JP6614193B2 - Hydraulic transmission device for automatic transmission - Google Patents

Description

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

  In a hydraulic circuit for controlling friction engagement elements such as a clutch and a brake of an automatic transmission, a mechanical oil pump driven by an engine crankshaft is generally used as a hydraulic pressure supply source. The discharge amount of this type of mechanical oil pump varies depending on the engine speed.

  When a fixed displacement type mechanical oil pump is used, the oil pump needs to have a large discharge capacity so that a required discharge amount can be obtained even when the engine speed is low. In a hydraulic supply device equipped with this type of oil pump, the discharge amount of the oil pump exceeds the required amount when the engine speed is high to some extent, but excess oil discharged from the oil pump Without being supplied to the hydraulic chamber or the like, the oil pan is drained, whereby the line pressure is adjusted.

  However, in this type of hydraulic pressure supply device, oil is wasted due to the draining as described above, and the oil pump drive loss is likely to occur, which is disadvantageous in improving the fuel efficiency of the engine. Become.

  On the other hand, as disclosed in Patent Document 1 and the like, a variable displacement type mechanical oil pump may be used as a hydraulic pressure supply source for performing hydraulic control of the automatic transmission.

  In the oil pump disclosed in Patent Document 1, the amount of eccentricity of the cam ring with respect to the drive shaft changes according to the hydraulic pressure of the control chamber of the hydraulic piston that presses the cam ring, and the discharge pressure increases as the amount of eccentricity increases. It is configured. The hydraulic pressure output from the oil pump is supplied to the hydraulic circuit and fed back to the piston control chamber via a regulator valve.

  In this type of hydraulic pressure supply device, the regulator valve operates to output a feedback hydraulic pressure corresponding to the discharge pressure of the oil pump to the control chamber.

  For example, when the line pressure is controlled to a constant value, when the discharge pressure of the oil pump rises, the feedback hydraulic pressure rises accordingly, thereby reducing the amount of eccentricity of the cam ring. The discharge pressure decreases. On the contrary, when the discharge pressure of the oil pump decreases, the feedback hydraulic pressure decreases accordingly, thereby increasing the amount of eccentricity of the cam ring, thereby increasing the discharge pressure of the oil pump.

  By always performing such hydraulic pressure feedback, oil discharge is suppressed while the oil pump discharge pressure is adjusted to a constant line pressure. Therefore, compared to the case where a fixed displacement type oil pump is used, the driving loss of the oil pump is reduced, and the fuel efficiency can be improved.

JP-A-2-003780

  However, when the variable displacement type oil pump as described above is used, when the oil is low temperature and high viscosity, such as when cold, the viscous resistance acting on the cam ring increases, so that the feedback hydraulic pressure described above is increased. Regarding the discharge capacity control of the used oil pump, the responsiveness tends to be lowered. For this reason, the oil pump discharge pressure, and thus the line pressure, may be lower than the target value due to a delay in the rise timing of the oil pump discharge pressure.

  In general, when the frictional engagement element is switched for shifting the automatic transmission, the oil pressure is temporarily supplied to the engagement hydraulic chamber of the predetermined frictional engagement element, thereby temporarily reducing the line pressure. descend.

  And, when the line pressure decreases due to a decrease in the responsiveness of the discharge capacity control of the variable displacement oil pump as described above, if this timing overlaps with the timing of the shift, the line pressure decreases extremely, There is a possibility that the responsiveness and accuracy of the shift control may be adversely affected.

  Even when the shift is not being performed, if the line pressure decreases due to a decrease in the response of the discharge capacity control of the variable displacement oil pump, the accuracy of the hydraulic control is likely to decrease.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to stabilize line pressure while reducing the drive loss of an oil pump in a hydraulic pressure supply device for an automatic transmission having a variable displacement oil pump.

  In order to solve the above-described problems, a hydraulic pressure supply device for an automatic transmission according to the present invention is configured as follows.

