JP6491007B2 - Oil pump discharge rate switching device - Google Patents

Description

  The present invention relates to a discharge amount switching device for an oil pump.

  An automatic transmission for a vehicle (for example, a stepped automatic transmission (Step AT) or a continuously variable transmission (CVT)) includes an oil pump that is driven by engine power and discharges high-pressure hydraulic oil. By adjusting and supplying high-pressure hydraulic fluid discharged from the pump, various functions such as shifting and forward / reverse switching are realized.

  On the other hand, in recent years, there has been a demand for reducing the load on the oil pump in response to a request for improving the fuel consumption of vehicles. As a technique for reducing the load of such an oil pump, for example, Patent Document 1 discloses a variable displacement pump that discharges oil sucked from two suction ports from two discharge ports, and two discharge ports have two suction ports. Technology for switching to a full capacity operation state that is completely shut off from the port, or a half capacity (partial capacity) operation state where one of the two discharge ports communicates with one of the suction ports (operation state switching device for variable displacement pump) ) Is disclosed.

  More specifically, the variable displacement pump operation state switching device described in Patent Document 1 includes an electronic control unit that switches the operation state of the oil pump between the full-capacity operation state and the half-capacity operation state. The unit includes a half capacity operation state discharge flow rate calculation unit, a required discharge flow rate calculation unit, and an operation state switching unit. The half-capacity operation state discharge flow rate calculating means is configured to determine the oil amount when the oil pump is in a half-capacity operation state based on the engine speed detected by the engine speed sensor and the transmission oil temperature detected by the transmission oil temperature sensor. The discharge flow rate is calculated. The required discharge flow rate calculation means calculates the required discharge flow rate of the oil pump currently required based on the specifications of the vehicle and the driving state of the vehicle. Here, the required discharge flow rate is a flow rate required for shifting by changing the side pressure of the drive pulley and driven pulley of the transmission, a flow rate corresponding to the amount of oil leakage from the hydraulic circuit of the transmission, The flow rate is necessary to lubricate the lubrication part.

  The operation state switching means subtracts the required discharge flow rate of the oil pump calculated by the required discharge flow rate calculation means from the discharge flow rate when the oil pump calculated by the half capacity operation state discharge flow rate calculation means is in the half capacity operation state. If the surplus flow rate is calculated and the surplus flow rate is greater than or equal to a preset threshold value, the shift solenoid valve is controlled to control the oil pump operation state to a half capacity operation state. Control to full capacity operation.

  According to this variable displacement pump operation state switching device, the difference between the oil pump discharge flow rate calculated by the half capacity operation state discharge flow rate calculation means and the oil pump required discharge flow rate calculated by the required discharge flow rate calculation means (margin) When the flow rate is equal to or higher than the predetermined determination threshold, the operation state switching means switches the variable displacement oil pump to the half displacement operation state, so that the drive energy of the variable displacement oil pump can be reduced while ensuring the minimum required discharge flow rate. You can save.

International Publication No. 2013/069101

  Incidentally, as described above, in the variable displacement pump operation state switching device described in Patent Document 1, the oil pump discharge flow rate when the engine is in the half displacement operation state calculated based on the engine speed and the transmission oil temperature The shift solenoid valve is controlled when the difference (margin flow rate) with the required discharge flow rate of the oil pump calculated from the vehicle specifications and the driving state of the vehicle is equal to or greater than a predetermined determination threshold value set in advance. Thus, the operation state of the oil pump is switched to the half capacity operation state, and if it is less than the determination threshold, the oil pump is switched to the full capacity operation state.

  Here, normally, in an electronic control unit, for example, an oil pump, a pump shift valve, a shift solenoid valve, and various sensors (characteristics), etc., manufacturing variability and control delay are taken into consideration (that is, a worst case is assumed), and safety is ensured. Switching between the full capacity operation state (full discharge operation state) and the half capacity operation state (half discharge operation state) is controlled with a margin on the side. In other words, there is a margin on the safe side in the calculation of the discharge flow rate of the oil pump in the half capacity operation state, the calculation of the required discharge flow rate of the oil pump, and the setting of a predetermined judgment threshold compared with the surplus flow rate. Need to be processed.

  Further, in the variable capacity pump operation state switching device described in Patent Document 1, it is assumed that the relationship between the flow balance calculation and the actual machine is deviated when the lock-up clutch is momentarily slipped or continuously slipped. It is set to the full discharge operation state. Similarly, since it is difficult to ensure the accuracy of the flow balance calculation immediately after the vehicle starts, the oil pump is set to the full discharge operation state. As described above, in the variable displacement pump operation state switching device described in Patent Document 1, the half discharge (partial discharge) operation region is limited, and there is a possibility that the load reduction effect of the oil pump cannot be sufficiently obtained. .

  On the other hand, depending on the operating state of the automatic transmission, for example, at extremely low temperatures, at the time of starting, or when it is desired to increase the shift speed, there are cases where it is desired to fix the oil pump to a full discharge state or a half discharge (partial discharge) state.

  The present invention has been made in order to solve the above-mentioned problems, and depending on the operation state, it is possible to fix the full discharge state or the partial discharge state, while expanding the operation region in the partial discharge state. An object of the present invention is to provide an oil pump discharge amount switching device capable of further reducing the load on the pump and further reducing the fuel consumption rate (fuel consumption).

  An oil pump discharge amount switching device according to the present invention boosts oil sucked from a suction port and discharges it from a plurality of discharge ports, and the discharge state of the oil pump based on the operating state of the automatic transmission. , All the discharge ports are all in communication with the high pressure oil passage, or some of the plurality of discharge ports are in communication with the high pressure oil passage, and some of the other discharge ports of the oil pump The switch hydraulic pressure generating means for generating the switch hydraulic pressure for switching between the fixed discharge state and the non-fixed state communicated with the suction port, and the pressing force by the actual hydraulic pressure of the high pressure oil passage between the full discharge state and the partial discharge state And a discharge state switching means for switching in accordance with a pressure difference between the pressing force by the control oil pressure for adjusting the oil pressure and the pressing force by the switch oil pressure generated by the switch oil pressure generating means. .

  According to the discharge amount switching device for an oil pump according to the present invention, the pressing force by the actual hydraulic pressure of the high-pressure oil passage, the pressing force by the actual control hydraulic pressure that is the control pressure of the hydraulic pressure, and the pressing force by the switch hydraulic pressure Depending on the difference in pressing force, all discharge states in which all of the plurality of discharge ports communicate with the high pressure oil passage, some discharge ports included in the plurality of discharge ports communicate with the high pressure oil passage, and some other The partial discharge state in which the discharge port is communicated with the suction port of the oil pump is switched. In other words, the switch hydraulic pressure can be adjusted according to the operating state of the automatic transmission to fix the full discharge state or the partial discharge state. In addition, when the switch hydraulic pressure is adjusted so that it is not fixed in either the full discharge state or the partial discharge state, depending on the pressure difference between the pressing force by the actual hydraulic pressure of the high pressure oil passage and the pressing force by the control hydraulic pressure The full discharge state and the partial discharge state can be switched. Therefore, in this case, it is not necessary to perform drive control of the shift solenoid valve or the like with a margin in consideration of component variations and control delay as in the prior art. As a result, it is possible to fix the full discharge state or the partial discharge state depending on the operation state, and it is possible to expand the operation region in the partial discharge state to further reduce the load of the oil pump, and to reduce the fuel consumption rate ( (Fuel consumption) can be further reduced.

  In the discharge amount switching device for an oil pump according to the present invention, when the discharge state switching means has a pressing force including the pressing force due to the switch hydraulic pressure and the pressing force due to the actual hydraulic pressure in the high-pressure oil passage is larger than the pressing force due to the control hydraulic pressure. In this case, the oil passage is switched so that a partial discharge state is reached, and if the pushing force including the pushing force by the switch oil pressure and the pushing force by the actual oil pressure of the high pressure oil passage is less than the pushing force by the control oil pressure, the full discharge It is preferable to switch the oil path so as to be in a state.

  In this way, the partial discharge state can be fixed by increasing the pressing force by the switch hydraulic pressure (for example, more than the pressing force by the control hydraulic pressure). On the other hand, by reducing the pressing force due to the switch hydraulic pressure (for example, zero), which of the pressing force including the pressing force due to the switch hydraulic pressure and the pressing force due to the actual hydraulic pressure in the high-pressure oil passage, or the pressing force due to the control hydraulic pressure is greater? Thus, the oil passage can be switched accurately (that is, switching between the partial discharge state and the full discharge state).

  On the other hand, in the discharge amount switching device of the oil pump according to the present invention, the discharge state switching means is such that the pressing force including the pressing force due to the actual hydraulic pressure of the high-pressure oil passage is larger than the pressing force due to the switch hydraulic pressure and the pressing force due to the control hydraulic pressure. In this case, the oil passage is switched so that a partial discharge state is reached. It is preferable to switch the oil path so as to be in a state.

  In this way, it is possible to fix the full discharge state by increasing the pressing force by the switch hydraulic pressure (for example, more than the pressing force by the actual hydraulic pressure). On the other hand, by reducing the pressing force by the switch hydraulic pressure (for example, zero), which of the pressing force including the pressing force by the actual hydraulic pressure of the high-pressure oil passage, the pressing force by the switch hydraulic pressure, and the pressing force by the control hydraulic pressure is larger? Thus, the oil passage can be switched accurately (that is, switching between the partial discharge state and the full discharge state).

