JP2005172112A - Lubricating device for transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain work volume of oil pumps from increasing in a lubricating device for a transmission. <P>SOLUTION: The lubricating device for a transmission having first feeding routes 11, 16 for feeding oil to a lubrication system 17 via a pressure control valve 12 and a second feeding route 21 for feeding oil to the lubrication system 17 in the case where the pressure control valve 12 fails has a first oil pump 8 and a second oil pump 9 and the first oil pump 8, the second oil pump 9. The first check valve 18, a second check valve 29 and the pressure control valve 12 are provided so that oil of the first oil pump 8 is fed to the pressure control valve 12 via the first check valve 18 and oil of a second oil pump 9 is fed to the pressure control valve 12 via the second check valve 29. The oil flowing to the upstream of the first check valve 18 is fed to the lubrication system 17 via a restricter part 22 and a third check valve 23. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a lubrication device for a transmission that supplies oil to a portion requiring lubrication.

  Conventionally, transmissions mounted on vehicles have been provided with rotating members that rotate relative to each other, such as gears meshed with each other, pulleys and belts, inner rings of bearings, outer rings and rolling elements, and the like. In order to suppress heat generation, seizure, wear, and the like due to relative rotation of the oil, a lubrication device that supplies oil is provided. A transmission control device having such a lubrication device is described in Patent Document 1. In this patent document 1, the oil discharged from the oil pump is supplied to the input port of the primary regulator valve via the oil passage. Then, the spool of the primary regulator valve operates according to the oil pressure of the oil passage, the oil in the oil passage is discharged from the escape port, and the oil pressure of the oil passage is controlled. The pressure oil in the oil passage is supplied to the hydraulic chamber of the primary pulley and the hydraulic chamber of the secondary pulley of the belt type continuously variable transmission.

The oil in the relief port is supplied to the lubrication system via the secondary regulator valve. On the other hand, another oil passage is provided for supplying the oil in the oil passage to the lubrication system via the pressure reducing valve and the secondary regulator valve. An orifice is provided in the oil passage from the pressure reducing valve to the secondary regulator valve. For this reason, even when oil is not discharged from the relief port of the primary regulator valve, it is possible to supply part of the oil discharged from the oil pump to the lubrication system via the pressure reducing valve and the secondary regulator valve, It is said that the shortage of oil in the lubrication system can be suppressed. A lubricating device for an automatic transmission for a vehicle is also described in Patent Document 2.
JP 2001-330112 A JP-A-2-176249

  However, in the lubricating device described in Patent Document 1, even when oil cannot be supplied to the lubrication system via the primary regulator valve, the oil is supplied to the lubrication system via the pressure reducing valve, the orifice, and the secondary regulator valve. As a result, the work of the oil pump may increase.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a lubricating device for a transmission that can suppress an increase in the work of an oil pump.

  In order to achieve the above object, the invention of claim 1 is characterized in that the first supply path for supplying oil to the lubrication system via the pressure control valve and the lubrication system when the pressure control valve fails. A transmission lubrication device capable of supplying oil to a motor has a first oil pump driven by an engine and a second oil pump driven by an electric motor, from the first oil pump. The discharged oil is supplied to the pressure control valve via the first check valve, and the oil discharged from the second oil pump is supplied to the pressure control valve via the second check valve. A first oil pump, a second oil pump, a first check valve, a second check valve and a pressure control valve are arranged in the first supply path so as to be supplied to the pressure control valve. And the pressure When the control valve fails, the oil flowing upstream from the first check valve in the flow direction of the oil discharged from the first oil pump passes through the throttle part and the third check valve. In this case, a second supply path for supplying the lubricant to the lubrication system is provided.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the oil supplied from the second oil pump to the lubrication system is all passed through the pressure control valve so that the first supply path It is characterized by comprising.

  In addition to the configuration of claim 1, the invention of claim 3 is provided with a third supply path in parallel with the pressure control valve in a path from the second oil pump to the lubrication system, Rather than the amount of oil supplied from the first oil pump to the lubrication system via the first supply path, the oil is supplied from the second oil pump to the lubrication system via the third supply path. A flow rate control device for reducing the amount of oil is provided.

  According to a fourth aspect of the present invention, the first oil passage to which the oil discharged from the oil pump is supplied and the flow rate of the oil discharged from the first oil passage to the lubrication system are controlled. When the pressure control valve is connected to the first oil passage and the pressure control valve fails, the oil in the first oil passage is supplied to the pressure control valve. And a second oil passage that is bypassed and supplied to the lubrication system, and is closed when the oil pressure of the first oil passage is equal to or lower than the valve opening oil pressure. And a pressure relief valve that is opened when the oil pressure in the first oil passage exceeds the valve opening oil pressure is provided.

  According to a fifth aspect of the present invention, in addition to the configuration of the fourth aspect, the hydraulic pressure of the first oil passage where the pressure control valve is opened is higher than the hydraulic pressure of the first oil passage where the pressure control valve is opened. The hydraulic pressure is set to a high pressure.

  According to a sixth aspect of the present invention, in addition to the configuration of the fourth aspect, a friction engagement device is provided in a power transmission path from the driving force source to the wheel, and the friction oil is generated by the pressure oil in the first oil path. The torque capacity of the engagement device is controlled, and the valve opening hydraulic pressure of the pressure relief valve is higher than the target hydraulic pressure of the first oil passage when the friction engagement device is engaged. It is characterized by being set to high pressure.

  According to a seventh aspect of the invention, in addition to the configuration of the fourth aspect, the oil discharged from the pressure control valve is supplied to the lubrication system via the downstream oil passage and the downstream pressure control valve. The downstream pressure control valve is configured to control the oil pressure of the downstream oil passage by controlling the amount of oil discharged from the downstream oil passage to the lubrication system. A second pressure relief valve is provided between the pressure relief valve and the lubrication system, and the second oil passage includes the pressure relief valve and a second pressure relief valve. A connecting oil passage is provided between the pressure relief valve and the downstream oil passage, and the second pressure relief valve has a hydraulic pressure of the downstream oil passage equal to or lower than a second predetermined value. In And a power transmission device that transmits the power of the driving force source to the wheels, and is configured to be opened when the second predetermined value is exceeded. The power transmission state in the power transmission path is controlled by the pressure oil supplied to the power transmission device.

  According to an eighth aspect of the present invention, in addition to the configuration of the fourth aspect, the oil discharged from the pressure control valve is supplied to the lubrication system via the downstream oil passage and the downstream pressure control valve. The downstream pressure control valve is configured to control the oil pressure of the downstream oil passage by controlling the amount of oil discharged from the downstream oil passage to the lubrication system. 2 and a connecting oil passage that connects the pressure relief valve and the pressure control valve and the downstream oil passage, and transmits the power of the driving force source to the wheels. And a power transmission state in the power transmission path is controlled by pressure oil supplied from the downstream oil path to the power transmission apparatus. is there.

  The invention according to claim 9 is the first supply path for supplying oil to the lubrication system via the pressure control valve, and the amount of oil supplied to the lubrication system via the first supply path is reduced. Even in this case, the transmission lubrication apparatus capable of supplying oil to the lubrication system includes a first oil pump driven by an engine and a second oil pump driven by an electric motor, The oil discharged from the first oil pump is supplied to the pressure control valve via the first check valve, and the oil discharged from the second oil pump is supplied to the second check valve. A first oil pump, a second oil pump, a first check valve, a second check valve, and the first supply path so as to be supplied to the pressure control valve via a valve; When the pressure control valve is arranged In addition, when the amount of oil supplied to the lubrication system via the first supply path is reduced, the first check is made in the flow direction of the oil discharged from the first oil pump. A second supply path for supplying oil flowing upstream from the valve to the lubrication system via the throttle portion and the third check valve is provided.

  According to the tenth aspect of the present invention, the first oil passage to which the oil discharged from the oil pump is supplied and the flow rate of the oil supplied from the first oil passage to the lubrication system are controlled. A pressure control valve for controlling the oil pressure of the oil passage; and when the oil pressure of the first oil passage rises above a predetermined pressure when connected to the first oil passage, the oil in the first oil passage And a second oil passage that bypasses the pressure control valve and supplies the second oil passage to the lubrication system, the oil pressure of the first oil passage is a predetermined value in the second oil passage. A pressure relief valve is provided which is closed in the following cases and opened when a predetermined value is exceeded.

  According to the first aspect of the present invention, the oil discharged from at least one of the first oil pump and the second oil pump can be supplied to the lubrication system. If the pressure control valve fails and oil discharged from the first oil pump cannot be supplied to the lubrication system via the pressure control valve, the oil is discharged from the first oil pump. Since the oil is supplied to the lubrication system via the second supply path, a decrease in the amount of oil supplied to the lubrication system can be suppressed. For this reason, it is possible to eliminate the route for supplying oil from the second oil pump to the lubrication system by bypassing the pressure control valve, or to reduce the supply amount thereof as much as possible. Therefore, when the engine is stopped and the first oil pump is stopped, the amount of oil supplied from the second oil pump to the lubrication system can be reduced, and the work amount of each oil pump can be reduced. It is possible.

  According to the invention of claim 2, in addition to obtaining the same effect as that of the invention of claim 1, the oil discharged from the second oil pump is supplied to the lubrication system without going through the pressure control valve. Therefore, the work of the oil pump can be further reduced.

  According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 1, than the amount of oil supplied from the first oil pump to the lubrication system via the first supply path, The amount of oil supplied from the second oil pump to the lubrication system via the third supply path is smaller. Therefore, it is possible to reliably reduce the work amount of the oil pump when the engine is stopped.

  According to the invention of claim 4, the oil supplied from the oil pump to the first oil passage is supplied to the lubrication system via the pressure control valve, the pressure control valve fails, and the pressure relief is applied. When the valve is opened, the oil in the first oil passage is supplied to the lubrication system via the second oil passage. Further, when the oil pressure in the first oil passage is equal to or lower than the valve opening oil pressure, the pressure relief valve is closed, so that the amount of oil supplied to the lubrication system via the second oil passage is increased (oil Can be suppressed). Therefore, an increase in the work amount of the oil pump can be suppressed. When the pressure relief valve is closed, the oil in the first oil passage is not supplied to the lubrication system via the second oil passage, and the hydraulic pressure rises in the first oil passage. Responsiveness is improved. That is, it is possible to achieve both reduction in the work amount of the oil pump and improvement in the rising response performance of the hydraulic pressure in the first oil passage.

