In a hydraulic control device including an oil receiving device that controls a power transmission state in a transmission device and an oil holding device that supplies oil to the oil receiving device, a plurality of the oil holding devices are provided, and a plurality of oil holding devices are provided. The apparatus includes a first oil chamber connected to the oil receiving device, and a second oil chamber in which an operable piston is interposed between the first oil chamber, Each piston in the plurality of oil holding devices is provided with a first pressure receiving surface that forms the first oil chamber and a second pressure receiving surface that forms the second oil chamber, respectively, Area of first pressure receiving surface Further, the area of the second pressure receiving surface is set to be narrower, and the first oil chamber is operated by increasing the oil pressure of the second oil chamber and operating each piston in a predetermined direction. An oil supply amount control device for supplying the oil to the oil receiving device is provided.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the oil supply amount control device controls a supply timing of oil supplied from the first oil chambers of the plurality of oil holding devices to the oil receiving device. , Each of which is further controlled.

  According to a third aspect of the present invention, in addition to the configuration of the second aspect, the oil supply amount control device controls a supply timing of oil supplied from the first oil chambers of the plurality of oil holding devices to the oil receiving device. It is characterized by further having a different structure for each oil holding device.

  In addition to the structure of Claim 2 or 3, the invention of Claim 4 was discharged from the first oil passage provided in the path from the first oil chamber to the oil receiving device, and the oil pump. When a second oil passage that supplies oil to the second oil chamber via the oil supply amount control device and the piston operates in a direction opposite to a predetermined direction, the oil in the oil pan is A third oil passage that supplies the first oil chamber; and a first oil passage that is provided in the first oil passage and that prevents oil from the oil receiving device from flowing back into the first oil chamber. A check valve and a second check valve that is provided in the third oil passage and prevents the oil in the first oil chamber from flowing back to the oil pan. It is a feature.

  According to a fifth aspect of the present invention, in addition to the structure of any of the first to fourth aspects, when the piston operates in a direction opposite to the predetermined direction, the oil discharged from the second oil chamber is A first lubricating oil passage for supplying a lubricating circuit for lubricating the power transmission device is further provided.

  According to a sixth aspect of the invention, in addition to the configuration of the fifth aspect, the oil supply amount control device also has a configuration as the first lubricating oil passage.

  According to a seventh aspect of the present invention, in addition to the structure of any one of the first to sixth aspects, the piston includes a first partition wall having the first pressure receiving surface and a second wall having the second pressure receiving surface. A partition wall is formed between the first partition wall and the second partition wall, and a back pressure chamber in which the hydraulic pressure is changed by the operation of the piston is formed. A second lubricating oil passage for supplying the lubricating circuit is provided.

  According to an eighth aspect of the invention, in addition to the configuration of the seventh aspect, a third reverse is provided in the second lubricating oil passage and prevents the oil in the lubricating circuit from flowing back into the back pressure chamber. A stop valve, a fourth oil passage for supplying oil from the oil pan to the back pressure chamber, and a fourth check valve for preventing the oil in the back pressure chamber from flowing back to the oil pan. It is characterized by that.

  The invention according to claim 9 controls the power transmission state in the power transmission device based on the power transmission device arranged in the path from the driving force source to the wheel, the oil being supplied, and the supply state of the oil. In the hydraulic control device including an oil receiving device and an oil holding device that supplies oil to the oil receiving device, the oil holding device includes a first oil chamber connected to the oil receiving device, and the first oil chamber. A second oil chamber in which an operable piston is interposed between the first oil chamber, the first pressure receiving surface forming the first oil chamber, and the second oil chamber. And a second pressure receiving surface that forms a second oil chamber, the area of the second pressure receiving surface is set to be smaller than the area of the first pressure receiving surface, and the second pressure receiving surface The oil pressure of the oil chamber is increased to move the piston in a predetermined direction When an oil supply amount control device for supplying oil in the first oil chamber to the oil receiving device by operating is provided, and when the piston operates in a direction opposite to the predetermined direction, A lubricating oil passage for supplying oil discharged from the second oil chamber to a lubricating circuit for lubricating the power transmission device is provided.

  According to a tenth aspect of the present invention, a power transmission device disposed in a path from the driving force source to the wheel, oil is supplied, and the power transmission state in the power transmission device is controlled based on the oil supply state. In the hydraulic control device including an oil receiving device and an oil holding device that supplies oil to the oil receiving device, the oil holding device includes a first oil chamber connected to the oil receiving device, and the first oil chamber. A second oil chamber in which an operable piston is interposed between the first oil chamber, the first pressure receiving surface forming the first oil chamber, and the second oil chamber. And a second pressure receiving surface that forms a second oil chamber, the area of the second pressure receiving surface is set to be smaller than the area of the first pressure receiving surface, and the second pressure receiving surface Increase the oil pressure in the oil chamber of the An oil supply amount control device for supplying the oil in the first oil chamber to the oil receiving device by operating the first oil chamber, and the piston has a first pressure receiving surface. A partition wall and a second partition oil chamber having the second pressure receiving surface are formed, and a back pressure whose hydraulic pressure is changed by the operation of the piston between the first partition wall and the second partition wall. A chamber is formed, and a lubricating oil passage for supplying oil from the back pressure chamber to a lubricating circuit for lubricating the power transmission device is provided.

  In the inventions of the ninth and tenth aspects, the number of the oil holding devices may be one or more.

  According to an eleventh aspect of the invention, in addition to the configuration of the seventh aspect, the oil is supplied to the common lubricating circuit from the second oil chamber and the back pressure chamber of all the oil retaining devices. One lubricating oil passage and the second lubricating oil passage are provided.

  According to a twelfth aspect of the present invention, in addition to the configuration of the seventh aspect, the lubrication circuit includes a first lubrication circuit and a second lubrication circuit, and the second oil of all the oil retaining devices. The first lubricating oil passage is provided so that oil is supplied from the chamber to the first lubricating circuit, and from the back pressure chamber of all the oil holding devices, the second lubricating circuit is provided. The second lubricating oil passage is provided so that oil is supplied to the oil.

  According to a thirteenth aspect of the present invention, in addition to the configuration of the seventh aspect, the lubrication circuit includes a first lubrication circuit and a second lubrication circuit, and the plurality of oil retaining devices include a first lubrication circuit. An oil retaining device and a second oil retaining device from the back pressure chamber of the first oil retaining device and the second oil chamber of the second oil retaining device. The second lubricating oil passage and the first lubricating oil passage are provided so that oil is supplied to the lubricating circuit, and the second oil chamber and the first lubricating oil passage of the first oil holding device are provided. The first lubricating oil passage and the second lubricating oil passage are provided so that oil is supplied from the back pressure chamber of the second oil holding device to the second lubricating circuit. It is what.

According to the first aspect of the invention, when the oil pressure supplied to the second oil chamber is increased to operate the piston, the oil in the first oil chamber is supplied to the oil receiving device. Here, the amount of oil supplied from the first oil chamber to the oil receiving device is obtained by the following equation, for example.
Oil amount of second oil chamber × (area of first pressure receiving surface / area of second pressure receiving surface)
That is, the flow rate of the oil supplied from the first oil chamber to the oil receiving device is larger than the flow rate of the oil supplied to the second oil chamber in the oil holding device, and is supplied to the oil receiving device. It is possible to increase the oil supply efficiency. Accordingly, it is possible to improve the hydraulic pressure increase response in the oil receiving device and improve the control response of the power transmission state in the power transmission device. Further, since a plurality of oil holding devices are provided, the amount of oil supplied from the oil holding device to the oil receiving device can be further increased, and it is necessary for the oil supply amount to reach a predetermined amount. Time can be shortened.