  An oil pump discharge amount switching device according to the present invention includes an oil pump having a first discharge port and a second discharge port for discharging pressurized oil, a high-pressure oil passage communicating with the first discharge port, and an automatic transmission. Based on the operation state, the switch hydraulic pressure for switching whether or not to fix the discharge destination of the oil discharged from the second discharge port to the high-pressure oil passage or the low-pressure oil passage communicating with the suction port of the oil pump is The switch hydraulic pressure generating means to be generated, the pressing force by the actual hydraulic pressure of the high pressure oil passage, the pressing force by the control hydraulic pressure for adjusting the hydraulic pressure, and the pressing force by the switch hydraulic pressure generated by the switch hydraulic pressure generating means A switching control valve that switches a discharge destination of oil discharged from the second discharge port between a high-pressure oil passage and a low-pressure oil passage based on the force difference is provided.

  According to the discharge amount switching device for an oil pump according to the present invention, the pressing force by the actual hydraulic pressure of the high-pressure oil passage, the pressing force by the actual control hydraulic pressure that is the control pressure of the hydraulic pressure, and the pressing force by the switch hydraulic pressure The discharge destination of the oil discharged from the second discharge port is switched between the high pressure oil passage and the low pressure oil passage communicating with the suction port of the oil pump in accordance with the pressing force difference. In other words, the switch hydraulic pressure can be adjusted based on the operating state of the automatic transmission to fix the full discharge state or the partial discharge state. In addition, when the switch hydraulic pressure is adjusted so that it is not fixed in either the full discharge state or the partial discharge state, depending on the pressure difference between the pressing force by the actual hydraulic pressure of the high pressure oil passage and the pressing force by the control hydraulic pressure The full discharge state and the partial discharge state can be switched. Therefore, in that case, it is not necessary to perform drive control of the shift solenoid valve with a margin in consideration of component variations and control delay as in the prior art. As a result, it is possible to fix the full discharge state or the partial discharge state depending on the operation state, and it is possible to expand the operation region in the partial discharge state to further reduce the load of the oil pump, and to reduce the fuel consumption rate ( (Fuel consumption) can be further reduced.

  In the oil pump discharge amount switching device according to the present invention, when the switching control valve has a pressing force including the pressing force due to the switch hydraulic pressure and the pressing force due to the actual hydraulic pressure in the high-pressure oil passage larger than the pressing force due to the control hydraulic pressure. Switches the oil passage so that the second discharge port communicates with the low pressure oil passage, and the pushing force including the pushing force by the switch oil pressure and the pushing force by the actual oil pressure of the high pressure oil passage is less than the pushing force by the control oil pressure. In this case, it is preferable to switch the oil passage so that the second discharge port and the high-pressure oil passage communicate with each other.

  In this way, the partial discharge state can be fixed by increasing the pressing force by the switch hydraulic pressure (for example, more than the pressing force by the control hydraulic pressure). On the other hand, by reducing the pressing force due to the switch hydraulic pressure (for example, zero), which of the pressing force including the pressing force due to the switch hydraulic pressure and the pressing force due to the actual hydraulic pressure in the high-pressure oil passage, or the pressing force due to the control hydraulic pressure is greater? Thus, the communication state of the second discharge port of the oil pump can be appropriately switched between the low pressure oil passage and the high pressure oil passage.

  On the other hand, in the discharge amount switching device of the oil pump according to the present invention, when the switching control valve has a pressing force including the pressing force due to the actual hydraulic pressure of the high-pressure oil passage is larger than the pressing force due to the switch hydraulic pressure and the pressing force due to the control hydraulic pressure. The oil passage is switched so that the second discharge port communicates with the low pressure oil passage, and the pushing force including the pushing force by the actual oil pressure of the high pressure oil passage is less than the pushing force by the switch oil pressure and the pushing force by the control oil pressure. In this case, it is preferable to switch the oil passage so that the second discharge port and the high-pressure oil passage communicate with each other.

  In this way, it is possible to fix the full discharge state by increasing the pressing force by the switch hydraulic pressure (for example, more than the pressing force by the actual hydraulic pressure). On the other hand, by reducing the pressing force by the switch hydraulic pressure (for example, zero), which of the pressing force including the pressing force by the actual hydraulic pressure of the high-pressure oil passage, the pressing force by the switch hydraulic pressure, and the pressing force by the control hydraulic pressure is larger? Thus, the communication state of the second discharge port of the oil pump can be appropriately switched between the low pressure oil passage and the high pressure oil passage.

  In the discharge amount switching device of the oil pump according to the present invention, the switch oil pressure generating means fixes the discharge destination of the oil discharged from the second discharge port to the low pressure oil passage when the oil temperature is lower than the predetermined temperature. Thus, it is preferable to generate the switch hydraulic pressure.

  In this case, when the oil temperature (oil temperature) is lower than the predetermined temperature, the discharge destination of the oil discharged from the second discharge port is fixed to the low pressure oil passage. Therefore, for example, it is possible to fix the semi-discharge state at an extremely low temperature. Therefore, the occurrence of cavitation can be prevented, and noise (vibration) performance and reliability can be improved.

  In the discharge amount switching device for an oil pump according to the present invention, the switch oil pressure generating means determines the discharge destination of the oil discharged from the second discharge port when the rotation speed of the oil pump is equal to or higher than a predetermined rotation speed. It is preferable to generate the switch hydraulic pressure so as to be fixed to.

  In this case, when the rotation speed of the oil pump is equal to or higher than the predetermined rotation speed, the discharge destination of the oil discharged from the second discharge port is fixed to the low pressure oil passage. Therefore, for example, when the number of rotations of the oil pump is high, it can be fixed in a semi-discharge state. Therefore, the occurrence of cavitation can be prevented, and noise (vibration) performance and reliability can be improved.

  In the discharge amount switching device for an oil pump according to the present invention, the switch oil pressure generating means determines the discharge destination of the oil discharged from the second discharge port when the vehicle on which the automatic transmission is mounted is traveling normally. The switch hydraulic pressure is preferably generated so as to be fixed to the low-pressure oil passage.

  In this case, when the vehicle is traveling steadily, the discharge destination of the oil discharged from the second discharge port is fixed to the low pressure oil passage. Therefore, the occurrence of hydraulic pulsation due to switching between the full discharge state and the partial discharge state can be prevented, and reliability can be improved.

  In the discharge amount switching device for an oil pump according to the present invention, the switch oil pressure generating means is configured to change the discharge destination of the oil discharged from the second discharge port when the shift range of the automatic transmission is the neutral range or the parking range. It is preferable to generate the switch hydraulic pressure so as to be fixed to the oil passage.

  In this case, when the shift range is the neutral (neutral) range or the parking (parking) range, the discharge destination of the oil discharged from the second discharge port is fixed to the high-pressure oil passage. Therefore, after that, when the shift range is switched to the drive (forward) range or the reverse (reverse) range, a sufficient hydraulic flow rate can be secured, and the responsiveness at the start can be improved.

  In the discharge amount switching device for an oil pump according to the present invention, the switch hydraulic pressure generating means determines the discharge destination of the oil discharged from the second discharge port when the shift speed of the automatic transmission is equal to or higher than a predetermined speed. It is preferable to generate the switch hydraulic pressure so as to be fixed to.

  In this case, when the shift speed is equal to or higher than the predetermined speed, the discharge destination of the oil discharged from the second discharge port is fixed to the high-pressure oil passage. Therefore, a sufficient hydraulic flow rate can be ensured and a desired shift speed can be ensured at the time of a sudden shift that requires a large flow rate (a large amount of hydraulic flow rate).

  According to the present invention, it is possible to fix the full discharge state or the partial discharge state depending on the operation state, and it is possible to expand the operation region in the partial discharge state and further reduce the load of the oil pump, The consumption rate (fuel consumption) can be further reduced.

It is a figure which shows the structure of the continuously variable transmission to which the discharge amount switching apparatus of the oil pump which concerns on 1st Embodiment is applied. It is a figure which shows the structure of the discharge amount switching apparatus of the oil pump which concerns on 1st Embodiment. It is a figure which shows the relationship between the electric current value applied to a line pressure linear solenoid, a line pressure control pressure, and an actual line pressure. It is a flowchart which shows the process sequence of the discharge amount switching process by the discharge amount switching apparatus of the oil pump which concerns on 1st Embodiment. It is a figure which shows the structure of the discharge amount switching apparatus of the oil pump which concerns on 2nd Embodiment. It is a flowchart which shows the process sequence of the discharge amount switching process by the discharge amount switching apparatus of the oil pump which concerns on 2nd Embodiment. It is a figure which shows the structure of the discharge amount switching apparatus of the oil pump which concerns on 3rd Embodiment. It is a figure which shows the relationship between the duty ratio applied to a switch pressure duty solenoid, and switch hydraulic pressure (characteristic of a switch pressure duty solenoid). It is a flowchart which shows the process sequence of the discharge amount switching process by the discharge amount switching apparatus of the oil pump which concerns on 3rd Embodiment.

  DESCRIPTION OF EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. In the drawings, the same reference numerals are used for the same or corresponding parts. Moreover, in each figure, the same code | symbol is attached | subjected to the same element and the overlapping description is abbreviate | omitted.