  According to the invention of claim 5, in addition to obtaining the same effect as that of the invention of claim 4, it is possible to prevent the pressure relief valve from being opened before the pressure control valve is opened. The increase in work volume can be more reliably suppressed.

  According to the sixth aspect of the invention, in addition to obtaining the same effect as the fourth aspect of the invention, the pressure oil of the first oil passage is supplied to the friction engagement device to engage the friction engagement device. In this case, it is possible to prevent the pressure relief valve from being opened when the oil pressure in the first oil passage is equal to or lower than the target oil pressure. Therefore, the engagement responsiveness of the friction engagement device can be improved.

  According to the invention of claim 7, in addition to the same effect as that of the invention of claim 4, when the pressure control valve fails, the oil discharged from the oil pump passes through the pressure relief valve to the downstream oil passage. And the fluid transmission device. When the oil pressure in the downstream oil passage is low, the downstream pressure control valve is closed, so that the oil in the downstream oil passage is not supplied to the lubrication system. When the oil pressure in the downstream oil passage becomes high, the downstream pressure control valve is opened, and the oil in the downstream oil passage is supplied to the lubrication system. By the way, the downstream pressure control valve fails and the oil in the downstream oil passage cannot be supplied to the lubrication system via the downstream pressure control valve, and the oil pressure in the downstream oil passage exceeds a predetermined value. Only when the second pressure relief valve is opened, the oil discharged from the oil pump bypasses the pressure control valve and the downstream pressure control valve and is supplied to the lubrication system. Accordingly, it is possible to suppress a decrease in the rising response of the pressure oil supplied to the power transmission device.

  According to the invention of claim 8, in addition to the same effect as that of the invention of claim 4, the oil discharged from the oil pump is supplied to the fluid transmission device via the pressure control valve or the connecting oil passage. Further, in the second oil passage, when the hydraulic pressure upstream of the pressure relief valve is equal to or lower than the predetermined hydraulic pressure, the pressure relief valve is closed, so that the oil enters the lubrication system via the pressure relief valve. It is never supplied. On the other hand, in the second oil passage, when the hydraulic pressure upstream of the pressure relief valve exceeds the predetermined hydraulic pressure, the pressure relief valve is opened, so that the oil passes through the pressure relief valve. Supplied to the lubrication system. Furthermore, since the pressure relief valve does not open below a predetermined oil pressure, it is possible to suppress a decrease in the rise responsiveness of the pressure oil supplied to the power transmission device.

  According to the ninth aspect of the present invention, oil discharged from at least one of the first oil pump and the second oil pump can be supplied to the lubrication system. Further, when the flow rate of oil supplied from the first oil pump to the lubrication system via the pressure control valve decreases, the oil discharged from the first oil pump passes through the second supply path. And since it is supplied to a lubrication system, the fall of the amount of oil supplied to a lubrication system can be suppressed. For this reason, it is possible to eliminate the route for supplying oil from the second oil pump to the lubrication system by bypassing the pressure control valve, or to reduce the supply amount thereof as much as possible. Therefore, when the engine is stopped and the first oil pump is stopped, the amount of oil supplied from the second oil pump to the lubrication system can be reduced, thereby reducing the overall work amount of each oil pump. Is possible.

  According to the invention of claim 10, the oil supplied from the oil pump to the first oil passage is supplied to the lubrication system via the pressure control valve, and even if the pressure control valve is normal, the first When the oil pressure of one oil passage rises above a predetermined value, the pressure relief valve is opened, and the oil in the first oil passage is supplied to the lubrication system via the second oil passage. In addition, the pressure relief valve provided in the second oil passage is closed when the oil pressure in the first oil passage is equal to or less than a predetermined value, so that the lubrication system passes through the second oil passage. An increase in the amount of oil supplied (always supplying oil) can be suppressed. Therefore, an increase in the work amount of the oil pump can be suppressed. When the pressure relief valve is closed, the oil in the first oil passage is not supplied to the lubrication system via the second oil passage, and the hydraulic pressure rises in the first oil passage. Responsiveness is improved.

  Next, the present invention will be described in detail with reference to the accompanying drawings. FIG. 2 is a conceptual diagram showing a power train of the vehicle. The vehicle 1 shown in FIG. 2 has a configuration in which the power of the engine 2 is transmitted to the wheels 5 via the fluid transmission device 70, the forward / reverse switching device 3, and the belt type continuously variable transmission 4. The fluid transmission device 70 includes a pump impeller 71 and a turbine runner 72, and power is transmitted between the pump impeller 71 and the turbine runner 72 by the kinetic energy of oil as a working fluid. The fluid transmission device 70 may be either a torque converter having a torque amplification function or a fluid coupling having no torque amplification function.

  The forward / reverse switching device 3 has a planetary gear mechanism and a hydraulically controlled friction engagement device 3A. As this friction engagement device 3A, a clutch, a brake, or the like is used, and by controlling the engagement / release of the clutch, the brake, etc., it is possible to switch the rotation direction of the rotating member on the output side between forward and reverse. It has become. The belt type continuously variable transmission 4 includes a primary pulley 4A and a secondary pulley 4B, and a belt 4C wound around the primary pulley 4A and the secondary pulley 4B. Then, by controlling the clamping pressure applied from the primary pulley 4A to the belt 4C and the clamping pressure applied from the secondary pulley 4B to the belt 4C, the gear ratio between the primary pulley 4A and the secondary pulley 4B is stepless. While controlling, the capacity | capacitance of the torque transmitted between primary pulley 4A and secondary pulley 4B is controlled. Further, a hydraulic control device 6 for controlling the forward / reverse switching device 3, the belt type continuously variable transmission 4 and the fluid transmission device 70 is provided. Configuration examples of a hydraulic circuit (lubricating device) that constitutes a part of the hydraulic control device 6 will be sequentially described.

  A first embodiment of the hydraulic circuit will be described with reference to FIG. The first embodiment corresponds to the first, second, and ninth aspects of the invention. In the hydraulic circuit 7 shown in FIG. 1, a first oil pump 8 and a second oil pump 9 are provided. The first oil pump 8 is driven by the power of the engine 2, and the second oil pump 9 is driven by the power of the electric motor 10.

  First, the oil discharged from the first oil pump 8 is supplied to the primary regulator valve 12 via the oil passage 11. The primary regulator valve 12 has an input port 13, an output port 14, a feedback port 15, a spool 24 and an elastic member 25. The spool 24 can reciprocate in a predetermined direction, and the spool 24 is urged in a predetermined direction by the urging force of the elastic member 25.

  An input port 13 is connected to the oil passage 11. The oil pressure of the oil passage 11 is input to the feedback port 15, and the spool 24 is biased in the opposite direction to the elastic member 25 according to the oil pressure input to the feedback port 15. The spool 24 operates according to the oil pressure of the oil passage 11, and the flow rate of oil discharged from the oil passage 11 to the oil passage 16 and the oil pressure of the oil passage 11 are adjusted. The output port 14 is connected to the lubrication system 17 via the oil passage 16. The lubrication system 17 includes parts that require lubrication and cooling, such as a planetary gear mechanism of the forward / reverse switching device 3 and bearings (not shown) that support various rotating members.

  The oil passage 11 is provided with a check valve 18, which has an input port 19 and an output port 20, and the input port 19 is connected to the discharge port of the first oil pump 8. The output port 20 is connected to the input port 13 of the primary regulator valve 12. The check valve 18 has a function of allowing the oil of the input port 19 to be supplied to the output port 20 and preventing the oil of the output port 20 from flowing back to the input port 19.

  Furthermore, an oil passage (forced lubrication circuit) 21 is provided which is the oil passage 11 and connects the oil passage 16 between the first oil pump 8 and the check valve 18. That is, the oil passage 21 is disposed in parallel with the oil passage 11 and the primary regulator valve 12. The oil passage 21 is provided with a throttle portion 22 and a check valve 23. The check valve 23 is an oil passage 21 and is disposed between the throttle portion 22 and the oil passage 16, and the check valve 23 allows the oil of the first oil pump 8 to pass through the oil passage 21. The oil in the oil passage 16 is allowed to flow back to the oil passage 11 via the oil passage 21, specifically, the first oil pump 8 and It has a function of preventing backflow between the check valve 18 and the check valve 18.

  On the other hand, in the oil passage 11, an oil passage 26 is connected between the check valve 18 and the primary regulator valve 12, and the oil passage 26 is connected to various hydraulic chambers 27. The hydraulic chamber 27 includes a hydraulic chamber for controlling the clamping pressure between the primary pulley and the secondary pulley, a hydraulic chamber for controlling the engagement pressure of the friction engagement device 3A of the forward / reverse switching device 3 and the like. In FIG. 1, for convenience, it is shown as one hydraulic chamber 27. Further, the discharge port of the second oil pump 9 and the oil passage 26 are connected by an oil passage 28. A check valve 29 is provided in the oil passage 28. The check valve 29 allows the oil discharged from the second oil pump 9 to be supplied to the oil passage 26 via the oil passage 28, and the oil in the oil passage 26 passes through the oil passage 28. It has a function of preventing backflow to the second oil pump 9 via the relay.

  In the hydraulic circuit 7 configured as described above, oil is supplied from the first oil pump 8 to the oil passage 11, and the oil passage 11 includes the first oil pump 8 and the check valve 18. If the hydraulic pressure between them is higher than the hydraulic pressure between the check valve 18 and the primary regulator valve 12, the check valve 18 is opened and the oil discharged from the first oil pump 8 is The oil is supplied to the oil passage 26 via the oil passage 11. Further, when oil is supplied from the second oil pump 9 to the oil passage 28, the oil pressure in the oil passage 28 is between the second oil pump 9 and the check valve 29. If the hydraulic pressure between the valve 29 and the oil passage 26 is higher than the hydraulic pressure, the check valve 29 is opened. Therefore, the oil discharged from the second oil pump 9 is supplied to the oil passage 26.