The invention according to claim 1 of the present application is
A hydraulic supply device for an automatic transmission comprising a variable displacement oil pump that generates hydraulic pressure to be supplied to a hydraulic circuit for controlling the automatic transmission, and a regulator valve that adjusts the discharge pressure of the oil pump. And
A first line for controlling a line pressure supplied to the hydraulic circuit by changing a discharge capacity of the oil pump according to a feedback hydraulic pressure supplied from an output portion of the regulator valve to a control chamber of the oil pump. Pressure control means;
The second line pressure that controls the line pressure by adjusting the flow rate of the oil discharged from the oil pump and drained without being supplied to the hydraulic circuit with the discharge capacity of the oil pump fixed. Control means;
Detection means for detecting a predetermined state in which the line pressure is likely to decrease;
Selecting means for controlling the line pressure by any one selected from the first line pressure control means or the second line pressure control means,
The oil pump includes a first control chamber to which a feedback hydraulic pressure for reducing the discharge capacity of the oil pump is supplied, and a second control chamber to which a feedback hydraulic pressure for increasing the discharge capacity of the oil pump is supplied. Have
The first line pressure control means supplies oil to one of the first control chamber and the second control chamber and discharges oil from the other of the first control chamber and the second control chamber, The line pressure is controlled by changing the discharge capacity of the oil pump in accordance with the feedback oil pressure supplied to the second control chamber.
The second line pressure control means maintains the oil discharge state from the first control chamber and the oil supply state to the second control chamber and fixes the discharge capacity of the oil pump from the oil pump. By adjusting the flow rate of oil that is discharged and drained without being supplied to the hydraulic circuit, the line pressure is controlled,
The selection means controls the line pressure by the second line pressure control means when the predetermined state is detected.

The invention according to claim 2 of the present application is the invention according to claim 1,
The predetermined state is a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature.

The invention according to claim 3 of the present application is the invention according to claim 1,
The predetermined state is a state in which a shift is being performed.

The invention according to claim 4 of the present application is the invention according to claim 1,
The predetermined state is a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature and a gear shift is being performed.

The invention according to claim 5 of the present application is the invention according to claim 1,
The predetermined state includes a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature region, and a state in which the temperature of the oil is in the predetermined temperature region and shifting is performed. And

The invention according to claim 6 of the present application is the invention according to any one of claims 3 to 5,
The gear shift is a gear shift to a specific gear stage that requires a large oil flow rate for fastening the friction engagement element.

  In the present specification, the “specific shift stage that requires a large oil flow rate for engaging the frictional engagement element” means that the oil flow rate required for engaging the frictional engagement element during a shift is different from that of another speed change. This means a shift stage that is larger than the shift stage.

The invention according to claim 7 of the present application is the invention according to claim 1,
The predetermined state includes a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature range and a shift to an arbitrary gear stage is performed, and the temperature of the oil is in the predetermined temperature range, and And a state in which a shift to a specific shift stage that requires a large oil flow rate for fastening the frictional engagement element is performed.

  According to the first aspect of the present invention, for example, when the oil viscosity is high, the response of the discharge capacity control of the oil pump is low, or when the shift is being performed, the line pressure is likely to decrease. When the condition is detected, the line pressure is controlled by adjusting the oil drain flow rate in the state where the discharge capacity of the oil pump is fixed as in the conventional line pressure control in which a fixed displacement type oil pump is used. Thereby, the fall of the discharge amount of an oil pump can be suppressed. Therefore, at this time, it is possible to stabilize the discharge pressure of the oil pump, and thus to stabilize the line pressure, thereby improving the accuracy and responsiveness of the hydraulic control of the automatic transmission.

On the other hand, in a situation where the line pressure can be stably controlled without detecting the predetermined state, the discharge capacity of the variable displacement oil pump is changed according to the feedback hydraulic pressure, so that the discharge amount of the oil pump is reduced. Since it is adjusted appropriately, the line pressure can be controlled while suppressing waste of oil. Therefore, the drive loss of the oil pump can be reduced, and this can contribute to the improvement of the fuel consumption performance of the engine.
Further, when the line pressure control by the first line pressure control means is performed, the discharge capacity of the oil pump can be precisely controlled by controlling the hydraulic pressure of the first control chamber and the hydraulic pressure of the second control chamber. . Further, since the discharge capacity of the oil pump can be controlled by the balance between the hydraulic pressure in the first control chamber and the hydraulic pressure in the second control chamber, the urging means for counteracting or balancing the hydraulic pressure in the control chamber can be reduced or eliminated. It becomes possible. Therefore, the variable displacement oil pump can be made compact.

  According to the invention described in claim 2, when the oil temperature is low and the viscosity is high, when the response of the discharge capacity control of the oil pump to the feedback hydraulic pressure is low, the discharge capacity of the oil pump is fixed. By performing the line pressure control, it is possible to stabilize the line pressure.