(First embodiment)
First, the configuration of the oil pump discharge amount switching device 1 according to the first embodiment will be described with reference to FIGS. 1 and 2 together. The oil pump discharge amount switching device 1 switches and controls the flow rate of oil discharged from an oil pump 10 used in an automatic transmission or the like. Here, a case where the present invention is applied to a continuously variable transmission (CVT) 110 will be described as an example. FIG. 1 is a diagram illustrating a configuration of a continuously variable transmission 110 to which an oil pump discharge amount switching device 1 is applied. FIG. 2 is a diagram illustrating a configuration of the discharge amount switching device 1 of the oil pump.

  The continuously variable transmission 110 is connected to a crankshaft of an engine (not shown) via a torque converter (not shown), for example, and converts and outputs a driving force from the engine. The continuously variable transmission 110 has a primary shaft (input shaft) 120 connected to the output shaft of the torque converter, and a secondary shaft (output shaft) 130 disposed in parallel with the primary shaft 120.

  A primary pulley 121 is provided on the primary shaft 120. The primary pulley 121 is a fixed pulley 121a joined to the primary shaft 120, and a movable pulley (sheave) that faces the fixed pulley 121a and is slidable in the axial direction of the primary shaft 120 and is not relatively rotatable. 121b, and is configured to be able to change the cone surface interval between the pulleys 121a and 121b, that is, the pulley groove width. On the other hand, a secondary pulley 131 is provided on the secondary shaft 130. The secondary pulley 131 includes a fixed pulley 131a joined to the secondary shaft 130, and a movable pulley (sheave) that faces the fixed pulley 131a and is slidable in the axial direction of the secondary shaft 130 and is not relatively rotatable. 131b, and the pulley groove width can be changed.

  Between the primary pulley 121 and the secondary pulley 131, a chain 140 that transmits a driving force is suspended. By changing the groove widths of the primary pulley 121 and the secondary pulley 131 and changing the ratio of the winding diameter of the chain 140 to the pulleys 121 and 131 (pulley ratio), the gear ratio is changed steplessly. If the winding diameter of the chain 140 around the primary pulley 121 is Rp and the winding diameter of the secondary pulley 131 is Rs, the gear ratio i is expressed by i = Rs / Rp. Further, the shift speed is represented by di / dt.

  Here, a primary drive oil chamber (hydraulic cylinder chamber) 122 is formed in the primary pulley 121 (movable pulley 121b). On the other hand, a secondary drive oil chamber (hydraulic cylinder chamber) 132 is formed in the secondary pulley 131 (movable pulley 131b). The groove width of each of the primary pulley 121 and the secondary pulley 131 is set and changed by adjusting the primary hydraulic pressure introduced into the primary drive oil chamber 122 and the secondary hydraulic pressure introduced into the secondary drive oil chamber 132.

  The hydraulic pressure for shifting the continuously variable transmission 110, that is, the primary hydraulic pressure and the secondary hydraulic pressure described above are controlled by a valve body in which a control valve (C / V) mechanism 160 is incorporated. The control valve mechanism 160 opens and closes an oil passage formed in the control valve mechanism 160 using a plurality of spool valves and a solenoid valve (solenoid valve) that moves the spool valves, so that the hydraulic pressure discharged from the oil pump 10 is increased. (Line pressure) is adjusted and supplied to the primary drive oil chamber 122 and the secondary drive oil chamber 132 of the continuously variable transmission 110 described above. In addition, the control valve mechanism 160 also supplies a regulated hydraulic pressure (operating hydraulic pressure, lubricating hydraulic pressure, etc.) to each hydraulic mechanism 170 such as a forward / reverse switching mechanism that switches forward / backward movement of the vehicle, for example.

  Shift control of the continuously variable transmission 110 is executed by a transmission control device (hereinafter also referred to as “TCU”) 150. That is, the TCU 150 supplies the primary drive oil chamber 122 of the primary pulley 121 and the secondary drive oil chamber 132 of the secondary pulley 131 by controlling the drive of the solenoid valve (electromagnetic valve) constituting the control valve mechanism 160 described above. The transmission ratio of the continuously variable transmission 110 is changed by adjusting the hydraulic pressure.

  The oil pump 10 sucks oil (ATF) stored in the oil pan 150 through the first suction oil passage 80A and the two suction ports (the first suction port 106A and the second suction port 106B), and increases the pressure. Are discharged from two discharge ports (first discharge port 107A and second discharge port 107B). In the present embodiment, the oil pump 10 is a two-port vane pump having two discharge ports (first discharge port 107A and second discharge port 107B).

  The oil pump 10 is a so-called balanced vane pump, and includes a cam ring 101 having an inner peripheral surface having a substantially elliptical cross section, a rotor 102 disposed inside the cam ring 101 and driven by the driving force of the engine, and the rotor 102. The pump shaft 103 that is rotatably supported and a plurality of vanes 104 that are incorporated in grooves formed around the rotor 102 are configured.

  Each of the plurality of vanes 104 is movable in the radial direction of the rotor 102, and when the rotor 102 rotates, the vane 104 incorporated in the groove of the rotor 102 pops out by centrifugal force, and the tip thereof is the inner peripheral surface of the cam ring 101. Rotate along the inner surface of the cam ring 101 which is eccentric while in contact with the. At this time, the volume of the oil chamber 105 defined by the cam ring 101, the rotor 102, and the vane 104 is changed, and the suction / discharge operation is performed.

  That is, as the rotor 102 rotates, the oil sucked from the first suction port 106A through the first suction oil passage 80A is pressurized and discharged from the first discharge port 107A to the first line oil passage 70A. Similarly, the oil sucked from the second suction port 106B through the first suction oil passage 80A is pressurized and discharged from the second discharge port 107B to the second line oil passage 70B.

  As described above, the first line pressure oil passage (corresponding to the high pressure oil passage described in claims) 70A is connected to the first discharge port 107A of the oil pump 10. The second line pressure oil passage 70B is connected to the second discharge port 107B. The second line pressure oil passage 70B is configured to communicate with the first line pressure oil passage 70A via the switching control valve 60 (details will be described later). In the first line pressure oil passage 70A, a line pressure control valve (regulator) for adjusting the oil pressure (discharge pressure) of oil discharged from the oil pump 10 to the oil pressure (line pressure) required for the continuously variable transmission 110 is provided. Valve) 30 is provided.

  The line pressure control valve 30 is connected to a first control pressure oil passage 91, a first line pressure oil passage 70A, and a drain oil passage 93 for discharging oil, which communicate with a line pressure linear solenoid 20 described later. The line pressure control valve 30 accommodates a spool 31 therein so as to be slidable in the axial direction. A spring 32 is disposed at the end of the spool 31 and is pressed by a line pressure control pressure (corresponding to the control oil pressure described in the claims, details will be described later) generated by the line pressure linear solenoid 20. The spool 31 is driven in the axial direction according to the balance of the force (line pressure control pressure × pressure receiving area), the spring force (biasing force) of the spring 32, and the pressing force by the line pressure (line pressure × pressure receiving area). Thus, the amount of oil discharged from the line pressure oil passage 70A to the drain oil passage 93 is adjusted, and the line pressure is regulated.

  That is, the line pressure control valve 30 communicates the first line pressure oil passage 70A and the drain oil passage 93 with each other when the pushing force due to the actual line pressure is larger than the pushing force due to the line pressure control pressure. By discharging the oil in the pressure oil passage 70A through the drain oil passage 93, the line pressure is adjusted so that the actual line pressure and the line pressure control pressure coincide. On the other hand, when the pressing force due to the actual line pressure is smaller than the pressing force due to the line pressure control pressure, the line pressure control valve 30 cuts off the communication between the first line pressure oil passage 70A and the drain oil passage 93. Oil discharge from the one-line pressure oil passage 70A is stopped.

  The line pressure linear solenoid 20 has a linear solenoid 21 that displaces the valve in the axial direction in accordance with the current value applied from the TCU 150 based on the line pressure required for the continuously variable transmission 110. The line pressure control pressure is adjusted by adjusting the balance between the supply pressure (pilot pressure) from the pilot pressure oil passage 90 and the drain in accordance with the current applied to 21 (see FIG. 3). By supplying the regulated line pressure control pressure to the line pressure control valve 30 through the first control pressure oil passage 91, the line pressure control valve 30 is driven and controlled as described above. Here, as shown in FIG. 3, as the current value applied to the line pressure linear solenoid 20 increases, the line pressure control pressure (see the broken line) increases linearly, and accordingly, the actual line pressure (see the solid line). ) Also increases linearly.

  The second discharge port 107B of the oil pump 10 is communicated with the first line pressure oil passage 70A via the second line pressure oil passage 70B and the switching control valve 60. Further, the second discharge port 107B of the oil pump 10 is connected to the second line pressure oil passage 70B, the switching control valve 60, and the second suction oil passage 80B (corresponding to the low pressure oil passage described in the claims), The first suction oil passage 80A is communicated.

  The switching control valve 60 includes a pressing force by the actual line pressure (actual oil pressure) of the first line pressure oil passage 70A, a pressing force by the line pressure control pressure (control oil pressure) for adjusting the line pressure, and a switch described later. Based on the pressing force difference from the pressing force generated by the switch hydraulic pressure generated by the pressure solenoid 50, the discharge destination of the oil discharged from the second discharge port 107B is changed to the first line pressure oil passage 70A (high pressure oil passage), Switching is made between the second suction oil passage 80B (low pressure oil passage) communicating with the second suction port 106B of the oil pump. That is, the switching control valve 60 functions as the discharge state switching means described in the claims.