  In this way, the oil discharged from at least one of the first oil pump 8 or the second oil pump 9 is supplied to the oil passages 11 and 26. Here, when the oil pressure in the oil passages 11 and 26 is equal to or less than a predetermined value, the input port 13 and the output port 14 of the primary regulator valve 12 are blocked. For this reason, the oil in the oil passage 11 is not discharged to the oil passage 16, and a decrease in the hydraulic pressure of the pressure oil supplied from the oil passages 11 and 26 to the hydraulic chamber 27 is suppressed.

  When the oil pressure in the oil passages 11 and 26 rises to a predetermined value or more, the input port 13 and the output port 14 communicate with each other, the oil in the oil passage 11 is discharged to the oil passage 16, and the oil passage 16 The oil is supplied to the lubrication system 17. Accordingly, an increase in the oil pressure of the oil passages 11 and 26 is suppressed, and seizure and wear of parts in the lubrication system 17 are suppressed. Further, when the input port 13 and the output port 14 are in communication with each other, and the oil pressure in the oil passages 11 and 26 is reduced, the flow rate of oil discharged from the oil passage 11 to the oil passage 16 is reduced. Thus, the oil pressure of the oil passages 11 and 26, that is, the line pressure is controlled by the function of the primary regulator valve 12.

  A part of the oil discharged from the first oil pump 8 to the oil passage 11 is supplied to the oil passage 21, but when the check valve 18 is opened, the oil passes through the throttle portion 22. The resistance of the oil is larger than the resistance of the oil passing through the check valve 18, and most of the oil discharged from the first oil pump 8 is supplied to the oil passage 26. The amount of oil that passes through 22 and flows into the oil passage 16 is small.

  Next, a case where the check valve 18 is closed will be described. For example, in the state where the input port 13 and the output port 14 of the primary regulator valve 12 are shut off, when a failure occurs in which the spool 24 is fixed, the oil passage 11 includes the check valve 18 and the primary regulator valve. The hydraulic pressure between the first and second oil pumps 11 and 11 is higher than the hydraulic pressure between the check valve 18 and the first oil pump 8, and the check valve 18 is closed. Even if the function of the primary regulator valve 12 is normal, the amount of oil supplied to the oil passage 26 becomes excessive than the amount of oil required in the hydraulic chamber 27, and the oil pressure in the oil passage 26 reaches the predetermined oil pressure. As a result, the check valve 18 may be closed. For this reason, when the check valve 18 is closed, the oil discharged from the first oil pump 8 is supplied to the oil passage 21 and the oil in the oil passage 21 passes through the oil passage 16. And supplied to the lubrication system 17. Therefore, even when the check valve 18 is closed, the oil discharged from the first oil pump 8 can be forcibly supplied to the lubrication system 17, and a shortage of lubrication oil in the lubrication system 17 is suppressed. it can.

  By the way, when the vehicle 1 is a vehicle having no driving force source other than the engine 2, when the engine 2 is stopped (idling stop), the first oil pump 8 is stopped and the lubrication system 17 is stopped. The oil supply to is stopped. Further, since the vehicle 1 does not travel when the engine 2 is stopped, it is not necessary to supply oil to the hydraulic chamber 27 and the lubrication system 17, so the electric motor 10 is also stopped and the second oil pump 9 is stopped. Oil will not be discharged from.

  On the other hand, the case where the vehicle 1 is a hybrid vehicle which has the electric motor for driving | running | working which functions as a driving force source other than the engine 2 is demonstrated. In such a hybrid vehicle, it is possible to execute control in which the vehicle 1 travels with the power of the traveling motor and the engine 2 is stopped. Such control is executed when the traveling load is low and the vehicle speed request is low. In this way, when the vehicle 1 travels with the travel motor and the engine 2 is stopped, the motor 10 is driven and the oil discharged from the second oil pump 9 is supplied to the oil passages 26 and 11. At the same time, the oil in the oil passage 11 is supplied to the lubrication system 17 via the oil passage 16 according to the same principle as described above.

  In this case, the electric motor 10 may be a traveling electric motor, or an electric motor that does not have a function as a driving force source of the vehicle 1, that is, a dedicated motor provided to drive the second oil pump 9. Any of these motors may be used. When the second oil pump 9 is driven and the first oil pump 8 is stopped, the primary regulator valve 12 fails, the input port 13 and the output port 14 are shut off, and the oil passage Even when the oil pressures 11 and 26 rise and the check valve 18 and the check valve 29 are closed, the oil in the oil passages 11 and 26 is supplied to the lubrication system 17 via the oil passage 21. Absent.

  Thus, in the hydraulic circuit 7 shown in FIG. 1, the discharge from the second oil pump 9 driven by the electric motor 10 is performed only when the input port 13 and the output port 14 of the primary regulator valve 12 communicate with each other. The oil to be supplied is supplied to the lubrication system 17, and the oil from the second oil pump 9 is supplied to the lubrication system 17 without passing through the primary regulator valve 12 (bypassing oil). (Road) is not required. In other words, the consumption flow rate of oil discharged from the second oil pump 9 can be reduced. Therefore, it is possible to suppress an increase in the work amount of the second oil pump 9, to reduce the size (discharge capacity) of the second oil pump 9, to reduce the rating of the electric motor 10, and The number of times can be reduced.

  Furthermore, the efficiency of the second oil pump 9 and the electric motor 10 can be increased, and the cost can be reduced. Further, only when the input port 13 and the output port 14 of the primary regulator valve 12 communicate with each other, the oil discharged from the second oil pump 9 is supplied to the lubrication system 17, so that the first oil pump 8 When the oil pressure of the oil passages 11 and 26 is secured by the oil of the second oil pump 9, it is possible to improve the rise response of the oil pressure of the oil passages 11 and 26. Further, in the case where the power is generated by the power of the engine 2 and the generated electric power is supplied to the electric motor 10 via the power storage device and the inverter, the electric motor 10 is reduced by reducing the load on the electric motor 10. It is possible to reduce the load of the electric power supplied to 10 and the electric system, and to suppress a reduction in fuel consumption of the engine 2.

  Next, another embodiment of the hydraulic circuit 7 constituting a part of the hydraulic control device 6 will be described with reference to FIG. The second embodiment corresponds to the first, third, and ninth aspects of the invention. In the configuration of the hydraulic circuit 7 of the third embodiment, the same configurations as those of the hydraulic circuit 7 of the first embodiment are denoted by the same reference numerals as those in FIG. In the second embodiment, an oil passage 30 that connects the oil passage 28 and the oil passage 16 is provided. Specifically, in the oil passage 28, the second oil pump 9 and the check valve 29 are connected to the oil passage 16 by an oil passage (forced lubrication circuit) 30 indicated by a solid line. . That is, the oil passage 30 is arranged in parallel to the oil passages 11 and 26 and the primary regulator valve 12. The oil passage 30 is provided with a throttle portion 31 and a check valve 32. Specifically, in the oil passage 30, a check valve 32 is provided between the throttle portion 31 and the oil passage 16. Further, the flow area of the throttle unit 31 is set to be narrower than the flow area of the throttle unit 22. Further, the check valve 32 allows the oil discharged from the second oil pump 9 to be supplied to the oil passage 16 via the oil passage 28 and the oil passage 30, and The oil has a function of preventing the oil from flowing back to the oil passage 28 via the oil passage 30.

  In the second embodiment, the same effects as those of the first embodiment can be obtained for the same configuration as the first embodiment. In the second embodiment, when the oil pressure in the oil passage 26 increases and the check valve 29 is closed, the oil discharged from the second oil pump 9 passes through the oil passage 30 and the oil passage 16. And supplied to the lubrication system 17. That is, the oil discharged from the second oil pump 9 is supplied to the lubrication system 17 without going through the primary regulator valve 12, in other words, bypassing the primary regulator valve 12. Furthermore, in the second embodiment, the flow area of the throttle unit 31 is set to be narrower than the flow area of the throttle unit 22. For this reason, the oil discharged from the first oil pump 8 and passed through the oil passage 21 and supplied to the lubrication system 17 is discharged from the second oil pump 9 via the oil passage 30 and lubricated. The amount of oil supplied to the system 17 is smaller. Therefore, the work amount of the second oil pump 9 can be reduced, and the same effect as in the first embodiment can be obtained.

  In the second embodiment, when the vehicle 1 travels at a high speed, the required amount of lubricating oil in the lubrication system 17 increases. When the vehicle 1 travels at a low speed, the required amount of lubricating oil in the lubrication system 17 decreases. Therefore, when the vehicle 1 travels at a high speed, the first oil pump 8 is driven and the second oil pump 9 is stopped. On the other hand, when the vehicle 1 travels at a low speed, the second oil pump 8 is stopped. By executing the control to drive the oil pump 9 and stop the first oil pump 8, the required amount of lubricating oil in the lubricating system 17 and the actual amount of lubricating oil supplied to the lubricating system 17 are matched. It is possible to make it.

  In the second embodiment, it is possible to connect the oil passage 28 between the check valve 29 and the oil passage 26 and the oil passage 16 through the oil passage 30 as indicated by a two-dot chain line. is there. In this case, the oil supplied from the first oil pump 8 to the oil passage 26 can be supplied to the lubrication system 17 via the oil passage 30.

  Here, the correspondence between the configurations of the first and second embodiments and the configuration of the present invention will be described. The primary regulator valve 12 corresponds to the pressure control valve of the present invention, and the oil passages 11, 16, 26 are provided. , 28 correspond to the first supply path of the present invention, the oil path 21 corresponds to the second supply path of the present invention, and the check valve 18 corresponds to the first check valve of the present invention. The check valve 29 corresponds to the second check valve of the present invention, the throttle portion 22 corresponds to the throttle portion of the present invention, and the check valve 23 corresponds to the third check valve of the present invention. The oil path 30 corresponds to the third supply path of the present invention, and the throttle portions 22 and 31 correspond to the flow control device of the present invention.