  According to the third aspect of the present invention, when the line pressure is likely to decrease due to the supply of the engagement hydraulic pressure to the friction engagement element at the time of shifting, the line pressure control is performed with the discharge capacity of the oil pump fixed. Thus, it is possible to reduce the amount of decrease in the line pressure during the shift, and thereby it is possible to improve the response and accuracy of the shift control.

  According to the fourth aspect of the present invention, the line pressure control in a state in which the discharge capacity of the oil pump is fixed when the line pressure is likely to suddenly decrease due to the shift being performed with the oil temperature being low. By doing so, it is possible to reduce the amount of decrease in the line pressure when a shift is performed at a low oil temperature state, thereby improving the response and accuracy of shift control.

  According to the fifth aspect of the present invention, when the oil pressure is remarkably low and the response of the discharge capacity control of the oil pump is low, the line pressure is likely to drop regardless of whether or not there is a shift, and the oil If the line pressure is likely to suddenly drop due to the speed change when the temperature has not risen sufficiently, line pressure control is performed with the oil pump discharge capacity fixed, thereby reducing the line pressure. Can be stabilized.

  When the invention according to claim 6 is applied to the invention according to any one of claims 3 to 5, the oil pump is used when a shift to a specific gear position where the line pressure is particularly likely to decrease is performed. The line pressure can be stabilized by performing the line pressure control with the discharge capacity fixed. In addition, when shifting is not being performed and when shifting to a shift stage where the amount of decrease in line pressure is relatively small, line pressure control is performed while changing the discharge capacity of the oil pump. It becomes possible to reduce the driving loss and thus improve the fuel efficiency of the engine.

  According to the seventh aspect of the present invention, the gear shift is performed in a state where the oil temperature is extremely low, or the gear shift to the specific gear stage is performed in a state where the oil temperature is not sufficiently increased. When the line pressure is likely to suddenly drop, the line pressure is controlled with the oil pump discharge capacity fixed, so that the line pressure can be stabilized.

1 is a circuit diagram showing a hydraulic pressure supply device for an automatic transmission according to a first embodiment of the present invention. The circuit diagram similar to FIG. 1 which shows the supply-and-discharge oil state when decreasing the discharge capacity | capacitance of an oil pump by 1st line pressure control. The circuit diagram similar to FIG. 1 which shows the supply-and-discharge oil state when increasing the discharge capacity | capacitance of an oil pump by 1st line pressure control. The circuit diagram similar to FIG. 1 which shows the supply-and-discharge oil state when performing 2nd line pressure control. It is a control system figure of the oil pressure supply device of the automatic transmission concerning a 1st embodiment. It is a flowchart which shows the flow of control action of the 1st control example. It is a flowchart which shows the flow of control action of the 2nd control example. It is a flowchart which shows the flow of control operation | movement of the 3rd control example. It is a flowchart which shows the flow of control operation | movement of the 4th control example. It is a flowchart which shows the flow of control operation | movement of the 5th control example. It is a flowchart which shows the flow of control operation | movement of the 6th control example. The circuit diagram which shows the hydraulic pressure supply apparatus of the automatic transmission which concerns on 2nd Embodiment of this invention. The circuit diagram similar to FIG. 12 which shows the supply / discharge oil state when decreasing the discharge capacity | capacitance of an oil pump by 1st line pressure control. The circuit diagram similar to FIG. 12 which shows the supply / discharge oil state when increasing the discharge capacity | capacitance of an oil pump by 1st line pressure control. The circuit diagram similar to FIG. 12 which shows the oil supply / discharge oil state when performing 2nd line pressure control.

  Hereinafter, a specific configuration of a hydraulic pressure supply device for an automatic transmission according to the present invention will be described for each embodiment.

[First Embodiment]
A hydraulic pressure supply device 10 for an automatic transmission according to the first embodiment will be described with reference to FIGS.

[overall structure]
As shown in FIG. 1, a hydraulic pressure supply device 10 includes a variable displacement oil pump 20 as a hydraulic pressure supply source for generating hydraulic pressure used for controlling an automatic transmission, and a discharge pressure of the oil pump 20 as a line pressure. And a regulator valve 40 to be adjusted.

[Oil pump]
The oil pump 20 includes a housing 22 that accommodates components described below, a drive shaft 24 that is rotationally driven by, for example, an engine crankshaft (not shown), a rotor 26 that is coupled to the drive shaft 24, A cam ring 30 disposed on the radially outer side of the rotor 26 and a plurality of vanes 34 provided so as to protrude radially outward from the outer peripheral surface of the rotor 26 and accommodated in the cam ring 30 are provided.