More specifically, the switching control valve 60 includes a first control pressure oil passage 91 communicating with the line pressure linear solenoid 20, a second control pressure oil passage (switch pressure oil passage) 92 communicating with the switch pressure solenoid 50, a first. Line pressure oil passage 70A, second line pressure oil passage 70B communicating with the second discharge port 107B, and second suction oil passage communicating with the first suction oil passage 80A (first and second suction ports 106A, 106B) It is connected to 80B. The switching control valve 60 accommodates a spool 61 therein so as to be slidable in the axial direction. A spring 62 is disposed at one end of the spool 61 and is generated by a pressing force F _PL (= actual line pressure PL × pressure receiving area A _PL ) due to the actual line pressure PL and the line pressure linear solenoid 20. Pressure F _PLCONT (= line pressure control pressure PLCONT × pressure receiving area A _PLCONT ), spring force (biasing force) F _spring (= K × X (spring collapse allowance)) of the spring 62, and switch The spool 61 is driven in the axial direction according to the balance with the pressing force F _SW (switch hydraulic pressure P _SW × pressure receiving area A _SW ) generated by the switch hydraulic pressure P _SW generated by the pressure solenoid 50, whereby the second line pressure oil is driven. The oil passage communicating with the passage 70B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B. Incidentally, the pressure receiving area _{A PL} of the actual line pressure PL of the spool 61 is set smaller than the pressure receiving area _{A PLCONT} the line pressure control pressure PLCONT.

  More specifically, the switching control valve 60 has a case where the resultant force of the pressing force due to the actual line pressure of the first line pressure oil passage 70A, the spring force, and the pressing force due to the switch hydraulic pressure is greater than the pressing force due to the line pressure control pressure. The second line pressure oil passage 70B and the second suction oil passage 80B communicate with each other, that is, the discharge destination of the oil discharged from the second discharge port 107B becomes the second suction oil passage 80B. Switch. On the other hand, when the resultant force of the pressing force by the actual line pressure of the first line pressure 70A, the spring force, and the pressing force by the switch hydraulic pressure is less than the pressing force by the line pressure control pressure, the switching control valve 60 It switches so that the oil path 70B and the 1st line pressure oil path 70A may be connected, ie, the discharge destination of the oil discharged from the 2nd discharge port 107B turns into the 1st line pressure oil path 70A.

  For this reason, the switching control valve 60 receives the second line when a switch oil pressure (for example, a switch oil pressure in which the resultant force is greater than the pressing force by the line pressure control pressure) is supplied from a switch pressure solenoid 50 described later. The oil passage (circuit) is connected so that the pressure oil passage 70B and the second suction oil passage 80B communicate with each other, that is, the discharge destination of the oil discharged from the second discharge port 107B becomes the second suction oil passage 80B. Fix (fixed in a semi-discharge state). On the other hand, the switching control valve 60, for example, when the switch hydraulic pressure is not supplied from the switch pressure solenoid 50 (when the switch hydraulic pressure is zero), as described above, the pressing force based on the actual line pressure and the pressing force based on the line pressure control pressure. The oil passage communicating with the second line pressure oil passage 70B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B in accordance with the balance between the force and the spring force.

  Based on the operating state of the continuously variable transmission 110, the switch pressure solenoid 50 communicates the discharge destination of the oil discharged from the second discharge port 107B with the suction ports 106A and 106B of the oil pump 10. A switch hydraulic pressure is generated that switches between fixing to 80B (that is, fixing to a semi-discharge state) and not fixing. The above-described pilot pressure oil passage 90 and the second control pressure oil passage (switch pressure oil passage) 92 are connected to the switch pressure solenoid 50. When the switch pressure solenoid 50 is opened, the supply pressure (pilot pressure) from the pilot pressure oil passage 90 passes through the second control pressure oil passage 92 and one of the switching control valves 60 (the spring 62 is disposed). Is supplied as switch hydraulic pressure to the end of the other side. On the other hand, when the switch pressure solenoid 50 is closed, the supply of the switch hydraulic pressure is stopped. At this time, the oil in the second control pressure oil passage 92 is drained, and the switch hydraulic pressure is made zero.

  As the switch pressure solenoid 50, for example, an on / off solenoid that opens when a voltage is applied and closes when a voltage is stopped is preferably used. The relationship between voltage application / stop and valve opening / closing may be reversed (normally open). The opening / closing of the switch pressure solenoid 50 is controlled by the TCU 150. That is, the switch pressure solenoid 50 and the TCU 150 function as switch hydraulic pressure generating means described in the claims.

  The TCU 150 includes a microprocessor that performs calculations, a ROM that stores a program for causing the microprocessor to execute each process, a RAM that stores various data such as calculation results, a backup RAM in which the stored contents are held by a battery, And an input / output I / F or the like.

  The TCU 150 is connected to various sensors including, for example, a range switch 151 that detects the selected position of the shift lever, an oil temperature sensor 152 that detects the temperature of the oil of the continuously variable transmission 110 (oil temperature), and the like. Further, the TCU 150 receives information such as an accelerator pedal opening degree and an engine speed from an ECU that comprehensively controls the engine via a CAN (Controller Area Network).

  The TCU 150 controls driving of the switch pressure solenoid 50 and the above-described line pressure linear solenoid 20 based on various information acquired from the above-described various sensors. Further, the TCU 150 automatically shifts the gear ratio steplessly according to the driving state of the vehicle (for example, the accelerator pedal opening degree and the vehicle speed) according to the shift map. The shift map is stored in the ROM in the TCU 150.

  More specifically, the TCU 150 opens the switch pressure solenoid 50 when, for example, the oil temperature (oil temperature) is lower than a predetermined temperature (for example, at a very low temperature). That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B (fixed in the half discharge state).

  Similarly, the TCU 150 opens the switch pressure solenoid 50 when the rotational speed of the oil pump 10 is equal to or higher than a predetermined rotational speed (during high rotation). That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B (fixed in the half discharge state). In addition, the rotation speed of the oil pump 10 can be calculated from the engine rotation speed, for example.

  The TCU 150 is used when the vehicle on which the continuously variable transmission 110 is mounted is traveling steadily (for example, when the change in the amount of depression of the accelerator pedal is less than a predetermined value and the gear ratio is substantially constant and does not change significantly). Then, the switch pressure solenoid 50 is opened. That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B (fixed in the half discharge state).

  In a case other than the operation state described above, the TCU 150 closes the switch pressure solenoid 50 (sets the switch hydraulic pressure to zero). Therefore, as described above, the oil passage communicating with the second line pressure oil passage 70B is in accordance with the balance between the pushing force by the actual line pressure, the pushing force by the line pressure control pressure, and the spring force. It is switched between the path 70A (full discharge state) and the second suction oil path 80B (half discharge state).

  Next, the operation of the oil pump discharge amount switching device 1 will be described with reference to FIG. FIG. 4 is a flowchart showing a processing procedure of a discharge amount switching process by the discharge amount switching device 1 (TCU 150) of the oil pump. This process is repeatedly executed in the TCU 150 every predetermined time (for example, every 10 ms).

In step S100, a determination is made as to whether or not the oil temperature of continuously variable transmission 110 is less than a predetermined temperature (for example, an extremely low temperature). Here, the oil when the temperature is lower than the predetermined temperature in step S108, the switch pressure solenoid 50 is opened ( _{"F PL + F spring + F SW} > F PLCONT " and), the discharge state of the oil pump 10 is semi-discharged The state is fixed (step S110). Thereafter, the process is temporarily exited. On the other hand, when the oil temperature is equal to or higher than the predetermined temperature, the process proceeds to step S102.

  In step S102, a determination is made as to whether or not the rotation speed of the oil pump 10 is equal to or higher than a predetermined rotation speed (high rotation). If the pump rotational speed is equal to or higher than the predetermined rotational speed, the switch pressure solenoid 50 is opened in step S108, and the discharge state of the oil pump 10 is fixed to the half discharge state (step S110). Thereafter, the process is temporarily exited. On the other hand, when the pump rotational speed is less than the predetermined rotational speed, the process proceeds to step S104.

  In step S104, it is determined whether or not the vehicle is in a steady running state (for example, whether or not the change in the amount of depression of the accelerator pedal is equal to or less than a predetermined value and the gear ratio is substantially constant and has not changed significantly). . Here, in the steady running state, the switch pressure solenoid 50 is opened in step S108, and the discharge state of the oil pump 10 is fixed to the half discharge state (step S110). Thereafter, the process is temporarily exited. On the other hand, when the vehicle is not in a steady running state, the process proceeds to step S112.

In step S112, the switch pressure solenoid 50 is closed, and the switch hydraulic pressure supplied to the switching control valve 60 becomes zero. Therefore, the force acting on the spool 61 of the switching control valve 60, i.e., a pushing force _{F PL} by real line pressure PL, the spring force and (urging _{force) F spring,} the pressing force _{F PLCONT} by real line pressure control pressure PLCONT When the balance becomes “F _PL + F _spring > F _PLCONT ” (step S114), the second line pressure oil passage 70B and the second suction oil passage 80B are communicated with each other. Therefore, the oil discharged from the second discharge port 107B passes through the second line pressure oil passage 70B, the second suction oil passage 80B, and the first suction oil passage 80A, and the first and second suction ports 106A, Return to 106B. As a result, the oil pump 10 enters a half-discharge (partial discharge) operation state in which oil is supplied from only the first discharge port 107A to the first line pressure 70A (step S110).