  Next, another embodiment of the hydraulic circuit 7 constituting a part of the hydraulic control device 6 will be described with reference to FIG. The third embodiment is an embodiment corresponding to the inventions of claims 4, 5, and 10. In the configuration of FIG. 4, the same components as those in FIG. 1 are denoted by the same reference numerals as those in FIG. In the third embodiment, since there is one oil pump, the first oil pump 8 is referred to as “oil pump 8” for convenience. First, an oil passage 16 is connected to the output port 14 of the primary regulator valve 12, and a lubrication system 17 is connected to the oil passage 16 via an oil passage 33. The oil passage 33 is provided with a throttle portion 34.

  Further, the oil passage 16 is connected to a lubrication pressure control valve 35. The lubrication pressure control valve 35 has an input port 36, an output port 37, a feedback port 38, a spool 39 and an elastic member 40. The spool 39 can reciprocate in a predetermined direction, and the spool 39 is urged in a predetermined direction by the urging force of the elastic member 40. The oil passage 16 and the input port 36 are connected, and the oil passage 41 is connected to the output port 37. When the oil pressure in the oil passage 16 is less than or equal to a predetermined oil pressure, the lubrication pressure control valve 35 shuts off the input port 36 and the output port 37, and when the oil pressure in the oil passage 16 exceeds the predetermined oil pressure, the feedback port 38 The spool 39 operates against the urging force of the elastic member 40 with an urging force corresponding to the hydraulic pressure, and the input port 36 and the output port 37 are communicated with each other. Thus, the flow rate of oil discharged from the oil passage 16 to the oil passage 41 and the oil pressure of the oil passage 16 are adjusted according to the operation of the spool 39.

  On the other hand, oil passages 42 and 43 and a pressure relief valve 44 are provided so as to connect the oil passage 11 and the oil passage 16 and bypass the primary regulator valve 12. Specifically, the oil passage 42 and the oil passage 11 are connected, and the oil passage 43 and the oil passage 16 are connected. A pressure relief valve 44 is interposed between the oil passage 42 and the oil passage 43. That is, the primary regulator valve 12 and the pressure relief valve 44 are arranged in parallel. The pressure relief valve 44 includes a valve seat 46 that forms a port 45, a valve body 47 that opens and closes the port 45, and an elastic member 48 that urges the valve body 47 toward the valve seat 46. The pressure relief valve 44 is configured such that when the oil pressure in the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure, the port 45 is closed, and when the oil pressure in the oil passages 11 and 42 exceeds the valve opening oil pressure, the valve body 47 Operates against the urging force of the elastic member 48, and the port 45 is opened. The valve opening hydraulic pressure of the pressure relief valve 44 is set higher than the valve opening hydraulic pressure of the primary regulator valve 12.

  In addition to the pressure relief valve 44, a pressure relief valve 49 is provided. The pressure relief valve 49 is provided between the oil passage 43 and the oil passage 54. The pressure relief valve 49 includes a valve seat 51 that forms the port 50, a valve body 52 that opens and closes the port 50, and an elastic member 53 that biases the valve body 52 in a direction toward the valve seat 51. The pressure relief valve 49 is configured such that when the oil pressure in the oil passage 43 is equal to or lower than a predetermined oil pressure, the port 50 is closed, and when the oil pressure in the oil passage 43 exceeds a predetermined oil pressure, the valve body 52 is connected to the elastic member 53. It operates against the urging force and is configured to open the port 50. The hydraulic pressure at which the pressure relief valve 49 is opened, that is, the valve opening hydraulic pressure is set to be higher than the valve opening hydraulic pressure of the lubricating oil control valve 35.

  Next, the function of the hydraulic circuit 7 shown in FIG. 4 will be described. The oil discharged from the oil pump 8 is supplied to the hydraulic chamber 27 via the oil passage 11 and the oil passage 26 and also to the input port 13 of the primary regulator valve 12. When the primary regulator valve 12 is normal, the amount of oil discharged from the oil passage 11 to the oil passage 16 is controlled according to the same principle as described in the first embodiment, and the oil pressure of the oil passages 11 and 26 is changed. It is regulated. The oil supplied to the oil passage 16 is supplied to the lubrication system 17 via the oil passage 33.

  Further, the function of the lubrication pressure control valve 35 will be described. First, when the oil pressure in the oil passage 16 is equal to or lower than the valve opening oil pressure of the lubrication pressure control valve 35, the input port 36 and the output port 37 of the lubrication pressure control valve 35 are blocked. For this reason, the oil in the oil passage 16 is not discharged to the oil passage 41, and a decrease in the oil pressure in the oil passages 16 and 33 is suppressed. On the other hand, when the oil pressure in the oil passages 16 and 33 exceeds the valve opening oil pressure of the lubrication pressure control valve 35, the input port 36 and the output port 37 communicate with each other, and the oil in the oil passage 16 flows into the oil passage. As a result, the oil pressure of the oil passages 16 and 33 is suppressed. Further, when the oil pressure of the oil passages 16 and 33 is lowered when the lubrication pressure control valve 35 is opened, the flow rate of oil discharged from the oil passage 16 to the oil passage 41 is reduced. Thus, the oil pressure of the oil supplied to the lubrication system 17 is controlled by the lubrication pressure control valve 35.

  Next, a case where the primary regulator valve 12 fails, specifically, a case where a failure that the spool 24 sticks in a closed state occurs will be described. In this case, since the oil in the oil passage 11 is not discharged to the oil passage 16, the oil pressure in the oil passages 11 and 26 increases. If the amount of oil discharged from the oil pump 8 to the oil passage 11 is greater than the amount of oil consumed in the hydraulic chamber 27 and the amount of oil discharged from the primary regulator valve 12 to the oil passage 16, Even if the primary regulator valve 12 is normal, the hydraulic pressure in the hydraulic chambers 11 and 26 may increase.

  As described above, when the oil pressure of the oil passages 11 and 26 is increased, when the oil pressure of the oil passages 11 and 26 is equal to or lower than the valve opening oil pressure of the pressure relief valve 44, the pressure relief valve 44 is closed. The oil in the oil passage 11 is not discharged to the oil passage 43. On the other hand, when the oil pressure of the oil passages 11 and 26 exceeds the valve opening oil pressure of the pressure relief valve 44, the valve body 47 operates against the urging force of the elastic member 48, and the port 45 is opened. . As a result, the oil in the oil passage 11 is discharged to the oil passage 43 via the port 45, and further increase in the oil pressure of the oil passages 11 and 26 is suppressed. The oil discharged to the oil passage 43 is supplied to the lubrication system 17 via the oil passages 16 and 33. When the pressure relief valve 44 is opened and the oil pressure in the oil passage 42 falls below the valve opening oil pressure of the pressure relief valve 44, the valve body 47 is operated by the urging force of the elastic member 48. The pressure relief valve 44 is closed. Further, when the pressure relief valve 44 is closed, even if the oil pressure in the oil passage 43 becomes higher than the oil pressure in the oil passage 42, the pressure relief valve 44 does not open, and the oil passage 43 The oil does not flow back to the oil passage 42.

  Further, a case where the lubrication pressure control valve 35 fails, specifically, a case where a failure that the spool 39 sticks in the closed state occurs will be described. In this case, since the oil in the oil passage 16 is not discharged to the oil passage 41, the oil pressure in the oil passages 16 and 33 increases. Note that the amount of oil discharged from the primary regulator valve 12 to the oil passage 16 is greater than the amount of oil consumed by the lubrication system 17 and the amount of oil discharged from the lubrication pressure control valve 35 to the oil passage 41. Even if the lubrication pressure control valve 35 is normal, the oil pressure of the oil passages 16, 33, 43 may increase.

  In this way, when the oil pressure of the oil passage 43 increases, when the oil pressure of the oil passage 43 is equal to or lower than the valve opening oil pressure of the pressure relief valve 49, the pressure relief valve 49 is closed, so the oil passage 43 oil is not discharged into the oil passage 54. On the other hand, when the oil pressure of the oil passage 43 exceeds the valve opening oil pressure of the pressure relief valve 49, the valve body 52 operates against the urging force of the elastic member 53, and the port 50 is opened. As a result, the oil in the oil passage 43 is discharged to the oil passage 54 via the port 50, and further increase in the oil pressure of the oil passages 16 and 43 is suppressed. In the case where the pressure relief valve 49 is open, if the oil pressure in the oil passage 43 falls below the valve opening oil pressure of the pressure relief valve 49, the valve body 52 is operated by the urging force of the elastic member 53. The pressure relief valve 49 is closed.

  As described above, in the third embodiment, when the oil pressure in the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure of the pressure relief valve 44, the oil in the oil passage 11 is not discharged to the oil passage 43. Therefore, an increase in the flow rate of the oil supplied to the lubrication system 17 out of the oil discharged from the oil pump 8 can be suppressed as much as possible, and the same effect as the first embodiment can be obtained. The valve opening hydraulic pressure of the pressure relief valve 44 is set to be higher than the valve opening hydraulic pressure of the primary regulator valve 12. For this reason, if the primary regulator valve 12 is normal, the primary regulator valve 44 is not opened before the primary regulator valve 12 is opened, and the rise response of the oil pressure of the oil passages 11 and 26 is reduced. Can be suppressed.

  Here, an example of the relationship between the elapsed time from the start of the driving of the oil pump 8 and the oil pressure of the oil passages 11 and 26, that is, the line pressure will be described based on the diagram of FIG. The hydraulic pressure characteristic corresponding to the third embodiment is indicated by a solid line, and the hydraulic pressure characteristic of the comparative example is indicated by a broken line. In the third embodiment, when the oil discharged from the oil pump 8 fills the oil passages 11 and 26, that is, from time t1, the line pressure becomes a hydraulic pressure exceeding zero megapascals, and the line pressure with time elapses. Tends to rise. If the primary regulator valve 12 is normal, the line pressure is maintained at a substantially constant predetermined pressure after time t3 by the line pressure regulating function of the primary regulator valve 12.