  The housing 22 includes a suction port 22 a that takes oil into the housing 22 from the oil pan 66, and a discharge port 22 b that discharges the oil pressurized by the oil pump 20 to the outside of the housing 22.

  The drive shaft 24 is driven to rotate counterclockwise in FIG. 1 while the engine is being driven. The rotor 26 is disposed on the axis of the drive shaft 24 and is provided so as to rotate with the drive shaft 24 around the axis.

  The cam ring 30 is rotatably supported by a support shaft 31 parallel to the drive shaft 24. A spring 32 as an urging means is interposed between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22. The cam ring 30 is biased by a spring 32 so as to be always eccentric with respect to the axis of the rotor 26. That is, the urging direction of the cam ring 30 by the spring 32 is a direction in which the eccentric amount of the cam ring 30 with respect to the axis of the rotor 26 is increased. It should be noted that the spring 32 that applies the urging force to the cam ring 30 only needs to have a minimum elastic force that can secure an eccentric amount of the cam ring 30 when the engine is started.

  The plurality of vanes 34 are radially arranged as viewed from the axial direction at intervals in the circumferential direction. Each vane 34 is held by the rotor 26 in a state in which the movement in the circumferential direction is restricted, and thereby rotates around the axis of the drive shaft 24 together with the rotor 26.

  Each vane 34 is held by the rotor 26 so as to be able to advance and retreat toward the radially outer side. During the rotation of the rotor 26, the radially outer end of each vane 34 slides on the inner peripheral surface of the cam ring 30.

  During the rotation of the rotor 26, a pump chamber 35 surrounded by the outer peripheral surface of the rotor 26, the inner peripheral surface of the cam ring 30, and a pair of adjacent vanes 34 is formed. Since the cam ring 30 is eccentric with respect to the axial center of the rotor 26, the radial interval between the outer peripheral surface of the rotor 26 and the inner peripheral surface of the cam ring 30 varies depending on the circumferential position. Therefore, there is a volume difference between the plurality of pump chambers 35, and the volume of each pump chamber 35 changes according to the rotation of the rotor 26.

  While the oil pump 20 is being driven, each pump chamber 35 communicates with the suction port 22a when the volume is relatively small, and then the discharge port 22b when the volume is once increased and then decreased. Communicate with. Thereby, the oil taken into the pump chamber 35 from the suction port 22a is discharged from the discharge port 22b in a state where the pressure is increased by driving the oil pump 20.

  A feedback hydraulic pressure for controlling the discharge capacity of the oil pump 20 is supplied from the regulator valve 40 between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22. Is provided. A first control chamber 36 is disposed on the opposite side of the spring 32 across the cam ring 30, and a second control chamber 38 is disposed on the same side as the spring 32. The first control chamber 36 and the second control chamber 38 are arranged to face each other. The first control chamber 36 and the second control chamber 38 are partitioned by, for example, a resin seal member 37.

  The first control chamber 36 is supplied with feedback hydraulic pressure for reducing the discharge capacity of the oil pump 20, and the second control chamber 38 is supplied with feedback hydraulic pressure for increasing the discharge capacity of the oil pump 20. .

  The cam ring 30 is displaced toward the first control chamber 36 or the second control chamber 38 depending on the magnitude relationship between the hydraulic pressure of the first control chamber 36, the hydraulic pressure of the second control chamber 38, and the biasing force of the spring 32. . That is, the amount of eccentricity of the cam ring 30 with respect to the axis of the rotor 26 is determined by the balance between the hydraulic pressure in the first control chamber 36 and the hydraulic pressure in the second control chamber 38.

  When the cam ring 30 is displaced toward the second control chamber 38 and the amount of eccentricity is reduced, the volume difference between the pump chambers 35 is reduced, so that the discharge capacity of the oil pump 20 is reduced. On the other hand, when the cam ring 30 is displaced toward the first control chamber 36 (the biasing direction of the spring 32) and the amount of eccentricity is increased, the volume difference between the pump chambers 35 is increased, so that the oil pump 20 discharges. Capacity increases.

  Thus, the discharge capacity of the oil pump 20 is controlled according to the hydraulic pressures in the first control chamber 36 and the second control chamber 38. Further, the discharge pressure of the oil pump 20 can be adjusted by increasing or decreasing the discharge amount in accordance with the increase or decrease of the discharge capacity of the oil pump 20.