  According to the invention of claim 2, in addition to obtaining the same effect as that of the invention of claim 1, the supply timing of the oil supplied from the first oil chamber of the plurality of oil holding devices to the oil receiving device, Each can be controlled. Therefore, it is possible to control the oil supply timing according to the oil required timing in the oil receiving device.

  According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 2, the supply timing of the oil supplied from the first oil chambers of the plurality of oil holding devices to the oil receiving device is set. It is possible to vary for each oil holding device. Therefore, it is possible to more appropriately control the oil supply timing according to the oil required timing in the oil receiving device.

  According to the invention of claim 4, the oil discharged from the oil pump is supplied to the second oil chamber via the oil supply amount control device provided in the second oil passage. When the oil pressure in the second oil chamber rises and the piston moves in a predetermined direction, the oil discharged from the first oil chamber is supplied to the oil receiving device via the first oil passage. In this case, since the second check valve is closed, the oil in the first oil chamber is prevented from flowing back to the oil pan. On the other hand, when the piston operates in the direction opposite to the predetermined direction, Oil is supplied to the first oil chamber via the third oil passage. In this case, since the first check valve is closed, the oil in the oil receiving device can be prevented from flowing back into the first oil chamber.

  According to the invention of claim 5, in addition to obtaining the same effect as that of any of the inventions of claims 1 to 4, oil discharged from the second oil chamber can be supplied to the lubricating circuit. Therefore, a decrease in the amount of oil supplied to the lubrication circuit can be suppressed.

  According to the sixth aspect of the invention, in addition to the same effects as the fifth aspect of the invention, the oil discharged from the second oil chamber is supplied to the lubrication circuit via the oil supply amount control device. The

  According to the invention of claim 7, in addition to obtaining the same effect as that of any of the inventions of claims 1 to 6, the hydraulic pressure of the back pressure chamber is changed by the operation of the piston and is discharged from the back pressure chamber. Is supplied to the lubricating circuit via the second lubricating oil passage. Therefore, a decrease in the amount of oil supplied to the lubrication circuit can be suppressed.

  According to the eighth aspect of the invention, in addition to obtaining the same effect as that of the seventh aspect of the invention, it is possible to more reliably suppress a decrease in the amount of oil supplied to the lubricating circuit.

According to the ninth aspect of the present invention, when the hydraulic pressure of the oil supplied to the second oil chamber is increased and the piston is operated in a predetermined direction, the oil in the first oil chamber is supplied to the oil receiving device. Here, the amount of oil supplied from the first oil chamber to the oil receiving device is obtained by the following equation, for example.
Oil amount of second oil chamber × (area of first pressure receiving surface / area of second pressure receiving surface)
That is, the flow rate of the oil supplied from the first oil chamber to the oil receiving device is larger than the flow rate of the oil supplied to the second oil chamber in the oil holding device, and is supplied to the oil receiving device. It is possible to increase the oil supply efficiency. Accordingly, it is possible to improve the hydraulic pressure increase response in the oil receiving device and improve the control response of the power transmission state in the power transmission device. Further, when the piston moves in the direction opposite to the predetermined direction, the oil discharged from the second oil chamber is supplied to the lubricating circuit via the lubricating oil passage. Therefore, a decrease in the amount of oil supplied to the lubrication circuit can be suppressed.

According to the invention of claim 10, when the hydraulic pressure of the oil supplied to the second oil chamber is raised and the piston is operated in a predetermined direction, the oil in the first oil chamber is supplied to the oil receiving device. Here, the amount of oil supplied from the first oil chamber to the oil receiving device is obtained by the following equation, for example.
Oil amount of second oil chamber × (area of first pressure receiving surface / area of second pressure receiving surface)
That is, the flow rate of the oil supplied from the first oil chamber to the oil receiving device is larger than the flow rate of the oil supplied to the second oil chamber in the oil holding device, and is supplied to the oil receiving device. It is possible to increase the oil supply efficiency. Accordingly, it is possible to improve the hydraulic pressure increase response in the oil receiving device and improve the control response of the power transmission state in the power transmission device. Further, when the hydraulic pressure in the back pressure chamber changes due to the operation of the piston, the oil in the back pressure chamber is supplied to the lubricating circuit via the lubricating oil passage. Therefore, a decrease in the amount of oil supplied to the lubrication circuit can be suppressed.

  According to the eleventh aspect of the present invention, the same effect as that of the seventh aspect of the invention can be obtained, and the oil can be interrupted to the common lubricating circuit from the second oil chamber and the back pressure chamber in all the oil holding devices. It can be continuously supplied without any problems.

  According to the invention of claim 12, in addition to obtaining the same effect as that of the invention of claim 7, oil is supplied from the second oil chambers of all the oil holding devices to the first lubricating circuit, Oil is supplied to the second lubrication circuit from the back pressure chambers of all the oil holding devices. Therefore, oil can be continuously supplied to the first lubrication circuit and the second lubrication circuit without interruption.

  According to the invention of claim 13, oil is supplied from the back pressure chamber of the first oil holding device and the second oil chamber of the second oil holding device to the first lubricating circuit, and the first Oil is supplied to the second lubricating circuit from the second oil chamber of the oil holding device and the back pressure chamber of the second oil holding device. Therefore, oil can be continuously supplied to the first lubrication circuit and the second lubrication circuit without interruption.

  Next, FIG. 2 shows a power train of a vehicle having the hydraulic control device of the present invention and a control system of the vehicle. In the vehicle Ve shown in FIG. 2, a fluid transmission device 3, a lockup clutch 4, a forward / reverse switching device 5, a belt-type continuously variable transmission 6, and the like are provided on a power transmission path between the engine 1 and the wheels 2. ing. The fluid transmission device 3 and the lockup clutch 4 are provided in a power transmission path between the engine 1 and the forward / reverse switching device 5, and the fluid transmission device 3 and the lockup clutch 4 are arranged in parallel with each other. Has been. The fluid transmission device 3 is a device that transmits power by the kinetic energy of the fluid, and the lockup clutch 4 is a device that transmits power by a frictional force.

  Further, the forward / reverse switching device 5 is a device that selectively switches the rotation direction of the output member relative to the input member. The forward / reverse switching device 5 includes a planetary gear mechanism (not shown), a clutch (not shown) that controls the transmission state of power to the rotating element of the planetary gear mechanism, and the rotation / stop of the rotating element of the planetary gear mechanism. And a brake (not shown) for controlling the motor. And it is comprised so that the engagement pressure of friction engagement apparatuses, such as a clutch and a brake, may be controlled by oil_pressure | hydraulic.

  The belt type continuously variable transmission 6 is provided in a power transmission path between the forward / reverse switching device 5 and the wheels 2. The belt type continuously variable transmission 6 has a primary shaft 7 and a secondary shaft 8 arranged in parallel to each other. The primary shaft 7 is provided with a primary pulley 9, and the secondary shaft 8 is provided with a secondary pulley 10. The primary pulley 9 has a fixed sheave 11 fixed to the primary shaft 7 and a movable sheave 12 configured to be movable in the axial direction of the primary shaft 7. A groove M <b> 1 is formed between the fixed sheave 11 and the movable sheave 12.

  Further, a hydraulic servo mechanism 13 is provided for moving the movable sheave 12 in the axial direction of the primary shaft 7 so that the movable sheave 12 and the fixed sheave 11 approach and separate from each other. The hydraulic servo mechanism 13 includes a hydraulic chamber 13A and a piston (not shown) connected to the movable sheave 12 that can operate in the axial direction of the primary shaft 7 in accordance with the hydraulic pressure of the hydraulic chamber 13A. Yes.