On the other hand, when the balance of the force acting on the spool 61 of the switching control valve 60 becomes “F _PL + F _spring <F _PLCONT ”, the second line pressure oil passage 70B and the first line pressure oil passage 70A communicate with each other. Is done. Therefore, the oil discharged from the second discharge port 107B joins and is supplied with the oil discharged from the first discharge port 107A. As a result, the oil pump 10 is switched to a full discharge state in which oil is supplied from the first discharge port 107A and the second discharge port 107B (step S116).

  As described above in detail, according to the present embodiment, the resultant force of the first line pressure oil passage 70A by the actual line pressure, the spring force, and the switch oil pressure, and the control pressure of the line pressure. The discharge destination of the oil discharged from the second discharge port 107B is between the first line pressure oil path 70A and the second suction oil path 80B in accordance with the pressing force difference with the pressing force due to the line pressure control pressure. It can be switched with. Therefore, it is possible to fix the semi-discharge state by supplying the switch hydraulic pressure according to the operating state of the continuously variable transmission 110. On the other hand, when the supply of the switch hydraulic pressure is stopped (when the switch hydraulic pressure is set to zero), the line is not fixed in the semi-discharge state, and the resultant force of the pressing force and the spring force due to the actual line pressure in the first line oil passage 70A The full discharge state and the half discharge state can be switched in accordance with the pressing force difference from the pressing force due to the pressure control pressure. Therefore, in that case, it is not necessary to perform drive control of the shift solenoid valve with a margin in consideration of component variations and control delay as in the prior art. As a result, depending on the operation state, it is possible to fix the full discharge state or the partial discharge state, while expanding the operation region in the partial discharge state, it is possible to further reduce the load of the oil pump 10, and the fuel consumption rate (Fuel consumption) can be further reduced.

  Further, according to the present embodiment, when the oil temperature (oil temperature) is lower than a predetermined temperature, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B. Therefore, for example, it is possible to fix the semi-discharge state at an extremely low temperature. Therefore, the occurrence of cavitation can be prevented, and noise (vibration) performance and reliability can be improved.

  Similarly, according to the present embodiment, when the rotation speed of the oil pump 10 is equal to or higher than a predetermined rotation speed, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B. Therefore, for example, when the rotation speed of the oil pump 10 is high, it can be fixed in a semi-discharge state. Therefore, the occurrence of cavitation can be prevented, and noise (vibration) performance and reliability can be improved.

  Further, according to the present embodiment, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B during the steady running state. Therefore, the occurrence of hydraulic pulsation due to switching between the full discharge state and the partial discharge state can be prevented, and reliability can be improved.

(Second Embodiment)
In the first embodiment described above, the discharge state of the oil pump 10 can be fixed to the semi-discharge state in accordance with the operating state of the continuously variable transmission 110, but may be configured to be fixable to the full discharge state.

  Then, next, the structure of the discharge amount switching apparatus 2 of the oil pump which concerns on 2nd Embodiment is demonstrated using FIG. FIG. 5 is a diagram illustrating a configuration of the discharge amount switching device 2 of the oil pump. In FIG. 5, the same or equivalent components as those in the first embodiment are denoted by the same reference numerals.

  This embodiment is different from the first embodiment described above in that a switching control valve 60B is used instead of the switching control valve 60. Further, the second control pressure oil passage (switch pressure oil passage) 92 is connected to the other end (the side opposite to the spring 62) of the switching control valve 60B, which is different from the first embodiment described above. Yes. Since other configurations are the same as or similar to those of the first embodiment described above, detailed description thereof is omitted here.

The switching control valve 60B includes a first control pressure oil passage 91 communicating with the line pressure linear solenoid 20, a second control pressure oil passage 92 communicating with the switch pressure solenoid 50, a first line pressure oil passage 70A, and a second discharge port 107B. Are connected to the second line pressure oil passage 70B communicating with the first suction oil passage 80B and the second suction oil passage 80B communicating with the first suction oil passage 80A (first and second suction ports 106A, 106B). The switching control valve 60B accommodates a spool 61B therein so as to be slidable in the axial direction. A spring 62 is disposed at one end of the spool 61B, and is generated by the pressing force F _PL (= actual line pressure PL × pressure receiving area A _PL ) due to the actual line pressure and the line pressure linear solenoid 20. _{Pushing force FPLCONT} (= actual line pressure control pressure PLCONT × pressure receiving area _APLCONT ), spring force (biasing force) F _spring (= K × X (spring collapse allowance)) of the spring 62, and switch The spool 61B is driven in the axial direction in accordance with the balance with the pressing force F _SW (switch hydraulic pressure P _SW × pressure receiving area A _SW ) generated by the switch hydraulic pressure P _SW generated by the pressure solenoid 50, whereby the second line pressure oil is driven. The oil passage communicating with the passage 70B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B.

  More specifically, in the switching control valve 60B, the resultant force of the pressing force due to the actual line pressure of the first line pressure oil passage 70A and the spring force is greater than the resultant force of the pressing force due to the line pressure control pressure and the pressing force due to the switch hydraulic pressure. Is larger, the second line pressure oil passage 70B and the second suction oil passage 80B communicate with each other, that is, the discharge destination of the oil discharged from the second discharge port 107B is the second suction oil passage 80B. Switch to be. On the other hand, when the resultant force of the pressing force due to the actual line pressure of the first line pressure 70A and the spring force is less than the resultant force of the pressing force due to the line pressure control pressure and the pressing force due to the switch hydraulic pressure, the switching control valve 60 It switches so that the 2 line pressure oil path 70B and the 1st line pressure oil path 70A may be connected, ie, the discharge destination of the oil discharged from the 2nd discharge port 107B becomes the 1st line pressure oil path 70A.

  Therefore, the switching control valve 60B is configured so that the resultant pressure of the switch pressure solenoid 50 from the switch hydraulic pressure (for example, the resultant force of the switch hydraulic pressure and the pressure of the line pressure control pressure is greater than the resultant force of the actual line pressure and the spring force). Is supplied so that the second line pressure oil passage 70B and the first line pressure oil passage 70A communicate with each other, that is, the oil discharged from the second discharge port 107B. The oil passage (circuit) is fixed (fixed to the full discharge state) so that the discharge destination is the first line pressure oil passage 70A. On the other hand, the switching control valve 60, for example, when the switch hydraulic pressure is not supplied from the switch pressure solenoid 50 (when the switch hydraulic pressure is zero), as described above, the pressing force based on the actual line pressure and the pressing force based on the line pressure control pressure. The oil passage communicating with the second line pressure oil passage 70B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B in accordance with the balance between the force and the spring force.

  The switch pressure solenoid 50 fixes the discharge destination of the oil discharged from the second discharge port 107B to the first line pressure oil passage 70A based on the operating state of the continuously variable transmission 110 (that is, fixed to the full discharge state). Switch oil pressure is generated to switch between whether to fix or not to fix. As described above, the pilot pressure oil passage 90 and the second control pressure oil passage (switch pressure oil passage) 92 are connected to the switch pressure solenoid 50. When the switch pressure solenoid 50 is opened, the supply pressure (pilot pressure) from the pilot pressure oil passage 90 passes through the second control pressure oil passage 92 to the other side (opposite to the spring 62) of the switching control valve 60B. It is supplied as switch hydraulic pressure to the end. On the other hand, when the switch pressure solenoid 50 is closed, the supply of the switch hydraulic pressure is stopped. At this time, the oil in the second control pressure oil passage 92 is drained, and the switch hydraulic pressure is made zero.

  As described above, the opening / closing of the switch pressure solenoid 50 is controlled by the TCU 150B. For example, the TCU 150B opens the switch pressure solenoid 50 when the shift range of the continuously variable transmission 110 is a neutral (N) range or a parking (P) range. That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line pressure oil passage 70A (fixed to the full discharge state).

  Similarly, the TCU 150B opens the switch pressure solenoid 50 when the speed change speed di / dt of the continuously variable transmission 110 is equal to or higher than a predetermined speed (or predicted to be higher than the predetermined speed). That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line pressure oil passage 70A (fixed to the full discharge state).

  In a case other than the operation state described above, the TCU 150B closes the switch pressure solenoid 50 (sets the switch hydraulic pressure to zero). Therefore, as described above, the oil passage communicating with the second line pressure oil passage 70B is in accordance with the balance between the pushing force by the actual line pressure, the pushing force by the line pressure control pressure, and the spring force. It is switched between the path 70A (full discharge state) and the second suction oil path 80B (half discharge state).

  Next, the operation of the oil pump discharge amount switching device 2 will be described with reference to FIG. FIG. 6 is a flowchart showing a processing procedure of discharge amount switching processing by the discharge amount switching device 2 (TCU150B) of the oil pump. This process is repeatedly executed at a predetermined time (for example, every 10 ms) in the TCU 150B.

In step S200, it is determined whether or not the shift range of continuously variable transmission 110 is a neutral (N) range or a parking (P) range. Here, when the shift range is a neutral range or the parking range in step S204, the switch pressure solenoid 50 is opened ( _{"F PL + F spring <F PLCONT} + F SW " and), the discharge state of the oil pump 10 Is fixed to the full discharge state (step S206). Thereafter, the process is temporarily exited. On the other hand, when the shift range is not the neutral range or the parking range, the process proceeds to step S202.