  Next, a comparative example will be described. This comparative example is a hydraulic characteristic of a hydraulic circuit in which a throttle portion (not shown) is provided instead of the pressure relief valve 44 shown in FIG. This throttling portion is always in a valve open state and is not closed. That is, oil is supplied from the input side to the output side due to the pressure difference between the input side and the output side of the throttle portion. In the case of this comparative example, when the oil discharged from the oil pump reaches the throttle part, a part of the oil is discharged via the throttle part, so the time until the oil is filled in the oil path is Slower than Example 3. For this reason, for example, after time t2 later than time t1, the line pressure becomes a hydraulic pressure exceeding zero megapascals.

  In the comparative example, the line pressure increases with time. Here, the rising slope of the line pressure in the comparative example is gentler than the rising slope of the line pressure in the third embodiment. The reason is that in the third embodiment, the oil in the oil passage 11 is not discharged to the oil passage 16 unless the primary regulator valve 12 is opened, whereas in the comparative example, the oil passage is in the process of increasing the line pressure. This is because a part of the oil is discharged through the throttle portion. Then, after time t4, which is later than time t3, the line pressure in the comparative example is controlled to a predetermined pressure. As shown in FIG. 5, it can be seen that the increase characteristic of the line pressure, that is, the rising characteristic, is superior to the comparative example in Example 3.

  Here, the correspondence between the configuration of the third embodiment and the configuration of the present invention will be described. The oil passage 11 corresponds to the first oil passage of the present invention, and the oil passages 42 and 43 correspond to the present invention. The pressure relief valve 44 corresponds to the second oil passage, and corresponds to the pressure relief valve of the present invention. The valve opening hydraulic pressure of the primary regulator valve 12 corresponds to “the hydraulic pressure of the first oil passage where the pressure control valve is opened” of the present invention, and the valve opening hydraulic pressure of the pressure relief valve 44 of the present invention is “ This corresponds to “the hydraulic pressure of the first oil passage where the pressure relief valve is opened”. The correspondence relationship between the other configurations in the third embodiment and the configuration of the present invention is the same as the corresponding relationship between the configurations of the first and second embodiments and the configuration of the present invention.

  Another embodiment of the hydraulic circuit 7 constituting a part of the hydraulic control device 6 will be described with reference to FIG. The fourth embodiment is an embodiment corresponding to the inventions of claims 4, 6 and 10. In the configuration of FIG. 6, the same components as those of FIGS. 1 and 4 are denoted by the same reference numerals as those of FIGS. 1 and 4, and description thereof is omitted. In the fourth embodiment, a pressure relief valve 55 is provided instead of the pressure relief valve 44 of the third embodiment. The pressure relief valve 55 includes a throttle portion 56 that forms a port 65, a valve body 57 that opens and closes the port 65, and an elastic member 58 that biases the valve body 57 in a direction to approach the throttle portion 56. . The pressure relief valve 55 is configured such that when the oil pressure in the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure, the port 65 is closed, and when the oil pressure in the oil passages 11 and 42 exceeds the valve opening oil pressure, the valve element 57 Operates against the urging force of the elastic member 58, and the port 65 is opened.

  Further, an oil passage 60 is connected to the oil passage 42 via a pressure relief valve 59. The pressure relief valve 59 includes a valve seat 62 that forms the port 61, a valve body 63 that opens and closes the port 61, and an elastic member 64 that biases the valve body 63 in a direction to approach the valve seat 62. The pressure relief valve 59 is configured such that when the oil pressure of the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure, the port 61 is closed and when the oil pressure of the oil passages 11 and 42 exceeds the valve opening oil pressure, the valve body 63 Operates against the urging force of the elastic member 64 and the port 61 is opened.

Here, the correspondence relationship between the valve opening hydraulic pressure P1 of the primary regulator valve 12, the valve opening hydraulic pressure P2 of the pressure relief valve 59, the valve opening hydraulic pressure P3 of the pressure relief valve 55, and the target hydraulic pressure P4 is as follows.
P2>P1>P3> P4
Is set to Here, the target hydraulic pressure P4 is the hydraulic pressure of the oil passage 11 corresponding to the target hydraulic pressure of the hydraulic chamber 27 when the friction engagement device 3A is engaged. Each valve opening hydraulic pressure means the hydraulic pressure of the oil passages 11 and 42. The flow area of the port 65 of the pressure relief valve 55 is set to be narrower than the flow area of the port 45 of the pressure relief valve 44 in FIG.

  In the fourth embodiment, oil is supplied from the oil pump 8 to the oil passages 11 and 26, and the oil pressure of the oil passages 11 and 26 is increased. Further, when the condition for increasing the engagement pressure of the friction engagement device 3A is satisfied, the torque capacity of the friction engagement device 3A is increased by the hydraulic pressure of the pressure oil supplied from the oil passage 26 to the hydraulic chamber 27. Here, when the oil pressure in the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure P3, the pressure relief valves 55 and 59 and the primary regulator valve 12 are all closed. Accordingly, the oil in the oil passages 11 and 42 is not supplied to the lubrication system 17.

  Next, when the oil pressure in the oil passages 11 and 42 exceeds the valve opening oil pressure P3, the pressure relief valve 55 is opened, and the oil pressure in the oil passage 42 is higher than the oil pressure in the oil passage 43. In this case, the oil in the oil passage 42 is supplied to the lubrication system 17 via the oil passages 43 and 16. When the pressure relief valve 55 is opened and the oil pressure in the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure P3, the pressure relief valve 55 is closed and the oil passages 11 and 42 are connected. Oil is not discharged into the oil passage 43.

  When the oil pressure in the oil passage 11 further increases and the oil pressure in the oil passage 11 exceeds the valve opening oil pressure P1, the primary regulator valve 12 is opened, and the oil in the oil passage 11 passes through the primary regulator valve 12. It is discharged to the oil passage 16 via. Further, when the primary regulator valve 12 is opened and the oil pressure in the oil passage 11 decreases to the valve opening oil pressure P1 or less, the primary regulator valve 12 is closed. That is, the oil pressure of the oil passage 11 is regulated based on the same principle as in the first embodiment. At this time, the pressure relief valve 59 is closed.

  By the way, as explained in the first embodiment, when the primary regulator valve 12 fails and the oil pressure in the oil passages 11 and 42 further increases and the oil pressure exceeds the valve opening oil pressure P2, the pressure relief valve is used. 59 is opened. As a result, the oil in the oil passages 11 and 42 is discharged to the oil passage 60, and an increase in the oil pressure in the oil passages 11 and 42 is suppressed. . Further, when the pressure relief valve 59 is opened and the oil pressure in the oil passage 42 becomes equal to or less than the valve opening oil pressure P2, the pressure relief valve 59 is closed, and the oil in the oil passage 42 passes through the oil passage. No longer discharged to 60.

  FIG. 7 shows an example of a correspondence relationship between the oil pressure of the oil passage 11 in the fourth embodiment, that is, the line pressure, and the elapsed time since the driving of the oil pump 8 is started. The hydraulic characteristic corresponding to the fourth embodiment is indicated by a solid line, and the hydraulic characteristic of the comparative example is indicated by a broken line. In the fourth embodiment, when the oil discharged from the oil pump 8 fills the oil passages 11 and 26, that is, from the time t1, the line pressure becomes a hydraulic pressure exceeding zero megapascals, and the line pressure with time elapses. Tends to rise. During this time, the pressure relief valve 55 is closed.

  When the line pressure exceeds the valve opening hydraulic pressure P3 at time t3, the rising slope of the line pressure becomes gentler than the rising slope of the line pressure before time t3. Thereafter, when the line pressure further rises and the line pressure becomes near the valve opening hydraulic pressure P1 at time t4, the primary regulator valve 12 opens and closes, and the line pressure is maintained near the valve opening hydraulic pressure P1. .

  Next, a comparative example will be described. This comparative example is a hydraulic characteristic of a hydraulic circuit in which a throttle portion (not shown) is provided instead of the pressure relief valve 55 shown in FIG. This throttling portion is always in a valve open state and is not closed. That is, oil is supplied from the input side to the output side due to the pressure difference between the input side and the output side of the throttle portion. In the case of this comparative example, when the oil discharged from the oil pump reaches the throttle part, a part of the oil is discharged via the throttle part, so the time until the oil is filled in the oil path is Slower than Example 4. For this reason, for example, after time t2 later than time t1, the line pressure becomes a hydraulic pressure exceeding zero megapascals.

  In the comparative example, the line pressure increases with time. Here, the rising slope of the line pressure in the comparative example is gentler than the rising slope of the line pressure in the fourth embodiment. The reason for this is that in Example 4, unless the pressure relief valve 55 is opened, the oil in the oil passages 11 and 42 is not discharged to the oil passage 43, whereas in the comparative example, even in the process of increasing the line pressure, This is because part of the oil in the oil passage is discharged via the throttle portion. Then, after time t5 later than time t4, the line pressure in the comparative example is controlled to the hydraulic pressure P1. In Example 4, the line pressure increase gradient from time t3 to time t4 is the same as the line pressure increase gradient in the comparative example. As shown in FIG. 7, it can be seen that the rise characteristic of the line pressure, that is, the rising characteristic, is superior to the comparative example in Example 4.

  Thus, in the fourth embodiment, when the oil pressure in the oil passages 11 and 42 is equal to or lower than the valve opening oil pressure of the pressure relief valve 55, the oil in the oil passages 11 and 42 passes through the pressure relief valve 55. It is not discharged into the oil passage 43. Therefore, an increase in the work amount of the oil pump 8 can be suppressed, and the same effect as in the first embodiment can be obtained. Further, the opening hydraulic pressure P3 of the pressure relief valve 55 is set to be higher than the target hydraulic pressure P4. Therefore, it is possible to improve the response to increase in the oil pressure of the oil passages 11 and 26 and to improve the engagement response of the friction engagement device 3A.