  On the other hand, the secondary pulley 10 has a fixed sheave 14 fixed to the secondary shaft 8 and a movable sheave 15 configured to be movable in the axial direction of the secondary shaft 8. A V-shaped groove M <b> 2 is formed between the fixed sheave 14 and the movable sheave 15. In addition, a hydraulic servo mechanism 16 is provided that moves the movable sheave 15 in the axial direction of the secondary shaft 8 to bring the movable sheave 15 and the fixed sheave 14 closer to or away from each other. The hydraulic servo mechanism 16 includes a hydraulic chamber 26 and a piston (not shown) that can operate in the axial direction of the secondary shaft 8 by the hydraulic pressure of the hydraulic chamber 26 and is connected to the movable sheave 15. An endless belt 17 is wound around the primary pulley 9 and the secondary pulley 10 configured as described above.

  On the other hand, a hydraulic control device 18 having a function of controlling the hydraulic servo mechanisms 13 and 16 and the lockup clutch 4 and the forward / reverse switching device 5 of the belt type continuously variable transmission 6 is provided. The configuration of the hydraulic control device 18 will be described later. Further, an electronic control device 52 is provided as a controller for controlling the engine 1, the lockup clutch 4, the forward / reverse switching device 5, the belt type continuously variable transmission 6, and the hydraulic control device 18. The electronic control unit 52 includes an ignition switch signal, engine speed, accelerator pedal operation state, brake pedal operation state, throttle valve opening, shift position, primary shaft 7 rotation speed, and secondary shaft 8 rotation. A detection signal such as a number is input. Various data are stored in the electronic control unit 52. From the electronic control unit 52, a signal for controlling the engine 1, a signal for controlling the belt-type continuously variable transmission 6, and a signal for controlling the forward / reverse switching device 5 are stored. A signal for controlling the lock-up clutch 4 and a signal for controlling the hydraulic control device 18 are output.

  Next, the operation of the vehicle Ve shown in FIG. 2 will be described. The torque of the engine 1 is input to the forward / reverse switching device 5 via at least one of the fluid transmission device 3 and the lockup clutch 4. The torque output from the forward / reverse switching device 5 is transmitted to the wheels 2 via the belt type continuously variable transmission 6 to generate a driving force.

  In the belt type continuously variable transmission 6, the flow rate of oil supplied to the hydraulic chamber 13 </ b> A is controlled, and the thrust that moves the movable sheave 12 of the primary pulley 9 in the axial direction changes. Further, the hydraulic pressure in the hydraulic chamber 26 is controlled, and the thrust that moves the movable sheave 15 of the secondary pulley 10 in the axial direction changes. The width of the groove M1 changes according to the operation of the movable sheave 12 in the axial direction, and the width of the groove M2 changes according to the operation of the movable sheave 15 in the axial direction. As described above, the amount of oil supplied to the hydraulic chamber 13A is controlled to control the gear ratio of the belt-type continuously variable transmission 6, and the hydraulic pressure in the hydraulic chamber 26 is controlled to be applied to the belt 17. The clamping pressure changes, and the torque capacity of the belt type continuously variable transmission 6 is adjusted.

  On the other hand, in the vehicle Ve shown in FIG. 2, basically, the operation and stop of the engine 1 can be selectively switched based on the signal of the ignition switch. Further, it is possible to control operation and stop of the engine 1 based on conditions other than the ignition switch signal. For example, when the engine 1 is operated, the drive position is selected as the shift position, the accelerator pedal is returned, the brake pedal is depressed, and the vehicle Ve is stopped. When all of the above are detected, it is determined that the stop condition is satisfied, and control for stopping the engine 1 can be executed. Further, when the stop condition is satisfied and the engine 1 is stopped, when at least one of the above items is not detected, it is determined that the return condition is satisfied, and the engine 1 is operated. Control to start can be executed. Next, specific configurations of the hydraulic control device 18 that controls the lockup clutch 4, the forward / reverse switching device 5, and the belt-type continuously variable transmission 6 will be sequentially described.

  A first embodiment of the hydraulic control device 18 is shown in FIG. The first embodiment corresponds to the first to fourth aspects of the invention. The hydraulic control device 18 shown in FIG. 1 has an oil pump 30 driven by the engine 1. The oil pump 30 has a suction port 31 and a discharge port 32, and an oil passage 34 that connects the suction port 31 and the oil pan 33 is provided.

  On the other hand, an oil passage 36 is connected to the discharge port 32, and an oil passage 38 connected to the hydraulic chamber 26 and a hydraulic chamber 37 for a friction engagement device of the forward / reverse switching device 5 is formed. The friction engagement device includes a brake and a clutch, and each has a hydraulic chamber. However, for the sake of convenience, it will be described as one hydraulic chamber 37. A line pressure control valve 39 is provided in the path from the oil path 36 to the oil path 38. The line pressure control valve 39 includes a spool 39A, an input port 40, a drain port 41, a feedback port 42, a control port 44, and an elastic member 43. The input port 40 and the feedback port 42 are connected to the oil passage 36, and the drain port 41 is connected to the oil passage 38. The biasing force applied to the spool 39A according to the pressing force of the elastic member 43 and the hydraulic pressure of the control port 44 and the biasing force applied to the spool 39A according to the hydraulic pressure of the feedback port 42 are configured to be in opposite directions. ing.

  Further, a switching valve 46 connected to the oil passage 36 is provided. The switching valve 46 includes a spool 46A, an input port 47, output ports 48 and 49, drain ports 50 and 51, an elastic member 52, and a solenoid 53. Here, the input port 47 is connected to the oil passage 36, the output port 48 is connected to the oil passage 54, and the output port 49 is connected to the oil passage 55. An oil passage 56 is connected to the drain port 50, and an oil passage 57 is connected to the drain port 51. Further, the urging force applied to the spool 46A from the elastic member 52 and the urging force applied to the spool 46A based on the magnetic attraction force formed by the energization of the solenoid 53 are configured in opposite directions.

  Furthermore, an accumulator 58 connected to the oil passages 38, 54, 56 is provided. The accumulator 58 has a piston 61 that is disposed between the first oil chamber 59 and the second oil chamber 60 and is operable in the axial direction. The first oil chamber 59 is connected to the oil passage 56, and the second oil chamber 60 is connected to the oil passage 54. The piston 61 has a large-diameter portion 62 and a small-diameter portion 63, the end surface 64 of the large-diameter portion 62 is disposed facing the first oil chamber 59, and the end surface 65 of the small-diameter portion 63 is the second surface. It is arranged facing the oil chamber 60. In the plane orthogonal to the axial direction of the piston 61, the area of the second oil chamber 60 and the area of the end face 65 are set to be substantially the same, and the area of the first oil chamber 59 and the area of the end face 64 are substantially the same. Is set. Further, in the plane orthogonal to the axial direction of the piston 61, the areas of the second oil chamber 60 and the end face 65 are set to be narrower than the areas of the first oil chamber 59 and the end face 64.

  Further, the accumulator 58 has an elastic member 66, and a force that urges the piston 61 in the axial direction is applied from the elastic member 66. Specifically, a force is applied in such a direction that the volume of the second oil chamber 60 is reduced by the operation of the piston 61. A back pressure chamber 67 is formed between the large diameter portion 62 and the small diameter portion 63, and the back pressure chamber 67 communicates with the atmosphere via a passage 68.

  Furthermore, a check valve 69 is provided in a path from the oil path 56 to the oil pan 33. The check valve 69 has a configuration that allows the oil in the oil pan 33 to flow into the oil passage 56 and prevents the oil in the oil passage 56 from flowing back into the oil pan 33. Furthermore, a check valve 70 is provided between the oil passage 56 and the oil passage 38. The check valve 70 has a configuration that allows the oil in the first oil chamber 59 to flow into the oil passage 38 and prevents the oil in the oil passage 38 from flowing back into the oil passage 56. .