  The discharge port 22b of the oil pump 20 is connected via a main line 51 to a predetermined hydraulic circuit 2 that controls supply / discharge of oil to / from each friction engagement element (not shown) of the automatic transmission. An accumulator 61 is connected to the main line 51, thereby suppressing oil vibration in the main line 51.

  A first sub-line 52 that guides the discharge pressure of the oil pump 20 to the regulator valve 40 is connected to the main line 51 at a portion downstream of the accumulator 61 (on the hydraulic circuit 2 side). The first subline 52 is branched into a first input line 53, a first control line 54, a second input line 55, and a second control line 56 on the downstream side (regulator valve 40 side).

[Regulator valve]
The regulator valve 40 includes a spool 42 that is movable in the axial direction, and a return spring 44 that applies a biasing force to the spool 42 toward one side in the axial direction (the right side in FIG. 1).

  The regulator valve 40 includes a first control port A1, a second control port A2, a first input port B1, a second input port B2, a third input port B3, a first output port C1, a second output port C2, A first drain port D1, a second drain port D2, and a third drain port D3 are provided.

  The first control port A1 is connected to the first control line 54, the second control port A2 is connected to the second control line 56, the first input port B1 is connected to the first connection line 84 described later, and the second input port B2 is connected to the first input. The third input port B3 is connected to the line 53 and the second input line 55, respectively.

  An orifice 62 is provided in the first control line 54. As a result, oil whose flow rate is limited by the orifice 62 is supplied to the first control port A1. A hydraulic pressure corresponding to the discharge pressure (line pressure) of the oil pump 20 is input to the first control port A1. The hydraulic pressure input to the first control port A1 urges the spool 42 toward the side opposite to the elastic force of the return spring 44 (left side in FIG. 1).

  In the second control line 56, a pressure reducing valve 63, a first control valve 64, and an orifice 65 are provided. As a result, the hydraulic pressure input to the second control line 56 is reduced by the pressure reducing valve 63 and then controlled to a predetermined pressure by the first control valve 64. The oil whose hydraulic pressure is controlled by the first control valve 64 is supplied to the second control port A2 with the flow rate limited by the orifice 65. The hydraulic pressure input to the second control port A2 urges the spool 42 toward the same side as the elastic force of the return spring 44 (the right side in FIG. 1).

  As the first control valve 64, for example, an electromagnetic valve such as a linear solenoid valve is used. The hydraulic pressure input to the second control port A2 can be controlled to be a predetermined pressure corresponding to the command value of the line pressure by a control signal to the first control valve 64.

  The first output port C1 is connected to the first control chamber 36 of the oil pump 20 via a first feedback line 57 serving as a first feedback oil path. The first output port C1 selectively communicates with either the first input port B1 or the second drain port D2 according to the position of the spool 42.

  When oil is supplied to the first input port B1 in a state where the first output port C1 communicates with the first input port B1, the oil flows from the first output port C1 through the first feedback line 57 to the oil. Feedback is provided to the first control chamber 36 of the pump 20.

  The second drain port D <b> 2 is connected to the oil pan 66 through the second drain line 60. In the state where the second drain port D2 and the first output port C1 communicate with each other, the oil in the first feedback line 57 can be drained via the second drain line 60.

  The second output port C2 is connected to the second control chamber 38 of the oil pump 20 via a second feedback line 58 as a second feedback oil path. The second output port C2 selectively communicates with either the second input port B2 or the third drain port D3 according to the position of the spool 42.

  When oil is supplied to the second input port B2 in a state where the second output port C2 communicates with the second input port B2, the oil is supplied from the second output port C2 via the second feedback line 58 to the oil. This is fed back to the second control chamber 38 of the pump 20.

  The third drain port D3 is connected to the oil pan 66 via a second connection line 85 and a third drain line 86 which will be described later. In the state where the third drain port D3 and the second output port C2 communicate with each other, the oil in the second feedback line 58 can be drained via the second connection line 85 and the third drain line 86.

  The first drain port D <b> 1 is connected to the oil pan 66 through the first drain line 59. The first drain port D1 communicates with the third input port B3 in a state in which the third input port B3 is opened, thereby enabling draining via the first drain line 59.