  In step S202, a determination is made as to whether or not the shift speed di / dt of the continuously variable transmission 110 is equal to or higher than a predetermined speed (or whether or not it is predicted to be higher than the predetermined speed). If the shift speed is equal to or higher than the predetermined speed, the switch pressure solenoid 50 is opened in step S204, and the discharge state of the oil pump 10 is fixed to the full discharge state (step S206). Thereafter, the process is temporarily exited. On the other hand, when the shift speed is less than the predetermined speed, the process proceeds to step S208.

In step S208, the switch pressure solenoid 50 is closed, and the switch hydraulic pressure supplied to the switching control valve 60B becomes zero. Therefore, the force acting on the spool 61B of the switching control valve 60B, i.e., the pushing force _{F PL} by real line pressure PL, the spring force and (urging _{force) F spring,} the pressing force _{F PLCONT} by real line pressure control pressure PLCONT When the balance becomes “F _PL + F _spring > F _PLCONT ” (step S210), the second line pressure oil passage 70B and the second suction oil passage 80B are communicated with each other. Therefore, the oil discharged from the second discharge port 107B passes through the second line pressure oil passage 70B, the second suction oil passage 80B, and the first suction oil passage 80A, and the first and second suction ports 106A, Return to 106B. As a result, the oil pump 10 enters a semi-discharge (partial discharge) operation state in which oil is supplied from only the first discharge port 107A to the first line pressure 70A (step S212).

On the other hand, when the balance of the forces acting on the spool 61B of the switching control valve 60B becomes “F _PL + F _spring <F _PLCONT ”, the second line pressure oil passage 70B and the first line pressure oil passage 70A communicate with each other. Is done. Therefore, the oil discharged from the second discharge port 107B joins and is supplied with the oil discharged from the first discharge port 107A. As a result, the oil pump 10 is switched to a full discharge state in which oil is supplied from the first discharge port 107A and the second discharge port 107B (step S206).

  According to the present embodiment, the resultant force of the first line pressure oil passage 70A by the actual line pressure and the spring force, the actual line pressure control pressure that is the control pressure of the line pressure, and the switch oil pressure The discharge destination of the oil discharged from the second discharge port 107B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B according to the difference in pressing force with the resultant force. Therefore, it is possible to fix the full discharge state by supplying the switch hydraulic pressure according to the operating state of the continuously variable transmission 110. On the other hand, when the supply of the switch oil pressure is stopped (when zero), the pressing force and the spring force due to the actual oil pressure (actual line pressure) of the first line oil passage 70A are not fixed to the full discharge state. It is possible to switch between the full discharge state and the half discharge state in accordance with the pressing force difference between the resultant force and the pressing force by the control hydraulic pressure (line pressure control pressure). Therefore, in that case, it is not necessary to perform drive control of the shift solenoid valve with a margin in consideration of component variations and control delay as in the prior art. As a result, depending on the operation state, it is possible to fix the full discharge state or the partial discharge state, while expanding the operation region in the partial discharge state, it is possible to further reduce the load of the oil pump 10, and the fuel consumption rate (Fuel consumption) can be further reduced.

  Further, according to the present embodiment, when the shift range is the neutral (N) range or the parking (P) range, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line oil passage 70A ( (It is fixed to the whole discharge state). Therefore, after that, when the shift range is switched to the drive (D) range or the reverse (R) range, a sufficient hydraulic flow rate can be ensured, and the responsiveness at the start can be improved.

  Similarly, according to the present embodiment, when the shift speed is equal to or higher than the predetermined speed, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line oil passage 70A (fixed to the full discharge state). The Therefore, a sufficient hydraulic flow rate can be ensured and a desired shift speed can be ensured at the time of a sudden shift that requires a large flow rate (a large amount of hydraulic flow rate).

(Third embodiment)
In the first embodiment described above, the discharge state of the oil pump 10 can be fixed to the half discharge state according to the operating state of the continuously variable transmission 110, and in the second embodiment, the discharge state can be fixed to the full discharge state. It is good also as a structure which can be fixed to both a half discharge state and a full discharge state.

  Then, next, the structure of the discharge amount switching device 3 of the oil pump according to the third embodiment will be described with reference to FIG. FIG. 7 is a diagram illustrating a configuration of the discharge amount switching device 3 of the oil pump. In FIG. 7, the same or equivalent components as those in the first embodiment are denoted by the same reference numerals.

  This embodiment is different from the first embodiment described above in that a switching control valve 60C is used instead of the switching control valve 60. Moreover, it is different from the first embodiment described above in that a switch pressure duty solenoid 51 is used instead of the switch pressure solenoid 50. Since other configurations are the same as or similar to those of the first embodiment described above, detailed description thereof is omitted here.

The switching control valve 60C includes a first control pressure oil passage 91 communicating with the line pressure linear solenoid 20, a second control pressure oil passage 92 communicating with the switch pressure solenoid 50, a first line pressure oil passage 70A, and a second discharge port 107B. Are connected to the second line pressure oil passage 70B communicating with the first suction oil passage 80B and the second suction oil passage 80B communicating with the first suction oil passage 80A (first and second suction ports 106A, 106B). The switching control valve 60C accommodates a spool 61C therein so as to be slidable in the axial direction. A spring 62 is disposed at one end of the spool 61C, and is generated by the pressing force F _PL (= actual line pressure PL × pressure receiving area A _PL ) due to the actual line pressure and the line pressure linear solenoid 20. _{Push force FPLCONT} (= line pressure control pressure PLCONT × pressure receiving area _APLCONT ), spring force (biasing force) F _spring (= K × X (spring collapse allowance)) of the spring 62, and switch pressure The spool 61C is driven in the axial direction in accordance with the balance with the pressing force F _SW (switch hydraulic pressure P _SW × pressure receiving area A _SW ) generated by the switch hydraulic pressure P _SW generated by the solenoid 50, whereby the second line pressure oil passage. The oil passage communicating with 70B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B.

  More specifically, the switching control valve 60C has a case where the resultant force of the pressing force by the actual line pressure of the first line pressure oil passage 70A, the spring force, and the pressing force by the switch hydraulic pressure is larger than the pressing force by the line pressure control pressure. The second line pressure oil passage 70B and the second suction oil passage 80B communicate with each other, that is, the discharge destination of the oil discharged from the second discharge port 107B becomes the second suction oil passage 80B. Switch. On the other hand, when the resultant force of the pressing force by the actual line pressure of the first line pressure 70A, the spring force, and the pressing force by the switch hydraulic pressure is less than the pressing force by the line pressure control pressure, the switching control valve 60C It switches so that the oil path 70B and the 1st line pressure oil path 70A may be connected, ie, the discharge destination of the oil discharged from the 2nd discharge port 107B turns into the 1st line pressure oil path 70A.

  Therefore, the switching control valve 60C is supplied when the switch pressure duty solenoid 51 supplies a switch hydraulic pressure (for example, a switch hydraulic pressure with a duty of 100% and the resultant force larger than the pressing force by the line pressure control pressure). Is configured so that the second line pressure oil passage 70B and the second suction oil passage 80B communicate with each other, that is, so that the discharge destination of the oil discharged from the second discharge port 107B becomes the second suction oil passage 80B. The path (circuit) is fixed (fixed in a semi-discharge state).

  On the other hand, when the switch hydraulic pressure is not supplied from the switch pressure duty solenoid 51 (for example, when the duty is 0% and the switch hydraulic pressure is zero), the switching control valve 60C is connected to the second line pressure oil passage 70B and the first line. The oil passage (circuit) is fixed so as to communicate with the pressure oil passage 70A, that is, so that the discharge destination of the oil discharged from the second discharge port 107B becomes the first line pressure oil passage 70A (in a full discharge state). Fixed).

  Further, the switching control valve 60C, for example, when an intermediate switch hydraulic pressure is supplied from the switch pressure duty solenoid 51 (for example, a pressure with a duty of 50%, details will be described later), as described above, The oil passage communicating with the second line pressure oil passage 70B is divided into the first line pressure oil passage 70A and the second suction oil passage 80B in accordance with the balance between the pushing force by the pressure, the pushing force by the line pressure control pressure, and the spring force. To switch between. Therefore, in this embodiment, the spring force of the spring 62C is set to be weaker than the spring force of the spring 62 of the first embodiment. For example, the spring force of the spring 62C is set to be weaker than the spring force of the spring 62, for example, by the pressing force by the switch oil pressure when the duty is set to 50%. That is, for example, when the switch hydraulic pressure when the duty is set to 50% is supplied, the total discharge state is determined according to the balance between the pressing force based on the actual line pressure, the pressing force based on the line pressure control pressure, and the spring force. It is set so that it can be switched between the semi-discharge state.

  The switch pressure duty solenoid 51 is a second suction oil that communicates the discharge destination of the oil discharged from the second discharge port 107B to the suction ports 106A and 106B of the oil pump 10 based on the operating state of the continuously variable transmission 110. A switch hydraulic pressure is generated that switches between fixing to the passage 80B (that is, fixing to the semi-discharge state), fixing to the first line pressure oil passage 70A (that is, fixing to the full discharge state), or not fixing to either. .

  The above-described pilot pressure oil passage 90 and the second control pressure oil passage 92 are connected to the switch pressure duty solenoid 51. When the switch pressure duty solenoid 51 is driven at a duty of 100%, the supply pressure (pilot pressure) from the pilot pressure oil passage 90 passes through the second control pressure oil passage 92 and one of the switching control valves 60 (the spring 62 is It is supplied as switch hydraulic pressure to the end of the side where it is disposed.