  Further, in addition to the accumulator 58, an accumulator 71 connected to the oil passages 38, 55, and 57 is provided. The accumulator 71 has a piston 74 that is disposed between the first oil chamber 72 and the second oil chamber 73 and is operable in the axial direction. The first oil chamber 72 is connected to the oil passage 57, and the second oil chamber 73 is connected to the oil passage 55. The piston 74 has a large-diameter portion 75 and a small-diameter portion 76, the end surface 77 of the large-diameter portion 75 is disposed facing the first oil chamber 72, and the end surface 78 of the small-diameter portion 76 is the second surface. It is arranged facing the oil chamber 73. In the plane orthogonal to the axial direction of the piston 74, the area of the second oil chamber 73 and the area of the end surface 78 are set to be approximately the same, and the area of the first oil chamber 72 and the area of the end surface 77 are approximately the same. Is set. Further, in the plane orthogonal to the axial direction of the piston 74, the areas of the second oil chamber 73 and the end surface 78 are set to be narrower than the areas of the first oil chamber 72 and the end surface 77.

  Further, the accumulator 74 has an elastic member 79, and a force that urges the piston 74 in the axial direction is applied from the elastic member 79. Specifically, a force is applied in such a direction that the volume of the second oil chamber 73 is reduced by the operation of the piston 74. A back pressure chamber 80 is formed between the large diameter portion 75 and the small diameter portion 76, and the back pressure chamber 80 communicates with the atmosphere via a passage 81.

  Furthermore, a check valve 82 is provided in the path from the oil path 57 to the oil pan 33. The check valve 82 is configured to allow the oil in the oil pan 33 to flow into the oil passage 57 and prevent the oil in the oil passage 57 from flowing back into the oil pan 33. Furthermore, a check valve 83 is provided between the oil passage 57 and the oil passage 38. The check valve 83 has a configuration that allows the oil in the first oil chamber 72 to flow into the oil passage 38 and prevents the oil in the oil passage 38 from flowing back into the oil passage 57. .

  Further, a line pressure control valve 84 for controlling the oil pressure in the oil passage 38 is provided. The line pressure control valve 84 includes a spool 85, an input port 86, a drain port 87, a control port 88, a feedback port 89, and an elastic member 90. The input port 86 and the feedback port 89 are connected to the oil passage 38, and the drain port 87 is connected to the lubrication circuit 92 via the oil passage 91.

  Further, the urging force applied to the spool 85 according to the hydraulic pressure of the feedback port 89 and the urging force applied to the spool 85 according to the pressing force of the elastic member 90 and the hydraulic pressure of the control port 88 are opposite to each other. Has been. The line pressure control valve 84 controls the oil pressure of the oil passage 38, and applies an urging force according to the oil pressure of the feedback port 89, an urging force of the elastic member 90, and a signal oil pressure of the control port 88. The oil pressure of the oil passage 38 is controlled based on the force. Although not shown in FIG. 1, an oil passage for supplying oil discharged from the oil pump 30 to the hydraulic chamber 13A is also provided.

  Next, the function of the hydraulic control device 18 will be described. As described above, in the vehicle Ve, it is possible to control the stop and operation of the engine 1 based on conditions other than the signal of the ignition switch, that is, stop conditions and return conditions. As described above, the situation where the stop and the operation of the engine 1 are controlled based on the stop condition and the return condition include a situation where the user encounters a traffic jam or waiting for a signal while traveling in an urban area. In such a situation, when the engine 1 is stopped and then the engine 1 is started, it is necessary to improve the startability of the vehicle Ve. According to the hydraulic control device 18 of FIG. It is possible to cope with such a request.

  First, as described above, when the stop condition is satisfied and the engine 1 is stopped, the oil pump 30 is stopped, and oil (pressure oil) is not discharged from the oil pump 30 to the oil passage 36. Accordingly, the amount of oil in the hydraulic chambers 26 and 37 is reduced, the friction engagement device in the forward / reverse switching device 5 is released, and the transmission torque of the belt type continuously variable transmission 6 is reduced. When the engine 1 is stopped and the return condition is satisfied and the engine 1 is started, the oil pump 30 is driven by the power of the engine 1. When the oil pump 30 is driven, the oil in the oil pan 33 is sucked and discharged to the oil passage 36.

  Immediately after the engine 1 is started, when the oil pressure in the oil passage 36 is equal to or lower than a predetermined pressure, the input port 40 and the drain port 41 of the line pressure control valve 39 are shut off. That is, the line pressure control valve 39 is in a closed state. Note that the oil pressure of the oil passage 36 for opening the line pressure control valve 39, that is, the valve opening pressure is controlled by the signal pressure of the control port 44. Thus, when the line pressure control valve is closed, for example, when the solenoid 53 of the switching valve 46 is energized, the spool 46A operates downward in FIG. Then, the input port 47 and the output port 48 are connected, the drain port 50 is shut off, and the output port 49 and the drain port 51 are connected. Thus, the state in which the input port 47 and the output port 48 are connected, the drain port 50 is shut off, and the output port 49 and the drain port 51 are connected is “the switching valve 46 is on”. It is.

  First, the operation of the accumulator 58 when the switching valve 46 is controlled to be on will be described. When the oil in the oil passage 36 is supplied to the second oil chamber 60 via the oil passage 54, the oil pressure in the second oil chamber 60 rises, and the piston 61 operates in the right direction in FIG. Oil is held in the first oil chamber 59 in advance, and the hydraulic pressure of the first oil chamber 59 increases as the piston 61 operates, and the oil is discharged to the oil passage 56. Here, when the oil pressure in the oil passage 56 is higher than the oil pressure in the oil passage 38, the check valve 70 is opened and the oil in the first oil chamber 59 is supplied to the oil passage 38. When the oil pressure in the oil passage 56 rises, the check valve 69 is closed, so that the oil in the oil passage 56 is not discharged to the oil pan 33.

  Next, the operation of the accumulator 71 when the switching valve 46 is controlled to be in the on state will be described. When the output port 49 of the switching valve 46 and the drain port 51 are connected, in the accumulator 71, the hydraulic pressure of the second oil chamber 73 decreases and the urging force of the elastic member 79 causes the piston 74 in FIG. Move left. Then, the first oil chamber 72 becomes negative pressure, the check valve 82 is released, and the oil in the oil pan 33 is sucked into the first oil chamber 72. Further, the hydraulic pressure of the second oil chamber 73 is increased by the operation of the piston 74, and the oil discharged from the second oil chamber 73 is supplied to the first oil chamber 72 via the oil passages 55 and 57. The When the first oil chamber 72 has a negative pressure, the check valve 83 is closed, so that the oil in the oil passage 38 does not flow into the oil passage 57.

  As described above, when the control for rapidly increasing the amount of oil supplied to the oil passage 38 is continued even after the oil in the first oil chamber 59 in the accumulator 58 is supplied to the oil passage 38, the switching is performed. The solenoid 53 of the valve 46 is controlled to be in a non-energized state. Then, the spool 46A is moved upward in FIG. 1 by the urging force of the elastic member 52, the drain port 50 and the output port 48 are connected, the input port 47 is shut off, and the input port 47 and the output port 49 are connected. And are connected. Thus, the state in which the drain port 50 and the output port 48 are connected, the input port 47 is shut off, and the input port 47 and the output port 49 are connected is the “off state of the switching valve 46”. It is.