  Here, the correspondence relationship between the configuration shown in FIGS. 2 and 6 and the configuration of the present invention will be described. The engine 2 corresponds to the driving force source of the present invention. Further, the valve opening hydraulic pressure P3 of the pressure relief valve 55 corresponds to the “valve opening hydraulic pressure of the pressure relief valve” of the present invention. The correspondence between the other configurations of the fourth embodiment and the configuration of the present invention is the same as the correspondence between the configurations of the first and third embodiments and the configuration of the present invention.

  Furthermore, a configuration example of the hydraulic circuit 7 constituting a part of the hydraulic control device 6 will be described based on FIG. The fifth embodiment corresponds to the fourth, seventh and tenth aspects of the present invention. In the configuration of FIG. 8, the same components as those of FIGS. 1 and 4 are denoted by the same reference numerals as those of FIGS. 1 and 4, and the description of the configurations is omitted. In the fifth embodiment, the oil in the oil passage 16 is supplied to the fluid transmission device 70 via the oil passage 73. Further, a torque converter pressure control valve 74 that controls the hydraulic pressure of the pressure oil supplied from the oil passage 16 to the fluid transmission device 70 is provided.

  The torque converter pressure control valve 74 has an input port 75, an output port 76, a feedback port 77, a spool 78 and an elastic member 79. The spool 78 can reciprocate in a predetermined direction, and the spool 78 is urged in a predetermined direction by the urging force of the elastic member 79. The oil path 16 is connected to the input port 75, and the lubrication system 17 is connected to the output port 76 via the oil path 80. The valve opening hydraulic pressure of the torque converter pressure control valve 74 is set to be lower than the valve opening hydraulic pressure of the pressure relief valve 49.

  Further, an oil passage 81 that connects the oil passage 54 and the oil passage 80 is provided, and a check valve 82 is provided in the oil passage 81. The check valve 82 has a function of allowing the oil in the oil passage 54 to flow into the oil passage 80 and preventing the oil in the oil passage 80 from flowing back into the oil passage 54. Thus, the oil passages 43 and 81 and the pressure relief valve 49 connect the oil passage 16 and the oil passage 80 so as to bypass the torque converter pressure control valve 74. The valve opening hydraulic pressure of the pressure relief valve 49 is set to be higher than the valve opening hydraulic pressure of the torque converter pressure control valve 74. More specifically, the valve opening hydraulic pressure of the pressure relief valve 49 is set to be higher than the minimum pressure of the target hydraulic pressure of the pressure oil supplied to the fluid transmission device 70.

  Further, a throttle portion 83 is provided in the oil passage 54 downstream of the connection portion with the oil passage 81. The flow passage area of the throttle portion 83 is set to be larger than the flow passage area in the opened state of the check valve 82. Furthermore, an oil passage 84 that connects the oil passage 42 and the oil passage 16 is provided, and a check valve 85 is provided in the oil passage 84. The check valve 85 has a function of allowing the oil in the oil passage 42 to flow into the oil passage 16 and preventing the oil in the oil passage 16 from flowing back into the oil passage 42. The flow area when the check valve 85 is open is set to be narrower than the flow area of the port 45 of the pressure relief valve 44. As described above, the oil passage 84 connects the oil passage 11 and the oil passage 16 so as to bypass the primary regulator valve 12.

  Next, the operation of the hydraulic circuit 7 shown in FIG. 8 will be described. Oil discharged from the oil pump 8 is supplied to the oil passage 11 and the amount of oil discharged to the oil passage 16 is adjusted by the function of the primary regulator valve 12 in the same manner as in the fourth embodiment. The oil discharged to the oil passage 16 is supplied to the fluid transmission device 70 via the oil passage 73. Further, the oil supplied to the oil passage 11 is supplied to the oil passage 84 via the oil passage 42, and when the oil pressure in the oil passage 84 is higher than the oil pressure in the oil passage 16, the check valve 85 is opened, and the oil in the oil passage 42 is supplied to the oil passage 16 via the oil passage 84. On the other hand, when the oil pressure in the oil passage 84 is lower than the oil pressure in the oil passage 16, the check valve 85 is closed, so that the oil in the oil passage 42 is supplied to the oil passage 16. Absent. That is, when the check valve 85 is opened, the primary regulator valve 12 is opened, or the valve is closed, the oil passage 16 is passed through the oil passage 84. Oil can be supplied.

  Similarly to the fourth embodiment, when the oil pressure in the oil passages 11 and 42 is equal to or lower than the predetermined oil pressure, the pressure relief valve 44 is closed, and the oil in the oil passage 42 is downstream of the pressure relief valve 44. Will not be discharged. On the other hand, in the same manner as in the fourth embodiment, when the oil pressure in the oil passages 11 and 42 exceeds a predetermined oil pressure, the pressure relief valve 44 is opened and the oil in the oil passage 42 is supplied to the oil passage 43. To the oil passage 16.

  As described above, the oil discharged from the oil pump 8 is supplied to the fluid transmission device 70 via the primary regulator valve 12 or the pressure relief valve 44. Next, hydraulic control of oil supplied from the oil passage 16 to the fluid transmission device 70 will be described. The oil pressure of the oil passage 16 is input to the feedback port 77 of the torque converter pressure control valve 74, and the spool 78 is biased in the opposite direction to the elastic member 79 in accordance with the oil pressure input to the feedback port 77. Then, the spool 78 operates according to the oil pressure of the oil passage 16, and the flow rate of oil discharged from the oil passage 16 to the oil passage 80 and the oil pressure of the oil passage 16 are adjusted. In this way, the oil discharged to the oil passage 80 is supplied to the lubrication system 17. As described above, the oil passing through at least one of the primary regulator valve 12 or the oil passage 84 is supplied to the oil passage 16, and the hydraulic pressure supplied to the fluid transmission device 70 is controlled by the torque converter pressure control valve 74.

  By the way, when the oil pressure of the oil passages 16 and 43 is equal to or lower than a predetermined oil pressure, the pressure relief valve 49 is closed. For this reason, the oil in the oil passages 16 and 43 is not discharged to the oil passage 54. On the other hand, when the torque converter pressure control valve 74 fails and the input port 75 and the output port 76 are fully closed, or for other reasons, the oil pressure of the oil passages 16 and 43 becomes the predetermined oil pressure. When exceeding, the pressure relief valve 49 is opened, and the oil in the oil passages 16 and 43 is discharged to the oil passage 54. Part of the oil in the oil passage 54 is discharged via the throttle portion 83, and part of the oil in the oil passage 54 is supplied to the lubrication system 17 via the oil passages 81 and 80. In this way, an excessive increase in the oil pressure in the oil passages 16 and 43 is suppressed.

  Thus, in the hydraulic circuit 7 of the fifth embodiment, the same effects as those of the first and fourth embodiments can be obtained with respect to the same components as those of the first and fourth embodiments. Further, since the pressure relief valve 44 does not open unless the oil pressure of the oil passages 11 and 42 exceeds a predetermined oil pressure, an increase in the amount of oil supplied to the lubrication system 17 via the pressure relief valve 44 can be suppressed. Therefore, it is possible to suppress an increase in the work amount of the oil pump 8, and the same effect as in the first embodiment can be obtained. Further, if the torque converter pressure control valve 74 is normal in the process of increasing the oil pressure in the oil passage 16, the pressure relief is performed when the oil pressure in the oil passage 16 is lower than the valve opening oil pressure of the torque converter pressure control valve 74. The valve 49 never opens. Therefore, it is possible to suppress a decrease in response to an increase in the hydraulic pressure of the pressure oil supplied from the oil passage 16 to the fluid transmission device 70.

  Here, the correspondence between the configuration of the fifth embodiment and the configuration of the present invention will be described. The oil passages 16, 42, 43, 54, 80, 81 correspond to the second oil passage of the present invention. The pressure relief valve 44 corresponds to the pressure relief valve of the present invention, the oil passage 16 corresponds to the downstream oil passage of the present invention, and the torque converter pressure control valve 74 corresponds to the downstream pressure control valve of the present invention. The pressure relief valve 49 corresponds to the second pressure relief valve in the present invention, the oil passage 43 corresponds to the connecting oil passage in the present invention, and the fluid transmission device 70 corresponds to the power transmission device in the present invention. The torque capacity of the fluid transmission device 70 corresponds to the power transmission state of the power transmission device of the present invention, and is higher than the hydraulic pressure of the oil passage 16 and higher than the valve opening hydraulic pressure of the torque converter pressure control valve 74. Hydraulic pressure, which corresponds to a second predetermined value of the present invention. The correspondence between the other configuration of the fifth embodiment and the configuration of the present invention is the same as the corresponding relationship between the above-described embodiment and the configuration of the present invention.

  Next, another embodiment of the hydraulic circuit 7 constituting a part of the hydraulic control device 6 will be described with reference to FIG. The sixth embodiment corresponds to the fourth, seventh and tenth embodiments. In the configuration of FIG. 9, the same components as those of FIGS. 1, 4 and 8 are denoted by the same reference numerals as those of FIGS. In the sixth embodiment, the check valve 82 described above is not provided in the oil passage 81. Further, in the sixth embodiment, a pressure relief valve 86 is provided in place of the throttle portion 83 described above. Further, an oil passage 87 is connected to the discharge side of the pressure relief valve 86. The pressure relief valve 86 is closed when the oil pressure in the oil passages 54 and 81 is equal to or lower than a predetermined oil pressure, and is opened when the oil pressure in the oil passages 54 and 81 exceeds the predetermined oil pressure. ing.

  In the sixth embodiment, the same functions and effects as those of the first, third, and fifth embodiments can be obtained with respect to the same components as those of the first, third, and fifth embodiments. When the oil pressure in the oil passages 54 and 81 is equal to or lower than the predetermined oil pressure, the pressure relief valve 86 is closed, and the oil in the oil passages 54 and 81 is not discharged to the oil passage 87. On the other hand, when the oil pressure in the oil passages 54 and 81 exceeds a predetermined oil pressure, the pressure relief valve 86 is opened, and the oil in the oil passages 54 and 81 is discharged to the oil passage 87. , 81 is suppressed from further increasing.