[Switching mechanism]
The hydraulic pressure supply device 10 selectively supplies oil to the first control chamber 36 or the second control chamber 38 in accordance with the supply / discharge oil state in the first control chamber 36 and the second control chamber 38 of the oil pump 20. There is further provided a switching mechanism 68 that switches between the first state and the second state in which the oil drain state from the first control chamber 36 and the oil supply state to the second control chamber 38 are maintained.

  The switching mechanism 68 has a switching valve 70 connected to the regulator valve 40. The switching valve 70 includes a spool 72 that is movable in the axial direction, and a return spring 74 that applies a biasing force to the spool 72 toward one side (left side in FIG. 1) in the axial direction.

  The switching valve 70 includes a control port E1, an input port F1, an output port G1, a drain input port H1, a first drain output port I1, and a second drain output port I2.

  The switching mechanism 68 further includes a second subline 81 that guides the discharge pressure of the oil pump 20 to the switching valve 70. The second subline 81 is branched from the first subline 52, whereby the line pressure is input to the upstream side (oil pump 20 side) of the second subline 81. However, the second subline 81 may be branched from the main line 51. The second sub line 81 is branched into a control line 82 and an input line 83 on the downstream side (switching valve 70 side).

  The control port E 1 of the switching valve 70 is connected to the downstream side of the control line 82, and the input port F 1 is connected to the downstream side of the input line 83. The output port G1 is connected to the first input port B1 of the regulator valve 40 via the first connection line 84, and the drain input port H1 is connected to the third drain port D3 of the regulator valve 40 via the second connection line 85. It is connected. The first drain output port I1 is connected to the oil pan 66 via the third drain line 86, and the second drain output port I2 is connected to the oil pan 66 via the fourth drain line 87.

  A second control valve 88 is provided in the control line 82 of the switching mechanism 68. As the second control valve 88, for example, an electromagnetic valve such as an on / off solenoid valve is used. The second control valve 88 is opened and closed according to the control signal. As the second control valve 88, for example, a normally closed type electromagnetic valve that is closed when not energized and opened when energized is used.

  When the second control valve 88 is in the closed state, no hydraulic pressure is supplied to the control port E1, and the spool 72 of the switching valve 70 is positioned on the left side in FIG. When the second control valve 88 is opened, hydraulic pressure is input to the control port E1, so that the spool 72 of the switching valve 70 is on the side opposite to the elastic force of the return spring 74 (right side in FIG. 1). It is biased toward and is located on the right side of FIG. The axial position of the spool 72 is determined solely by the presence or absence of hydraulic pressure input to the control port E1.

  The output port G1 of the switching valve 70 is selectively communicated with either the input port F1 or the second drain output port I2 according to the position of the spool 72. In a state where the input port F1 and the output port G1 are in communication, the oil supplied from the input line 83 of the switching mechanism 68 to the input port F1 passes through the first connection line 84 from the output port G1 to the first of the regulator valve 40. Directed to input port B1. In a state where the output port G1 and the second drain output port I2 communicate with each other, draining from the first connection line 84 via the fourth drain line 87 is possible.

  The drain input port H1 of the switching valve 70 is selectively communicated with either the input port F1 or the first drain output port I1 according to the position of the spool 72. In a state where the drain input port H1 and the first drain output port I1 are in communication, draining from the second connection line 85 via the third drain line 86 is possible. In a state where the drain input port H1 and the input port F1 communicate with each other, the line pressure input to the input port F1 can be supplied to the third drain port D3 of the regulator valve 40 via the second connection line 85.

[Line pressure control]
In the switching mechanism 68, when the second control valve 88 is closed and the hydraulic pressure supply to the control port E1 of the switching valve 70 is stopped, the spool 72 is positioned on the left side of FIG. The supply / discharge oil state of 36 and the second control chamber 38 is the first state shown in FIGS. 2 and 3.

  In the first state shown in FIGS. 2 and 3, the various components of the hydraulic pressure supply device 10 function to perform first line pressure control (discharge capacity variable control). In the first line pressure control, the feedback hydraulic pressure is supplied to one of the first control chamber 36 or the second control chamber 38 and the oil is discharged from either one, whereby the discharge capacity of the oil pump 20 changes, The line pressure is controlled by adjusting the discharge amount of the oil pump 20 according to this.

  On the other hand, in the switching mechanism 68, when the second control valve 88 is opened and the hydraulic pressure is supplied to the control port E1, the spool 72 is positioned on the right side of FIG. The oil supply / discharge state of the control chamber 38 is the second state shown in FIG.