  Thus, when the switching valve 46 is controlled to be in the OFF state, the operation of the accumulator 71 will be described first. When the oil in the oil passage 36 is supplied to the second oil chamber 73 via the oil passage 55, the hydraulic pressure in the second oil chamber 73 increases, and the piston 74 operates in the right direction in FIG. The oil is sucked into the second oil chamber 72 as described above, and the hydraulic pressure in the first oil chamber 72 increases as the piston 74 operates, and the oil is discharged to the oil passage 57. . Here, when the oil pressure in the oil passage 57 is higher than the oil pressure in the oil passage 38, the check valve 83 is opened and the oil in the first oil chamber 72 is supplied to the oil passage 38. When the oil pressure in the oil passage 57 rises, the check valve 82 is closed, so that the oil in the oil passage 57 is not discharged to the oil pan 33.

  Next, the operation of the accumulator 58 when the switching valve 46 is controlled to be in the OFF state will be described. When the output port 48 of the switching valve 46 and the drain port 50 are connected, in the accumulator 58, the hydraulic pressure of the second oil chamber 60 decreases and the urging force of the elastic member 66 causes the piston 61 to move in FIG. Move left. Then, the first oil chamber 59 becomes negative pressure, the check valve 69 is opened, and the oil in the oil pan 33 is sucked into the first oil chamber 59. Further, the hydraulic pressure of the second oil chamber 60 is increased by the operation of the piston 61, and the oil discharged from the second oil chamber 60 is supplied to the first oil chamber 59 via the oil passages 54 and 56. The When the first oil chamber 59 becomes negative pressure, the check valve 70 is closed, so that the oil in the oil passage 38 does not flow into the oil passage 56. When it is necessary to increase the amount of oil supplied to the oil passage 38 abruptly, the energization / non-energization of the solenoid 53 of the switching valve 46 is alternately switched at a predetermined cycle, whereby the first accumulator 58 is switched. Oil can be supplied to the oil passage 38 alternately and continuously from the oil chamber 59 and the first oil chamber 72 of the accumulator 71.

  On the other hand, when it is no longer necessary to rapidly increase the amount of oil supplied to the oil passage 38, the signal pressure input to the control port 44 of the line pressure control valve 39 is reduced. Then, the spool 39A operates downward in FIG. 1 due to the increase in the hydraulic pressure of the feedback port 42, the line pressure control valve 39 is opened, and the oil in the oil passage 36 passes through the line pressure control valve 39 to the oil passage 38. To be supplied.

  As described above, the oil supplied to the oil passage 38 is supplied to the hydraulic chambers 26 and 37, and the clamping force applied to the belt 17 from the secondary pulley 10 increases and the friction engagement device of the forward / reverse switching device 5. The engagement pressure is increased. Therefore, when the vehicle Ve starts, the transmission torque of the forward / reverse switching device 5 and the transmission torque of the belt type continuously variable transmission 6 are increased.

  When the spool 61 of the accumulator 58 operates in the right direction in FIG. 1, the back pressure chamber 67 has a low pressure, and outside air is sucked into the back pressure chamber 67. On the other hand, when the spool 61 of the accumulator 58 operates in the left direction in FIG. 1, the back pressure chamber 67 becomes high pressure, and the air in the back pressure chamber 67 is exhausted to the atmosphere. Further, when the spool 74 of the accumulator 71 operates in the right direction in FIG. 1, the back pressure chamber 80 becomes low pressure, and outside air is sucked into the back pressure chamber 80. On the other hand, when the spool 74 of the accumulator 71 operates in the left direction in FIG. 1, the back pressure chamber 80 becomes high pressure, and the air in the back pressure chamber 80 is exhausted to the atmosphere. Therefore, the operations of the spools 61 and 74 are maintained well.

  By the way, the oil pressure of the oil passage 38 is input to the feedback port 89 of the line pressure control valve 84. When the oil pressure of the oil passage 38 is equal to or lower than a predetermined pressure, the input port 86 and the drain port 87 are shut off. Yes. When the oil pressure in the oil passage 38 exceeds a predetermined pressure, the spool 85 operates downward in FIG. 1 to connect the input port 86 and the drain port 87, and the oil in the oil passage 38 passes through the oil passage 91. Via the lubrication circuit 92. The lubrication circuit 92 supplies oil to the friction engagement device in the forward / reverse switching device 5, the belt-type continuously variable transmission 6, and the like to lubricate and cool these parts. Further, when the oil pressure in the oil passage 38 decreases, the spool 85 operates upward in FIG. 1 by the biasing force of the elastic member 90, and the flow rate of oil discharged from the oil passage 38 to the oil passage 91 decreases. Thus, the spool 85 operates in accordance with the hydraulic pressure input to the feedback port 89, and the hydraulic pressure in the oil passage 38 is controlled by the line pressure control valve 84.

  Thus, in the first embodiment, in the first half of the case where the stopped engine 1 is started and the oil discharged from the oil pump 30 is supplied to the oil passage 38, the second oil chamber 60 or The flow rate of oil supplied from the first oil chamber 59 or the second oil chamber 72 to the hydraulic chambers 26 and 37 via the oil passage 38 rather than the flow rate of oil supplied to the second oil chamber 73. It is possible to increase the supply efficiency of the oil supplied to the oil passage 38 and the hydraulic chambers 26 and 37. For this reason, the rising response of the hydraulic pressure in the oil passage 38 and the hydraulic chambers 26 and 37 can be improved, and the reliability of the hydraulic control device 18 is improved. Accordingly, the control response of the transmission torque in the forward / reverse switching device 5 and the belt-type continuously variable transmission 6 is improved, the slip of the friction engagement device in the forward / backward switching device 5 and the belt 17 in the belt-type continuously variable transmission 6 are improved. Slip can be suppressed and the starting performance of the vehicle Ve is improved. Further, in the first embodiment, since the oil can be supplied to the oil passage 38 by the plurality of accumulators 58 and 71, the amount of oil supplied to the oil passage 38 can be increased. It is possible to shorten the time required to supply the required oil amount. Furthermore, the volume of the first oil chamber in each of the single accumulators 58 and 71 can be reduced.

  Further, in the first embodiment, after the engine 1 enters the operating state, control is performed to maintain the switching valve 46 in either the on state or the off state. In such a situation, when the condition for abruptly changing the gear ratio of the belt-type continuously variable transmission 6 is established and the required oil amount in the oil passage 38 increases, the state of the switching valve 46 is changed from on to off, Alternatively, it is also possible to supply oil from the accumulators 58 and 71 to the oil passage 38 by executing control for switching from OFF to ON. Therefore, the shift response in the belt type continuously variable transmission 6 is improved.

  In the first embodiment, when the solenoid 53 of the switching valve 46 is switched between energization and non-energization, the timing for supplying oil from the accumulator 58 to the oil passage 38, and the timing for supplying oil from the accumulator 71 to the oil passage 38, Can be different. In other words, oil can be alternately supplied from the accumulator 58 and the accumulator 71 to the oil passage 38. That is, at the time when oil is sucked into the first oil chamber by one accumulator, it is possible to supply oil from the first oil chamber to the oil passage 38 by the other accumulator, Even when the oil is supplied over the oil, the oil is continuously supplied. Therefore, it is possible to secure a necessary oil supply amount in the oil passage 38 even when sudden deceleration is performed after rapid increase in speed by the belt type continuously variable transmission 6. Further, even when the supply timing of the oil supplied from one accumulator is deviated from the required oil timing in the oil passage 38, the required oil timing in the oil passage 38 is obtained by supplying the oil from the other accumulator. It is possible to avoid a shortage of oil due to a difference in actual oil supply timing.