  On the other hand, when the switch pressure duty solenoid 51 is driven with a duty of 0% (that is, the drive is stopped), the supply of the switch hydraulic pressure is stopped. At this time, the oil in the second control pressure oil passage 92 is drained, and the switch hydraulic pressure is made zero.

  Further, when the switch pressure duty solenoid 51 is driven between a duty of 0% and a duty of 100% (for example, a duty of 50%), an intermediate pressure is supplied to one end of the switching control valve 60 as a switch hydraulic pressure. Is done.

As the switch pressure duty solenoid 51, for example, a duty solenoid whose valve opening amount is controlled according to the duty ratio of the applied voltage is preferably used. Here, the relationship between the duty ratio (%) of the voltage applied to the switch pressure duty solenoid 51 and the switch hydraulic pressure P _SW (MPa) (characteristics of the switch pressure duty solenoid 51) is shown in FIG. The horizontal axis in FIG. 8 is the duty ratio (%), and the vertical axis is the switch hydraulic pressure P _SW (MPa).

  As shown in FIG. 8, when the duty ratio is 0 (%), the output switch hydraulic pressure is 0 (MPa). On the other hand, when the duty ratio is 100 (%), the output switch hydraulic pressure becomes the same pressure (MPa) as the supply pressure (pilot pressure) from the pilot pressure oil passage 90. In addition, when the duty ratio is between 0 and 100 (%), the switch hydraulic pressure increases linearly in proportion to the increase in the duty ratio.

  The switch pressure duty solenoid 51 is driven by the TCU 150C. That is, the switch pressure duty solenoid 51 and the TCU 150C also function as the switch hydraulic pressure generating means described in the claims.

  More specifically, the TCU 150C sets the duty applied to the switch pressure duty solenoid 51 to 100%, for example, when the oil temperature (oil temperature) is lower than a predetermined temperature (for example, extremely low temperature). That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B (fixed in the half discharge state).

  Similarly, the TCU 150C sets the duty applied to the switch pressure duty solenoid 51 to 100% when the rotation speed of the oil pump 10 is equal to or higher than a predetermined rotation speed (at the time of high rotation). That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B (fixed in the half discharge state).

  The TCU 150C is used when the vehicle on which the continuously variable transmission 110 is mounted is running steadily (for example, when the change in the amount of depression of the accelerator pedal is less than a predetermined value and the gear ratio is substantially constant and does not change significantly). In addition, the duty applied to the switch pressure duty solenoid 51 is set to 100%. That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B (fixed in the half discharge state).

  On the other hand, for example, when the shift range of the continuously variable transmission 110 is the neutral (N) range or the parking (P) range, the TCU 150C sets the duty applied to the switch pressure duty solenoid 51 to 0%. That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line pressure oil passage 70A (fixed to the full discharge state).

  Similarly, the TCU 150C sets the duty applied to the switch pressure duty solenoid 51 to 0% when the shift speed di / dt of the continuously variable transmission 110 is equal to or higher than a predetermined speed (or when predicted to be higher than the predetermined speed). Set. That is, the switch hydraulic pressure is generated so that the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line pressure oil passage 70A (fixed to the full discharge state).

  In a case other than the above-described operating state, the TCU 150C sets the duty applied to the switch pressure duty solenoid 51 to, for example, 50% (the switch hydraulic pressure is set to an intermediate pressure). Therefore, as described above, the oil passage communicating with the second line pressure oil passage 70B is in accordance with the balance between the pushing force by the actual line pressure, the pushing force by the line pressure control pressure, and the spring force. It is switched between the path 70A (full discharge state) and the second suction oil path 80B (half discharge state).

  Next, the operation of the oil pump discharge amount switching device 3 will be described with reference to FIG. FIG. 9 is a flowchart showing a processing procedure of discharge amount switching processing by the discharge amount switching device 3 (TCU150C) of the oil pump. This process is repeatedly executed at a predetermined time (for example, every 10 ms) in the TCU 150C.

In step S300, a determination is made as to whether or not the oil temperature of continuously variable transmission 110 is less than a predetermined temperature (for example, an extremely low temperature). Here, when the oil temperature is lower than the predetermined temperature, in step S310, the duty applied to the switch pressure duty solenoid 51 is set to 100% (“F _PL + F _spring + F _SW > F _PLCONT ”), and the oil The discharge state of the pump 10 is fixed to the half discharge state (step S312). Thereafter, the process is temporarily exited. On the other hand, when the oil temperature is equal to or higher than the predetermined temperature, the process proceeds to step S302.

  In step S302, it is determined whether or not the rotation speed of the oil pump 10 is equal to or higher than a predetermined rotation speed (high rotation). If the pump rotational speed is equal to or higher than the predetermined rotational speed, the duty applied to the switch pressure duty solenoid 51 is set to 100% in step S310, and the discharge state of the oil pump 10 is fixed to the half discharge state. (Step S312). Thereafter, the process is temporarily exited. On the other hand, when the pump rotational speed is less than the predetermined rotational speed, the process proceeds to step S304.

  In step S304, it is determined whether or not the vehicle is in a steady running state (for example, whether or not the change in the amount of depression of the accelerator pedal is a predetermined value or less and the gear ratio is substantially constant and does not change significantly). Here, in the steady running state, in step S310, the duty applied to the switch pressure duty solenoid 51 is set to 100%, and the discharge state of the oil pump 10 is fixed to the half discharge state (step S312). . Thereafter, the process is temporarily exited. On the other hand, when the vehicle is not in a steady running state, the process proceeds to step S306.

In step S306, it is determined whether or not the shift range of the continuously variable transmission 110 is a neutral (N) range or a parking (P) range. If the shift range is the neutral range or the parking range, the duty applied to the switch pressure duty solenoid 51 is set to 0% (“F _PL + F _spring + F _SW <F _PLCONT ”) in step S314. ), The discharge state of the oil pump 10 is fixed to the full discharge state (step S316). Thereafter, the process is temporarily exited. On the other hand, when the shift range is not the neutral range or the parking range, the process proceeds to step S308.

  In step S308, a determination is made as to whether or not the shift speed di / dt of the continuously variable transmission 110 is equal to or higher than a predetermined speed (or whether or not it is predicted to be higher than the predetermined speed). Here, when the shift speed is equal to or higher than the predetermined speed, in step S314, the duty applied to the switch pressure duty solenoid 51 is set to 0%, and the discharge state of the oil pump 10 is fixed to the full discharge state. (Step S316). Thereafter, the process is temporarily exited. On the other hand, when the shift speed is less than the predetermined speed, the process proceeds to step S320.

In step S320, the duty applied to the switch pressure duty solenoid 51 is set to 50%, and the switch hydraulic pressure supplied to the switching control valve 60C becomes an intermediate pressure. Therefore, the force acting on the spool 61C of the switching control valve 60C, i.e., a pushing force _{F PL} by real line pressure PL, the spring force and (urging _{force) F spring,} a pushing force _{F PLCONT} by real line pressure control pressure PLCONT, in the case where the balance between the pressing force _{F SW} by the switch pressure _{P SW} is set to _{"F PL + F spring + F SW} > F PLCONT " (step S320), the second line pressure oil passage 70B and the second suction oil passage 80B Is communicated. Therefore, the oil discharged from the second discharge port 107B passes through the second line pressure oil passage 70B, the second suction oil passage 80B, and the first suction oil passage 80A, and the first and second suction ports 106A, Return to 106B. As a result, the oil pump 10 enters a half-discharge (partial discharge) operation state in which oil is supplied from only the first discharge port 107A to the first line pressure 70A (step S312).

On the other hand, when the balance of the force acting on the spool 61C of the switching control valve 60C becomes “F _PL + F _spring + F _SW <F _PLCONT ”, the second line pressure oil passage 70B and the first line pressure oil passage 70A Is communicated. Therefore, the oil discharged from the second discharge port 107B joins and is supplied with the oil discharged from the first discharge port 107A. As a result, the oil pump 10 is switched to a full discharge state in which oil is supplied from the first discharge port 107A and the second discharge port 107B (step S316).

  According to the present embodiment, the resultant force of the first line pressure oil passage 70A by the actual line pressure, the spring force, and the pushing force by the switch oil pressure, and the pushing force by the line pressure control pressure that is the control pressure of the line pressure. The discharge destination of the oil discharged from the second discharge port 107B is switched between the first line pressure oil passage 70A and the second suction oil passage 80B. That is, by adjusting the switch hydraulic pressure according to the operating state of the continuously variable automatic transmission 110 (for example, duty 0% or duty 100%), it is possible to fix the full discharge state or the partial discharge state. On the other hand, when the switch hydraulic pressure is adjusted so as not to be fixed in either the full discharge state or the partial discharge state (for example, at a duty of 50%), it is pushed by the actual hydraulic pressure (actual line pressure) of the first line oil passage 70A. The full discharge state and the partial discharge state can be switched according to the difference between the resultant force of the force, the spring force, and the pressing force of the switch oil pressure and the pressing force of the control oil pressure (line pressure control pressure). Therefore, in that case, it is not necessary to perform drive control of the shift solenoid valve with a margin in consideration of component variations and control delay as in the prior art. As a result, depending on the operation state, it is possible to fix the full discharge state or the partial discharge state, while expanding the operation region in the partial discharge state, it is possible to further reduce the load of the oil pump 10, and the fuel consumption rate (Fuel consumption) can be further reduced.

  Further, according to the present embodiment, when the oil temperature (oil temperature) is lower than a predetermined temperature, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B. Therefore, for example, it is possible to fix the semi-discharge state at an extremely low temperature. Therefore, the occurrence of cavitation can be prevented, and noise (vibration) performance and reliability can be improved.