  Here, an example of the control characteristic of the torque converter pressure in the hydraulic circuit 7 of the fifth and sixth embodiments will be described with reference to FIG. FIG. 10 is a diagram showing an example of the relationship between the elapsed time from the start of driving of the oil pump 8 and the oil pressure of the oil passage 73, that is, the torque converter pressure. The hydraulic pressure characteristics corresponding to Examples 5 and 6 are indicated by solid lines, and the hydraulic pressure characteristics of the comparative example are indicated by broken lines. In Examples 5 and 6, when the oil discharged from the oil pump 8 fills the oil passages 16, 43, 73 and the like, that is, from time t1, the torque converter pressure becomes a hydraulic pressure exceeding zero megapascals, and the time As the time elapses, the torque converter pressure tends to increase. If torque converter pressure control valve 74 is normal, the torque converter pressure is maintained at a substantially constant predetermined pressure after time t3 by the pressure regulating function of torque converter pressure control valve 74.

  Next, a comparative example will be described. This comparative example is an oil passage 84 shown in FIGS. 9 and 10 in which oil upstream of the check valve 85 passes through a throttle (not shown) and lubricates without going through a pressure relief valve. It is a hydraulic characteristic of the hydraulic circuit provided with the oil path of the structure which discharges oil to a system | strain. This throttling portion is always in a valve open state and is not closed. That is, oil is supplied from the input side to the output side due to the pressure difference between the input side and the output side of the throttle portion. In the case of this comparative example, when the oil discharged from the oil pump reaches the throttle portion, a part of the oil is discharged via the throttle portion, so that the oil passages 16, 43, 73 are filled with oil. The time until is slower than in Examples 5 and 6. For this reason, for example, after time t2 later than time t1, the torque converter pressure becomes a hydraulic pressure exceeding zero megapascals.

  In the comparative example, the torque converter pressure increases with time. Here, the rising gradient of the torque converter pressure in the comparative example is gentler than the rising gradient of the torque converter pressure in the fifth and sixth embodiments. The reason is that in Examples 5 and 6, the oil in the oil passage 16 is not discharged to the oil passage 80 unless the torque converter pressure control valve 74 is opened, whereas in the comparative example, the torque converter pressure increases. This is because part of the oil in the oil passage 84 is discharged to the oil passage 80 via the throttle portion even in the process. Then, after time t4 later than time t3, the torque converter pressure in the comparative example is controlled to a predetermined pressure. As shown in FIG. 10, it can be seen that the rising characteristics of the torque converter pressure, that is, the rising characteristics, are superior in Examples 5 and 6 than in the comparative example. The correspondence relationship between the configuration of the sixth embodiment and the configuration of the present invention is the same as the correspondence relationship described in the fifth embodiment.

  Furthermore, another embodiment of the hydraulic circuit 7 constituting a part of the hydraulic control device 6 will be described with reference to FIG. The seventh embodiment corresponds to the fourth, eighth and tenth aspects of the present invention. In the configuration of FIG. 11, the same configurations as those of FIGS. 1, 4, and 8 are denoted by the same reference numerals as those of FIGS. 1, 4, and 8, and the description of the configurations is omitted. First, the downstream side of the pressure relief valve 44 is connected to an oil pan (not shown). In addition, a throttle portion 88 is provided between the check valve 85 and the oil passage 42 in the oil passage 84. In addition, an oil passage 89 is provided between the throttle portion 88 and the check valve 85, and an oil passage 89 is connected to the oil passage 80, and a pressure relief valve 90 is provided in the oil passage 89. ing.

  The pressure relief valve 90 includes a throttle portion 92 that forms a port 91, a valve body 93 that opens and closes the port 91, and an elastic member 94 that urges the valve body 93 toward the throttle portion 92. . The pressure relief valve 90 is an oil passage 89, and when the oil pressure upstream of the pressure relief valve 90 is equal to or lower than the valve opening oil pressure, the port 91 is closed and the oil passage 89 is provided. When the upstream hydraulic pressure exceeds the valve opening hydraulic pressure, the valve body 93 operates against the urging force of the elastic member 94 and the port 91 is opened.

  Furthermore, an oil passage 95 that connects the oil passage 16 and the oil pan is formed, and a pressure relief valve 96 is provided in the oil passage 95. Here, the valve opening hydraulic pressure of the torque converter pressure control valve 74 is set to be higher than the valve opening hydraulic pressure of the pressure relief valve 90, and the valve opening hydraulic pressure of the pressure relief valve 96 is set to the torque converter pressure control valve 74. The valve opening hydraulic pressure is set to be higher than that. More specifically, the valve opening hydraulic pressure of the pressure relief valve 90 is set to be higher than the minimum pressure of the target hydraulic pressure of the pressure oil supplied to the fluid transmission device 70.

  Next, the operation of the hydraulic circuit 7 shown in FIG. 11 will be described. In the configuration of FIG. 11, the same operation as the configuration of FIGS. 1, 4, and 8 occurs for the same configuration as the configurations of FIGS. In FIG. 11, when the oil discharged from the oil pump 8 is supplied to the oil passage 84 via the oil passage 11 and the oil passage 42, the oil that has passed through the throttle portion 88 is supplied to the check valve 85. The Here, in the oil passage 84, when the oil pressure in the oil passage 16 is higher than the oil pressure upstream of the check valve 85, the check valve 85 is closed and the oil in the oil passage 84 is Is not supplied to the oil passage 16. On the other hand, in the oil passage 84, when the oil pressure upstream of the check valve 85 is higher than the oil pressure in the oil passage 16, the check valve 85 is opened and the oil passage 84 is opened. The oil is supplied to the oil passage 16. Thus, in the seventh embodiment, the oil that has passed through at least one of the oil passage 84 or the primary regulator valve 12 is supplied to the oil passage 16.

  Incidentally, part of the oil in the oil passage 84 is also supplied to the oil passage 89. Here, in the oil passage 89, when the hydraulic pressure upstream of the pressure relief valve 90 is equal to or lower than a predetermined hydraulic pressure, the pressure relief valve 90 is closed. Therefore, the oil in the oil passage 84 is not supplied to the oil passage 80 via the pressure relief valve 90. On the other hand, in the oil passage 89, when the oil pressure upstream of the pressure relief valve 90 exceeds a predetermined oil pressure, the pressure relief valve 90 is opened, and a part of the oil in the oil passage 84 is oiled. The oil is supplied to the oil passage 80 via the passage 89, and the oil in the oil passage 80 is supplied to the lubrication system 17. At this time, the torque converter pressure control valve 74 is closed. In the oil passage 89, when the hydraulic pressure upstream of the pressure relief valve 90 drops below a predetermined hydraulic pressure, the pressure relief valve 90 is closed. Further, when the oil pressure in the oil passage 16 rises and the torque converter pressure control valve 74 is opened, a part of the oil in the oil passage 16 is transferred to the oil passage 80 via the torque converter pressure control valve 74. The oil pressure of the oil passage 16 is suppressed from being supplied.

  Incidentally, when the torque converter pressure control valve 74 fails and the input port 75 and the output port 76 are shut off and the oil pressure in the oil passage 16 exceeds a predetermined oil pressure, or the torque converter pressure control valve 74 is normal. Nevertheless, when the amount of oil supplied to the oil passage 16 is larger than the amount of oil required by the fluid transmission device 70 and the oil pressure of the oil passage 16 exceeds a predetermined oil pressure, the pressure relief valve 96 is used. Is opened, and the oil in the oil passage 16 is discharged to the oil pan. Therefore, further increase in the oil pressure of the oil passage 16 is suppressed. When the oil pressure in the oil passage 16 becomes equal to or lower than the valve opening oil pressure of the pressure relief valve 96, the pressure relief valve 96 is closed.

  As described above, in the seventh embodiment, the pressure relief valve 90 is opened only when the hydraulic pressure in the oil passage 89 and upstream of the pressure relief valve 90 exceeds the valve opening hydraulic pressure of the pressure relief valve 90. The oil in the oil passage 84 is supplied to the oil passage 80 via the oil passage 89 and then supplied to the lubrication system 17. In this way, it is possible to suppress an increase in the amount of oil supplied to the lubrication system 17 via the oil passage 89, and it is possible to suppress an increase in the work amount of the oil pump 8. Therefore, it is possible to obtain the same effect as in the first embodiment. Further, when the hydraulic pressure of the pressure oil supplied to the fluid transmission device 70 is increased, if the pressure relief valve 90 is closed, the rising response of the pressure oil supplied to the fluid transmission device 70 is improved. .

  FIG. 12 shows an example of a correspondence relationship between the oil pressure of the oil passage 16 in the seventh embodiment, that is, the torque converter pressure, and the elapsed time since the drive of the oil pump 8 is started. The hydraulic characteristic corresponding to the seventh embodiment is indicated by a solid line, and the hydraulic characteristic of the comparative example is indicated by a broken line. In the seventh embodiment, when the oil discharged from the oil pump 8 fills the oil passages 16 and 73, that is, from the time t1, the torque converter pressure becomes a hydraulic pressure exceeding zero megapascals, and the torque with the passage of time. The converter pressure tends to increase. During this time, the pressure relief valve 90 is closed.

  When the torque converter pressure exceeds the hydraulic pressure P3 at time t3, when the pressure relief valve 90 is opened, the rising gradient of the torque converter pressure becomes gentler than the rising gradient of the torque converter pressure before time t3. . Thereafter, when the oil pressure in the oil passages 16 and 73 becomes close to the opening hydraulic pressure of the torque converter pressure control valve 74, the torque converter pressure control valve 74 is opened and closed, and the torque converter pressure is controlled to be substantially constant.

  Next, a comparative example will be described. This comparative example is a hydraulic characteristic of a hydraulic circuit in which a throttle portion (not shown) is provided instead of the pressure relief valve 90 shown in FIG. This throttling portion is always in a valve open state and is not closed. That is, oil is supplied from the input side to the output side due to the pressure difference between the input side and the output side of the throttle portion. In the case of this comparative example, when the oil discharged from the oil pump reaches the oil passage 89, a part of the oil is always supplied to the lubrication system 17 via the throttle portion. The time until the oil is filled becomes slower than that in Example 7. For this reason, for example, after time t2 later than time t1, the torque converter pressure becomes a hydraulic pressure exceeding zero megapascals.