  Here, the correspondence relationship between the configuration of the first embodiment and the configuration of the present invention will be described. The engine 1 corresponds to the driving force source in the present invention, and the forward / reverse switching device 5 and the belt type continuously variable transmission 6 include: The oil passage 38 and the hydraulic chambers 26 and 37 correspond to the oil receiving device in the present invention, the accumulators 58 and 71 correspond to the oil holding device in the present invention, and the end faces 64 and 77 correspond to the power transmission device in the present invention. Corresponds to the first pressure receiving surface in the present invention, the end surfaces 65 and 78 correspond to the second pressure receiving surface in the present invention, and the switching valve 46 and the electronic control device 52 are the oil supply amount control device in the present invention. The oil passage 38 corresponds to the first oil passage of the present invention, the oil passages 36, 54, and 55 correspond to the second oil passage of the present invention, and the oil passages 56 and 57 correspond to this. In the third oil passage of the invention Those, and check valves 70,83 is equivalent to a first check valve of the present invention, the check valve 69,82 correspond to the second check valve of the present invention.

  Next, another embodiment of the hydraulic control device 18 will be described with reference to FIG. The second embodiment corresponds to the first, second, third, fifth, sixth and ninth aspects of the invention. In the configuration of the second embodiment, the same components as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment. In the second embodiment, the drain ports 50 and 51 of the switching valve 46 are connected to the lubricating circuit 92 via the oil passage 93. That is, the drain port 50 is not connected to the oil passage 56, and the drain port 51 is not connected to the oil passage 57. In the second embodiment, the same components and effects as those of the first embodiment produce the same effects as the first embodiment. By the way, in the second embodiment, when the switching valve 46 is controlled to be in the ON state, the oil in the second oil chamber 78 in the accumulator 71 passes through the oil passage 55 and the oil passage 93 to the lubricating circuit 92. Supplied. On the other hand, when the switching valve 46 is controlled to be in the OFF state, the oil in the second oil chamber 60 in the accumulator 58 is supplied to the lubricating circuit 92 via the oil passage 54 and the oil passage 93. Therefore, oil shortage in the lubrication circuit 92 can be avoided.

  Here, the correspondence between the configuration of the second embodiment and the configuration of the present invention will be described. The oil passages 54, 55, 93 and the switching valve 46 correspond to the lubricating oil passage and the first lubricating oil passage in the present invention. The engine 1 corresponds to the driving force source of the present invention.

  Next, another embodiment of the hydraulic control device 18 will be described with reference to FIG. The third embodiment corresponds to the first, second, third, seventh, eighth and tenth aspects of the present invention. In the configuration of the third embodiment, the same components as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment. In the third embodiment, the passages 68 and 81 are connected to the lubrication circuit 92. The passage 68 is provided with a check valve 94, and the passage 81 is provided with a check valve 95. The check valve 94 has a configuration that allows the oil in the back pressure chamber 67 to be sent to the lubrication circuit 92 and prevents the oil in the lubrication circuit 92 from flowing back into the back pressure chamber 67. The check valve 95 allows the oil in the back pressure chamber 72 to be sent to the lubrication circuit 92 and prevents the oil in the lubrication circuit 92 from flowing back into the back pressure chamber 72. Yes.

  The back pressure chamber 67 is connected to the oil pan 33 via an oil passage 96, and a check valve 97 is provided in the oil passage 96. Further, the back pressure chamber 80 is connected to the oil pan 33 through an oil passage 98, and a check valve 99 is provided in the oil passage 98. The check valve 97 allows the oil in the oil pan 33 to be sucked into the back pressure chamber 67 and prevents the oil in the back pressure chamber 67 from flowing back into the oil pan 33. . The check valve 99 has a configuration that allows the oil in the oil pan 33 to be sucked into the back pressure chamber 80 and prevents the oil in the back pressure chamber 80 from flowing back into the oil pan 33. ing.

  In the third embodiment, the same components and effects as those of the first embodiment produce the same effects as the first embodiment. In the third embodiment, when the switching valve 46 is controlled to be on and the piston 61 of the accumulator 58 moves rightward in FIG. 1, the back pressure chamber 67 becomes negative pressure and the check valve 97 becomes negative. Is released, and the oil in the oil pan 33 is sucked into the back pressure chamber 67 via the oil passage 96. In this case, since the check valve 94 is closed, the oil in the lubricating circuit 92 does not flow back into the back pressure chamber 67. In parallel with the above operation, in the accumulator 71, when the piston 74 moves leftward in FIG. 1, the hydraulic pressure in the back pressure chamber 80 rises, the check valve 95 is opened, and the oil in the back pressure chamber 80 is lubricated. This is supplied to the circuit 92. In this case, since the check valve 99 is closed, the oil in the back pressure chamber 80 is not discharged to the oil pan 33.

  On the other hand, when the switching valve is controlled to be turned off and the piston 74 of the accumulator 71 moves rightward in FIG. 1, the back pressure chamber 80 becomes negative pressure and the check valve 99 is opened. Oil in the oil pan 33 is sucked into the back pressure chamber 80 via the oil passage 98. In this case, since the check valve 95 is closed, the oil in the lubricating circuit 92 does not flow back into the back pressure chamber 80. In parallel with the above operation, in the accumulator 58, when the piston 74 moves leftward in FIG. 1, the hydraulic pressure in the back pressure chamber 67 rises, the check valve 94 is opened, and the oil in the back pressure chamber 67 is lubricated. This is supplied to the circuit 92. In this case, since the check valve 97 is closed, the oil in the back pressure chamber 80 is not discharged to the oil pan 33. Thus, also in Example 3, the oil shortage in the lubrication circuit 92 can be avoided. Here, the correspondence between the configuration of the third embodiment and the configuration of the present invention will be described. The large diameter portions 62 and 75 correspond to the first partition wall of the present invention, and the small diameter portions 63 and 76 correspond to the present invention. The oil passages 68 and 81 correspond to the lubricating oil passage and the second lubricating oil passage in the present invention, and the check valves 94 and 95 correspond to the third check valve of the present invention. The oil passages 96 and 98 correspond to the fourth oil passage of the present invention, and the check valves 97 and 99 correspond to the fourth check valve of the present invention. The correspondence between the other configurations in the third embodiment and the configuration of the present invention is the same as the correspondence between the configurations of the first and second embodiments and the configuration of the present invention.

  Next, another embodiment of the hydraulic control device 18 will be described with reference to FIG. The fourth embodiment corresponds to the first to eleventh aspects of the present invention. In the configuration of the fourth embodiment, the same components as those of the first to third embodiments are denoted by the same reference numerals as those of the first to third embodiments. In the fourth embodiment, an oil passage 93 is connected to the lubrication circuit 92, and a check valve 94 is provided between the passage 68 and the oil passage 93. The check valve 94 is configured to allow the oil in the back pressure chamber 67 to be supplied to the oil passage 93 and prevent the oil in the oil passage 93 from flowing back into the passage 68. The oil passage 93 is connected to the drain ports 50 and 51 of the switching valve 46, and a check valve 95 is provided between the oil passage 93 and the passage 81. The check valve 95 is configured to allow the oil in the back pressure chamber 80 to be supplied to the oil passage 93 and prevent the oil in the oil passage 93 from flowing back into the passage 81.

  In the fourth embodiment, the same components as those in the first to third embodiments can obtain the same effects as those in the first to third embodiments. In the fourth embodiment, when the output port 49 and the drain port 51 are connected by the switching operation of the switching valve 46, the oil in the second oil chamber 73 is lubricated via the oil passage 93. This is supplied to the circuit 92. Further, when the output port 48 and the drain port 50 are connected by the switching operation of the switching valve 46, the oil in the second oil chamber 60 is supplied to the lubrication circuit 92 via the oil passage 93. Further, when the hydraulic pressure in the back pressure chamber 67 increases due to the operation of the piston 61, the oil in the back pressure chamber 67 is supplied to the lubrication circuit 92 via the oil passage 93. Furthermore, when the hydraulic pressure in the back pressure chamber 80 increases due to the operation of the piston 74, the oil in the back pressure chamber 80 is supplied to the lubrication circuit 92 via the oil passage 93.