  Similarly, according to the present embodiment, when the rotation speed of the oil pump 10 is equal to or higher than a predetermined rotation speed, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B. Therefore, for example, when the rotation speed of the oil pump 10 is high, it can be fixed in a semi-discharge state. Therefore, the occurrence of cavitation can be prevented, and noise (vibration) performance and reliability can be improved.

  Further, according to the present embodiment, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the second suction oil passage 80B during the steady running state. Therefore, the occurrence of hydraulic pulsation due to switching between the full discharge state and the partial discharge state can be prevented, and reliability can be improved.

  On the other hand, according to the present embodiment, when the shift range is the neutral (N) range or the parking (P) range, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line oil passage 70A ( (It is fixed to the whole discharge state). Therefore, after that, when the shift range is switched to the drive (D) range or the reverse (R) range, a sufficient hydraulic flow rate can be secured, and (start) response can be improved.

  Similarly, according to the present embodiment, when the shift speed is equal to or higher than the predetermined speed, the discharge destination of the oil discharged from the second discharge port 107B is fixed to the first line oil passage 70A (fixed to the full discharge state). The Therefore, a sufficient hydraulic flow rate can be ensured and a desired shift speed can be ensured at the time of a sudden shift that requires a large flow rate (a large amount of hydraulic flow rate).

  Although the embodiment of the present invention has been described above, the present invention is not limited to the above embodiment, and various modifications can be made. For example, in the above embodiment, the case where the present invention is applied to a continuously variable transmission (CVT) has been described as an example. However, the present invention is also applicable to a stepped automatic transmission (Step AT), a DCT, and the like. Can do. In the above embodiment, the present invention is applied to a chain type continuously variable transmission (CVT). However, instead of a chain type continuously variable transmission, for example, a belt type continuously variable transmission, a toroidal type It can also be applied to a continuously variable transmission or the like.

  In the above embodiment, the two-port oil pump 10 having two discharge ports 107A and 107B has been described as an example. However, instead of the two-port oil pump 10, an oil pump having three or more discharge ports. May be used. Moreover, in the said embodiment, although the vane pump was used as the oil pump 10, it can replace with a vane pump and can also use an internal gear type gear pump, a trochoid pump, etc., for example.

  The partial discharge state is not limited to the semi-discharge state, and may be an operation state in which the discharge amount (capacity) is smaller than that in the full discharge state.

  In the third embodiment, the duty solenoid is used as the switch pressure duty solenoid 51. However, for example, a linear solenoid or a stepping motor may be used instead of the duty solenoid. Further, the duty when generating an intermediate pressure that can switch the discharge state of the oil pump 10 by the pressing force by the actual line pressure and the pressing force by the line pressure control pressure is not limited to 50%.

  In the third embodiment, the duty ratio applied to the switch pressure duty solenoid 51 is changed to switch between fixing to the full discharge state, fixing to the half discharge state, or not fixing. Instead of the configuration, for example, by using a three-way valve, the switch hydraulic pressure is introduced into one end portion of the switching control valve 60, introduced into the other end portion, or not introduced. It is good also as a structure which switches between fixing to a discharge state, fixing to a semi-discharge state, or not fixing.

1, 2, 3 Oil pump discharge amount switching device 10 Oil pump 101 Cam ring 102 Rotor 103 Pump shaft 104 Vane 105 Oil chamber 106A First suction port 106B Second suction port 107A First discharge port 107B Second discharge port 20 Line pressure Linear solenoid 30 Line pressure control valve 50 Switch pressure solenoid 51 Switch pressure duty solenoid 60, 60B, 60C Switching control valve 70A First line pressure oil path 70B Second line pressure oil path 70C Third line pressure oil path 80A First suction oil Road 80B Second suction oil passage 90 Pilot pressure oil passage 91 First control pressure oil passage 92 Second control pressure oil passage 93 Drain oil passage 110 Continuously variable transmission 150, 150B, 150C TCU
151 Range switch 152 Oil temperature sensor 160 Control valve

Claims (11)

An oil pump that boosts the oil sucked from the suction port and discharges it from a plurality of discharge ports;
Based on the operating state of the automatic transmission, the discharge state of the oil pump is changed to a full discharge state where all of the plurality of discharge ports communicate with a high-pressure oil passage, or some of the plurality of discharge ports are A switch oil pressure generating means for generating a switch oil pressure for switching whether to fix or not to be fixed in a partial discharge state in communication with the high pressure oil passage and other part of the discharge ports communicating with the suction port of the oil pump; ,
The full discharge state and the partial discharge state are generated by the pressing force by the actual oil pressure of the high-pressure oil passage, the pressing force by the control oil pressure for adjusting the oil pressure, and the switch oil pressure generating unit. A discharge amount switching device for an oil pump, comprising: discharge state switching means for switching according to a difference in pressing force from a pressing force by switch hydraulic pressure.   The discharge state switching means is in the partial discharge state when a pressing force including a pressing force by the switch hydraulic pressure and a pressing force by an actual hydraulic pressure of the high pressure oil passage is larger than a pressing force by the control hydraulic pressure. If the pressing force including the pressing force by the switch hydraulic pressure and the pressing force by the actual hydraulic pressure of the high pressure oil passage is less than the pressing force by the control hydraulic pressure, the full discharge state is set. 2. The oil pump discharge amount switching device according to claim 1, wherein the oil passage is switched to the oil pump.   The discharge state switching means enters the partial discharge state when a pressing force including a pressing force due to an actual hydraulic pressure of the high-pressure oil passage is larger than a pressing force due to the switch hydraulic pressure and a pressing force due to the control hydraulic pressure. When the pressing force including the pressing force due to the actual hydraulic pressure of the high-pressure oil passage is less than the pressing force due to the switch hydraulic pressure and the pressing force due to the control hydraulic pressure, the oil pressure is changed so that the full discharge state is obtained. 2. The oil pump discharge amount switching device according to claim 1, wherein the path is switched. An oil pump having a first outlet and a second outlet for discharging the pressurized oil;
A high-pressure oil passage communicating with the first discharge port;
Based on the operation state of the automatic transmission, the discharge destination of the oil discharged from the second discharge port is fixed or not fixed to the high-pressure oil passage or the low-pressure oil passage communicating with the suction port of the oil pump Switch oil pressure generating means for generating switch oil pressure for switching between,
Based on the pressing force difference between the pressing force by the actual oil pressure of the high-pressure oil passage, the pressing force by the control oil pressure for adjusting the oil pressure, and the pressing force by the switch oil pressure generated by the switch oil pressure generating means. An oil pump discharge amount switching device comprising: a switching control valve that switches a discharge destination of oil discharged from the second discharge port between the high-pressure oil passage and the low-pressure oil passage. .   When the pressing force including the pressing force by the switch hydraulic pressure and the pressing force by the actual hydraulic pressure of the high-pressure oil passage is larger than the pressing force by the control hydraulic pressure, the switching control valve is When the oil passage is switched so as to communicate with the low pressure oil passage, and the pushing force including the pushing force by the switch oil pressure and the pushing force by the actual oil pressure of the high pressure oil passage is less than the pushing force by the control oil pressure, 5. The oil pump discharge amount switching device according to claim 4, wherein the oil passage is switched so that the second discharge port communicates with the high-pressure oil passage.   When the pressing force including the pressing force due to the actual hydraulic pressure of the high-pressure oil passage is larger than the pressing force due to the switch hydraulic pressure and the pressing force due to the control hydraulic pressure, the switching control valve has the second discharge port and the low pressure When the oil passage is switched so as to communicate with the oil passage, and the pushing force including the pushing force by the actual oil pressure of the high-pressure oil passage is less than the pushing force by the switch oil pressure and the pushing force by the control oil pressure, The oil pump discharge amount switching device according to claim 4, wherein the oil passage is switched so that the two discharge ports communicate with the high-pressure oil passage.   The switch hydraulic pressure generating means generates the switch hydraulic pressure so as to fix the discharge destination of the oil discharged from the second discharge port to the low pressure oil passage when the temperature of the oil is lower than a predetermined temperature. The discharge amount switching device for an oil pump according to claim 4 or 5, characterized in that:   The switch oil pressure generating means adjusts the switch oil pressure so that the discharge destination of the oil discharged from the second discharge port is fixed to the low pressure oil passage when the rotation speed of the oil pump is equal to or higher than a predetermined rotation speed. 6. The oil pump discharge amount switching device according to claim 4, wherein the discharge amount switching device is an oil pump.   The switch oil pressure generating means is configured to fix a discharge destination of oil discharged from the second discharge port to the low pressure oil passage when a vehicle on which the automatic transmission is mounted is traveling steadily. 6. The oil pump discharge amount switching device according to claim 4, wherein the switch hydraulic pressure is generated.   The switch oil pressure generating means is configured to fix the discharge destination of the oil discharged from the second discharge port to the high pressure oil passage when the shift range of the automatic transmission is a neutral range or a parking range. The oil pump discharge amount switching device according to claim 4 or 6, wherein the oil pressure is generated. The switch hydraulic pressure generating means adjusts the switch hydraulic pressure so as to fix a discharge destination of oil discharged from the second discharge port to the high-pressure oil passage when a shift speed of the automatic transmission is equal to or higher than a predetermined speed. The oil pump discharge amount switching device according to claim 4 or 6, wherein the oil pump discharge amount switching device is generated.

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