  In the comparative example, the torque converter pressure increases with time. Here, the rising gradient of the torque converter pressure in the comparative example is gentler than the rising gradient of the torque converter pressure in the seventh embodiment. The reason is that, in the seventh embodiment, when the oil pressure of the oil passage 16 is equal to or lower than the valve opening oil pressure of the pressure relief valve 90, the oil is not supplied to the lubrication system 17 via the oil passage 89. In the comparative example, part of the oil in the oil passage 84 is supplied to the lubrication system via the throttle portion even in the process of increasing the torque converter pressure. Then, after time t5 later than time t4, the torque converter pressure in the comparative example is controlled to the hydraulic pressure P1. In Example 7, the increasing gradient of the torque converter pressure between time t3 and time t4 is the same as the increasing gradient of the torque converter pressure in the comparative example. As shown in FIG. 12, it can be seen that the rise characteristic of the torque converter pressure, that is, the rising characteristic, is superior to the comparative example in the seventh embodiment.

  Here, the correspondence relationship between the configuration of the seventh embodiment and the configuration of the present invention will be described. The oil passages 42, 84, 89 correspond to the second oil passage of the present invention, and the pressure relief valve 90 is This corresponds to the pressure relief valve of the present invention, and the oil passage 84 corresponds to the connection oil passage of the present invention. The correspondence between the other configurations of the seventh embodiment and the configuration of the present invention is the same as the corresponding relationship between the above-described embodiments and the configuration of the present invention.

  In each embodiment, the throttle portion may be either an orifice or a choke. In each embodiment, either a power train having a configuration in which the wheels to which the power of the engine is transmitted and a wheel to which the power of the traveling motor is transmitted may be the same, or a power train having a different configuration. In each embodiment, the hydraulic chamber to which the pressure oil regulated by the pressure control valve is supplied may be a hydraulic chamber that controls the engagement pressure of the friction engagement device that constitutes a part of the transmission. Good. The fifth, sixth, and seventh embodiments are also applicable to a hydraulic circuit that is configured to supply oil from the oil passage 16 to a hydraulic chamber (not shown) of the secondary pulley 4B. In this case, the “torque converter pressure control valve” described in the fifth, sixth, and seventh embodiments may be replaced with “secondary pressure control valve”, and “torque converter pressure” may be replaced with “secondary pressure”. Further, in this case, the winding radius of the belt 4C in the secondary pulley 4B, the gear ratio of the belt-type continuously variable transmission 4, the torque capacity of the belt-type continuously variable transmission 4, and the clamping pressure applied to the belt 4C from the secondary pulley 4B These correspond to the “power transmission state of the power transmission device” in the present invention. In FIGS. 5, 7, and 12, even if the same time is used in different diagrams, there is no correspondence between these times.

It is a conceptual diagram which shows Example 1 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a conceptual diagram which shows the power train of the vehicle which has the hydraulic control apparatus of the transmission of this invention. It is a conceptual diagram which shows Example 2 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a conceptual diagram which shows Example 3 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a diagram which shows an example which compared the rising characteristic of the hydraulic pressure in Example 3, and the rising characteristic of the hydraulic pressure in the comparative example. It is a conceptual diagram which shows Example 4 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a diagram which shows an example which compared the rising characteristic of the hydraulic pressure in Example 4, and the rising characteristic of the hydraulic pressure in a comparative example. It is a conceptual diagram which shows Example 5 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a conceptual diagram which shows Example 6 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a diagram which shows an example which compared the rising characteristic of the hydraulic pressure in Examples 5 and 6 and the rising characteristic of the hydraulic pressure in the comparative example. It is a conceptual diagram which shows Example 7 of the hydraulic circuit used for the hydraulic control apparatus of the transmission of this invention. It is a diagram which shows an example which compared the rising characteristic of the hydraulic pressure in Example 7, and the rising characteristic of the hydraulic pressure in a comparative example.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Engine, 3A ... Friction engagement apparatus, 5 ... Wheel, 8 ... 1st oil pump (oil pump), 9 ... 2nd oil pump, 10 ... Electric motor, 11, 16, 21, 28, 26, 30 , 42, 43, 80, 81, 84, 89 ... oil passage, 12 ... primary regulator valve, 17 ... lubrication system, 18, 23, 29 ... check valve, 22, 31 ... throttle part, 44, 55, 49, 90 ... Pressure relief valve, 70 ... Fluid transmission device, 74 ... Torque converter pressure control valve.

Claims (10)

A first supply path for supplying oil to a lubrication system via a pressure control valve; and a transmission lubrication device capable of supplying oil to the lubrication system when the pressure control valve fails.
A first oil pump driven by an engine and a second oil pump driven by an electric motor;
The oil discharged from the first oil pump is supplied to the pressure control valve via the first check valve, and the oil discharged from the second oil pump is supplied to the second reverse valve. A first oil pump, a second oil pump, a first check valve, and a second check valve are provided in the first supply path so as to be supplied to the pressure control valve via a stop valve. And a pressure control valve is arranged,
When the pressure control valve fails, oil that flows upstream from the first check valve in the flow direction of the oil discharged from the first oil pump is supplied to the throttle portion and the third check valve. A transmission lubrication device, characterized in that a second supply path is provided for supply to the lubrication system via   The said 1st supply path is comprised so that all the oil supplied to the said lubrication system from a said 2nd oil pump may pass through the said pressure control valve, The Claim 1 characterized by the above-mentioned. Transmission lubrication device.   A third supply path is provided in parallel with the pressure control valve in a path from the second oil pump to the lubrication system, and from the first oil pump via the first supply path. A flow rate control device is provided to reduce the amount of oil supplied from the second oil pump to the lubrication system via the third supply path rather than the amount of oil supplied to the lubrication system. The transmission lubrication device according to claim 1. The oil pressure of the first oil passage is controlled by controlling the first oil passage to which oil discharged from the oil pump is supplied and the flow rate of the oil discharged from the first oil passage to the lubrication system. When the pressure control valve is connected to the first oil passage and the pressure control valve fails, the oil in the first oil passage is bypassed by the pressure control valve to the lubrication system. In a lubricating device for a transmission having a second oil passage to be supplied,
The second oil passage is closed when the hydraulic pressure of the first oil passage is equal to or lower than the valve opening hydraulic pressure, and is opened when the hydraulic pressure of the first oil passage exceeds the valve opening hydraulic pressure. A lubrication device for a transmission, wherein a pressure relief valve is provided.   The hydraulic pressure of the first oil passage where the pressure relief valve is opened is set to be higher than the hydraulic pressure of the first oil passage where the pressure control valve is opened. Item 5. The transmission lubrication device according to Item 4.   A friction engagement device is provided in a power transmission path from the driving force source to the wheel, and the torque capacity of the friction engagement device is controlled by the pressure oil in the first oil passage. The valve opening hydraulic pressure of the pressure relief valve is set to be higher than the target hydraulic pressure of the first oil passage when the friction engagement device is engaged. Gearbox lubrication device. The oil discharged from the pressure control valve is configured to be supplied to the lubrication system via a downstream oil passage and a downstream pressure control valve, and the downstream pressure control valve is configured to be connected to the downstream oil passage. By controlling the oil amount discharged from the lubrication system to the hydraulic pressure of the downstream oil passage,
A second pressure relief valve provided between the pressure relief valve and the lubrication system, wherein the second oil passage comprises the pressure relief valve and the second oil passage. A connection oil passage is provided between the second pressure relief valve and the downstream oil passage, and the second pressure relief valve has a second predetermined oil pressure at the second oil passage. A configuration that is closed when the value is equal to or smaller than the value and is opened when the second predetermined value is exceeded,
A power transmission device that transmits the power of the driving force source to the wheels is provided, and a power transmission state in the power transmission path is controlled by pressure oil supplied from the downstream oil passage to the power transmission device The transmission lubrication device according to claim 4, wherein: The oil discharged from the pressure control valve is configured to be supplied to the lubrication system via a downstream oil passage and a downstream pressure control valve, and the downstream pressure control valve is configured to be connected to the downstream oil passage. By controlling the oil amount discharged to the lubrication system by controlling the oil pressure of the downstream oil passage, the second oil passage comprising the pressure relief valve and the pressure control. A connecting oil passage that connects between the valve and the downstream oil passage is provided,
A power transmission device that transmits the power of the driving force source to the wheels is provided, and a power transmission state in the power transmission path is controlled by pressure oil supplied from the downstream oil passage to the power transmission device The transmission lubrication device according to claim 4, wherein: A first supply path for supplying oil to the lubrication system via the pressure control valve, and when the amount of oil supplied to the lubrication system via the first supply path decreases, In a transmission lubrication device capable of supplying oil,
A first oil pump driven by an engine and a second oil pump driven by an electric motor, and the oil discharged from the first oil pump passes through a first check valve; The first supply path is configured so that oil supplied to the pressure control valve and discharged from the second oil pump is supplied to the pressure control valve via a second check valve. In addition, a first oil pump, a second oil pump, a first check valve, a second check valve and a pressure control valve are disposed, and the lubrication is performed via the first supply path. When the amount of oil supplied to the system decreases, the oil flowing upstream from the first check valve in the flow direction of the oil discharged from the first oil pump Lubricating system via check valve Lubricating device for a transmission, wherein the second supply path is provided for supplying. The oil pressure of the first oil passage is controlled by controlling the first oil passage to which oil discharged from the oil pump is supplied and the flow rate of oil supplied from the first oil passage to the lubrication system. When the pressure control valve is connected to the first oil passage and the oil pressure of the first oil passage rises to a predetermined pressure or higher, the oil in the first oil passage is supplied to the pressure control valve. In a transmission lubrication device having a second oil passage that is bypassed and supplied to the lubrication system,
The second oil passage is provided with a pressure relief valve that is closed when the hydraulic pressure of the first oil passage is equal to or lower than a predetermined value and opened when the hydraulic pressure of the first oil passage exceeds a predetermined value. A transmission lubrication device.

Images