  As described above, in the fourth embodiment, oil is continuously supplied from the second oil chambers 54 and 73 and the back pressure chambers 67 and 80 in all the accumulators 58 and 71 to the common lubricating circuit 92 without interruption. be able to. Here, the correspondence relationship between the configuration of the fourth embodiment and the configuration of the present invention will be described. The lubricating oil path 92 corresponds to a common lubricating circuit of the present invention, and the oil path 93 is the first of the present invention. This corresponds to the lubricating oil passage and the second lubricating oil passage. The relationship between the other configurations of the fourth embodiment and the configuration of the present invention is the same as the correspondence relationship between the configurations of the first to third embodiments and the configuration of the present invention.

  Next, another embodiment of the hydraulic control device 18 will be described with reference to FIG. The fifth embodiment is an embodiment corresponding to the inventions of claims 1 to 10 and claim 12. In the configuration of the fifth embodiment, the same components as those of the first and third embodiments are denoted by the same reference numerals as those of the first and third embodiments. In the fifth embodiment, a lubrication circuit 100 is provided, and drain ports 50 and 51 of the switching valve 46 are connected to the lubrication circuit 100 by an oil passage 101. Further, a lubrication circuit 102 different from the lubrication circuit 100 is provided, and an oil passage 103 is connected to the lubrication circuit 102. The oil passage 103 is branched in two directions, and one of the branches is connected to the passage 68 via a check valve 94. The check valve 94 allows the oil in the back pressure chamber 67 to be supplied to the oil passage 103 and prevents the oil in the oil passage 103 from flowing back into the passage 68. The other branched portion is connected to the passage 81 via a check valve 95. The check valve 95 is configured to allow the oil in the back pressure chamber 80 to be supplied to the oil passage 103 and prevent the oil in the oil passage 103 from flowing back into the passage 81.

  In the fifth embodiment, the same components as in the first and third embodiments can obtain the same effects as those in the first and third embodiments. In the fifth embodiment, when the output port 49 and the drain port 51 are connected by the switching operation of the switching valve 46, the oil in the second oil chamber 73 is lubricated via the oil passage 101. Supplied to the circuit 100. Further, when the output port 48 and the drain port 50 are connected by the switching operation of the switching valve 46, the oil in the second oil chamber 60 is supplied to the lubrication circuit 100 via the oil passage 101. Further, when the hydraulic pressure in the back pressure chamber 67 increases due to the operation of the piston 61, the oil in the back pressure chamber 67 is supplied to the lubrication circuit 102 via the oil passage 103. Furthermore, when the hydraulic pressure in the back pressure chamber 80 increases due to the operation of the piston 74, the oil in the back pressure chamber 80 is supplied to the lubrication circuit 102 via the oil passage 103.

  In this way, oil is supplied to the lubrication circuit 100 from the second oil chambers 60 and 73 of all the accumulators 58 and 71, and the lubrication circuit 102 is fed from the back pressure chambers 67 and 80 of all the accumulators 58 and 71. Is supplied with oil. Therefore, oil can be continuously supplied to the lubrication circuits 100 and 102 without interruption. The amount of oil supplied to the lubrication circuits 100 and 102 is a proportion corresponding to the cross-sectional area of the back pressure chambers 67 and 80 and the cross-sectional area of the second oil chambers 60 and 79. Therefore, the oil supply flow rate can be adjusted.

  Here, the correspondence between the configuration of the fifth embodiment and the configuration of the present invention will be described. The lubrication circuit 100 corresponds to the lubrication circuit and the first lubrication circuit of the present invention, and the lubrication circuit 102 corresponds to the present invention. The oil passage 101 corresponds to the first lubricating oil passage of the present invention, and the oil passage 103 corresponds to the second lubricating oil passage of the present invention. The correspondence relationship between the other configurations of the fifth embodiment and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first and third embodiments and the configuration of the present invention.

  Next, another embodiment of the hydraulic control device 18 will be described with reference to FIG. The sixth embodiment is an embodiment corresponding to the inventions of claims 1 to 10 and claim 13. In the configuration of the sixth embodiment, the same components as those of the first and third embodiments are denoted by the same reference numerals as those of the first and third embodiments. In the sixth embodiment, the lubrication circuit 100 is provided, and the drain port 51 of the switching valve 46 is connected to the lubrication circuit 100 by the oil passage 101. The oil passage 101 is connected to the passage 68 via a check valve 94. The check valve 94 is configured to allow the oil in the back pressure chamber 67 to be supplied to the oil passage 101 and prevent the oil in the oil passage 101 from flowing back into the passage 68.

  Further, a lubrication circuit 102 different from the lubrication circuit 100 is provided, and an oil passage 103 is connected to the lubrication circuit 102. The oil passage 103 is connected to the drain port 50 of the switching valve 46. The oil passage 102 is connected to the passage 81 via a check valve 95. The check valve 95 is configured to allow the oil in the back pressure chamber 80 to be supplied to the oil passage 102 and prevent the oil in the oil passage 102 from flowing back into the passage 81.

  In the sixth embodiment, the same components as in the first and third embodiments can obtain the same effects as those in the first and third embodiments. In the sixth embodiment, when the output port 49 and the drain port 51 are connected by the switching operation of the switching valve 46, the oil in the second oil chamber 73 is lubricated via the oil passage 101. Supplied to the circuit 100. Further, when the output port 48 and the drain port 50 are connected by the switching operation of the switching valve 46, the oil in the second oil chamber 60 is supplied to the lubrication circuit 102 via the oil passage 103. Further, when the hydraulic pressure in the back pressure chamber 67 increases due to the operation of the piston 61, the oil in the back pressure chamber 67 is supplied to the lubrication circuit 100 via the oil passage 101. Furthermore, when the hydraulic pressure in the back pressure chamber 80 increases due to the operation of the piston 74, the oil in the back pressure chamber 80 is supplied to the lubrication circuit 102 via the oil passage 103.

  In this way, oil is supplied from the second oil chamber 60 of the accumulator 58 to the lubrication circuit 102, and oil is supplied from the back pressure chamber 80 of the accumulator 71 to the lubrication circuit 102. In addition, oil is supplied to the lubrication circuit 100 from the second oil chamber 73 of the accumulator 71, and oil is supplied to the lubrication circuit 100 from the back pressure chamber 67 of the accumulator 58. Therefore, oil can be continuously supplied to the lubrication circuits 100 and 102 without interruption, and the amount of oil in the lubrication circuits 100 and 102 is averaged.

  Here, the correspondence between the configuration of the sixth embodiment and the configuration of the present invention will be described. The accumulator 58 corresponds to the first oil retaining device of the present invention, and the accumulator 71 is the second configuration of the present invention. The lubricating circuit 100 corresponds to the first lubricating circuit of the present invention, the lubricating device 102 corresponds to the second lubricating circuit of the present invention, and the oil passage 103 corresponds to the first lubricating circuit of the present invention. The oil passage 101 corresponds to the first lubricating oil passage, and the oil passage 101 corresponds to the second lubricating oil passage of the present invention. The correspondence relationship between the other configurations of the fifth embodiment and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first and third embodiments and the configuration of the present invention.

  In the first to sixth embodiments, the switching valve 46 is configured so that the oil is alternately supplied from the first oil chamber 59 and the first oil chamber 72 to the oil passage 38. It is also possible to configure the switching valve so that the oil is simultaneously supplied from the first oil chamber 59 and the first oil chamber 72 to the oil passage 38 and at the same time the supply of oil is terminated. Further, the supply timing of the oil supplied from the first oil chamber 59 to the oil passage 38 and the supply timing of the oil supplied from the first oil chamber 72 to the oil passage 38 are partially switched. It is also possible to construct a valve.

It is a conceptual diagram which shows Example 1 of the hydraulic control apparatus in this invention. It is a conceptual diagram which shows the power train and control system of the vehicle used as the object of this invention. It is a conceptual diagram which shows Example 2 of the hydraulic control apparatus in this invention. It is a conceptual diagram which shows Example 3 of the hydraulic control apparatus in this invention. It is a conceptual diagram which shows Example 4 of the hydraulic control apparatus in this invention. It is a conceptual diagram which shows Example 5 of the hydraulic control apparatus in this invention. It is a conceptual diagram which shows Example 6 of the hydraulic control apparatus in this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Engine, 2 ... Wheel, 5 ... Forward / reverse switching device, 6 ... Belt-type continuously variable transmission, 18 ... Hydraulic control device, 26, 37 ... Hydraulic chamber, 30 ... Oil pump, 33 ... Oil pan, 36, 38 , 54, 55, 56, 57, 68, 81, 93, 96, 98, 101, 103 ... oil passage, 46 ... switching valve, 58, 71 ... accumulator, 59, 72 ... first oil chamber, 60, 73 2nd oil chamber 61, 74 ... Piston 64, 65, 77, 78 ... End face 69, 70, 82, 83, 94, 95, 97, 99 ... Check valve, 92, 100, 102 ... Lubrication circuit.

Claims (13)

A power transmission device disposed in a path from the driving force source to the wheel; an oil receiving device that is supplied with oil and controls a power transmission state in the power transmission device based on a supply state of the oil; and the oil In a hydraulic control device including an oil holding device that supplies oil to a receiving device,
A plurality of the oil holding devices are provided, and the plurality of oil holding devices have a first oil chamber connected to the oil receiving device and an operable piston between the first oil chamber. Each of the plurality of oil retaining devices has a first pressure-receiving surface that forms the first oil chamber and the second oil chamber. And the second pressure receiving surface is provided, and the area of the second pressure receiving surface is set narrower than the area of the first pressure receiving surface,
An oil supply amount control device is provided for supplying the oil in the first oil chamber to the oil receiving device by raising the oil pressure in the second oil chamber and operating each piston in a predetermined direction. A hydraulic control device characterized by that.   The oil supply amount control device further has a configuration for controlling the supply timing of oil supplied from the first oil chambers of the plurality of oil holding devices to the oil receiving device, respectively. The hydraulic control device according to claim 1.   The oil supply amount control device further includes a configuration in which a supply timing of oil supplied from the first oil chambers of the plurality of oil holding devices to the oil receiving device is different for each oil holding device. The hydraulic control apparatus according to claim 2. A first oil passage provided in a path from the first oil chamber to the oil receiving device;
A second oil passage for supplying oil discharged from an oil pump to the second oil chamber via the oil supply amount control device;
A third oil passage for supplying oil in an oil pan to the first oil chamber when the piston operates in a direction opposite to a predetermined direction;
A first check valve that is provided in the first oil passage and prevents the oil of the oil receiving device from flowing back into the first oil chamber;
2. A second check valve provided in the third oil passage and configured to prevent the oil in the first oil chamber from flowing back to the oil pan. 2. The hydraulic control device according to 2 or 3.   A first lubricating oil passage for supplying oil discharged from the second oil chamber to a lubricating circuit for lubricating the power transmission device when the piston operates in a direction opposite to the predetermined direction; The hydraulic control device according to claim 1, wherein the hydraulic control device is provided.   6. The hydraulic control device according to claim 5, wherein the oil supply amount control device also has a configuration as the first lubricating oil passage.   The piston is formed with a first partition wall having the first pressure receiving surface and a second partition wall having the second pressure receiving surface. The first partition wall and the second partition wall A back pressure chamber in which the hydraulic pressure is changed by the operation of the piston is formed therebetween, and a second lubricating oil passage for supplying oil from the back pressure chamber to the lubricating circuit is provided. The hydraulic control device according to any one of claims 1 to 6. A third check valve provided in the second lubricating oil passage and preventing the oil in the lubricating circuit from flowing back into the back pressure chamber;
A fourth oil passage for supplying oil from the oil pan to the back pressure chamber;
The hydraulic control device according to claim 7, further comprising a fourth check valve that prevents the oil in the back pressure chamber from flowing back into the oil pan. A power transmission device disposed in a path from the driving force source to the wheel; an oil receiving device that is supplied with oil and controls a power transmission state in the power transmission device based on a supply state of the oil; and the oil In a hydraulic control device including an oil holding device that supplies oil to a receiving device,
The oil holding device includes a first oil chamber connected to the oil receiving device, and a second oil chamber in which an operable piston is interposed between the first oil chamber and the first oil chamber. The piston is provided with a first pressure receiving surface that forms the first oil chamber and a second pressure receiving surface that forms the second oil chamber. The area of the second pressure receiving surface is set narrower than the area,
An oil supply amount control device is provided for increasing the oil pressure in the second oil chamber and operating the piston in a predetermined direction to supply the oil in the first oil chamber to the oil receiving device. ,
A lubricating oil passage is provided for supplying oil discharged from the second oil chamber to a lubricating circuit for lubricating the power transmission device when the piston operates in a direction opposite to the predetermined direction. Hydraulic control device characterized by. A power transmission device disposed in a path from the driving force source to the wheel; an oil receiving device that is supplied with oil and controls a power transmission state in the power transmission device based on a supply state of the oil; and the oil In a hydraulic control device including an oil holding device that supplies oil to a receiving device,
The oil holding device includes a first oil chamber connected to the oil receiving device, and a second oil chamber in which an operable piston is interposed between the first oil chamber and the first oil chamber. The piston is provided with a first pressure receiving surface that forms the first oil chamber and a second pressure receiving surface that forms the second oil chamber. The area of the second pressure receiving surface is set narrower than the area,
An oil supply amount control device is provided for increasing the oil pressure in the second oil chamber and operating the piston in a predetermined direction to supply the oil in the first oil chamber to the oil receiving device. ,
The piston is formed with a first partition wall having the first pressure receiving surface and a second partition oil chamber having the second pressure receiving surface, and the first partition wall and the second partition wall. A back pressure chamber in which the hydraulic pressure changes due to the operation of the piston is formed, and a lubricating oil passage is provided for supplying oil in the back pressure chamber to a lubricating circuit for lubricating the power transmission device. A hydraulic control device characterized by comprising:   The first lubricating oil passage and the second lubricating oil passage are provided so that oil is supplied to the common lubricating circuit from the second oil chamber and the back pressure chamber of all the oil holding devices. The hydraulic control device according to claim 7, wherein the hydraulic control device is provided. The lubrication circuit includes a first lubrication circuit and a second lubrication circuit,
The first lubricating oil passage is provided so that oil is supplied to the first lubricating circuit from the second oil chamber of all the oil holding devices,
8. The second lubricating oil passage is provided so that oil is supplied to the second lubricating circuit from the back pressure chambers of all the oil holding devices. Hydraulic control device. The lubrication circuit includes a first lubrication circuit and a second lubrication circuit,
The plurality of oil holding devices include a first oil holding device and a second oil holding device,
The second lubricating oil is supplied to the first lubricating circuit from the back pressure chamber of the first oil holding device and the second oil chamber of the second oil holding device. A path and the first lubricating oil path are provided,
The first lubricating oil is supplied to the second lubricating circuit from the second oil chamber of the first oil holding device and the back pressure chamber of the second oil holding device. The hydraulic control device according to claim 7, wherein a passage and the second lubricating oil passage are provided.

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