  In the second state shown in FIG. 4, the various components of the hydraulic pressure supply device 10 function to perform the second line pressure control (discharge capacity fixing control). In the second line pressure control, the oil supply state to the second control chamber 38 of the oil pump 20 and the oil discharge state from the first control chamber 36 are maintained, so that the discharge capacity of the oil pump 20 is fixed. The line pressure is controlled by adjusting the flow rate of the oil discharged from the oil pump 20 and drained without being supplied to the hydraulic circuit 2.

  As described above, the hydraulic pressure supply device 10 includes the first line pressure control means including the various components responsible for the first line pressure control and the second line pressure including the various components responsible for the second line pressure control. Control means.

[First line pressure control]
The first line pressure control performed in the hydraulic pressure supply device 10 in the first state will be described more specifically with reference to FIGS. 2 and 3.

  In the first state of the hydraulic pressure supply device 10, in the switching mechanism 68, energization to the second control valve 88 is stopped, and the hydraulic pressure supply to the control port E 1 of the switching valve 70 is shut off by the closed second control valve 88. ing. In this state, in the switching valve 70, the spool 72 is fixed at the left position in the drawing, the input port F1 communicates with the output port G1, the drain input port H1 communicates with the first drain output port I1, and the second drain. The output port I2 is closed.

  As a result, the input line 83 and the first connection line 84 are connected, so that the hydraulic pressure is input to the first input port B1 of the regulator valve 40 via the input line 83 and the first connection line 84, and the first By connecting the second connection line 85 and the third drain line 86, draining from the third drain port D <b> 3 of the regulator valve 40 via the second connection line 85 and the third drain line 86 becomes possible.

  On the other hand, in the regulator valve 40, the axial position of the spool 42 depends on the input hydraulic pressure to the first control port A1 according to the actual line pressure and the input to the second control port A2 controlled by the first control valve 64. The pressure is appropriately adjusted according to the balance between the hydraulic pressure and the elastic force of the return spring 44.

  When the line pressure is controlled to a predetermined pressure, the output of the first control valve 64 is controlled to a constant pressure. Therefore, in the regulator valve 40, since a constant hydraulic pressure is input to the second control port A2, the axial movement of the spool 42 is performed exclusively according to the hydraulic pressure input to the first control port A1. become.

  The hydraulic pressure input to the first control port A1 varies according to the variation of the discharge pressure of the oil pump 20, that is, the variation of the line pressure. Therefore, the spool 42 of the regulator valve 40 moves to the left in the figure when the line pressure increases, and moves to the right in the figure when the line pressure decreases.

  As the spool 42 moves in the axial direction, the first output port C1 of the regulator valve 40 communicates with the first input port B1 shown in FIG. 2 and with the second drain port D2 shown in FIG. The second output port C2 is appropriately switched between the state connected to the third drain port D3 shown in FIG. 2 and the state connected to the second input port B2 shown in FIG. Can be switched.

  As shown in FIG. 2, the first input port B1 communicates with the first output port C1, the second output port C2 communicates with the third drain port D3, and the second input port B2 and the second drain port D2 are closed. In this state, the oil supplied to the first input port B1 via the switching valve 70 is guided from the first output port C1 to the first control chamber 36 of the oil pump 20 via the first feedback line 57. In addition, the oil discharged from the second control chamber 38 to the second feedback line 58 is drained via the second connection line 85 and the third drain line 86.

  At this time, in the oil pump 20, the feedback hydraulic pressure is supplied to the first control chamber 36, and the oil is drained from the second control chamber 38, thereby reducing the eccentric amount of the cam ring 30 and thus the discharge capacity of the oil pump 20. .

  On the other hand, as shown in FIG. 3, the second output port C2 communicates with the second input port B2, the first output port C1 communicates with the second drain port D2, and the first input port B1 and the third drain port D3. Is closed, the oil supplied from the first input line 53 to the second input port B2 passes from the second output port C2 to the second control chamber 38 of the oil pump 20 via the second feedback line 58. While being guided, the oil discharged from the first control chamber 36 is drained via the second drain line 60.

  At this time, in the oil pump 20, the feedback hydraulic pressure is supplied to the second control chamber 38, and the oil is drained from the first control chamber 36, thereby increasing the eccentric amount of the cam ring 30 and consequently the discharge capacity of the oil pump 20. .

  In the state where the first line pressure control is performed, when an abnormal increase in line pressure occurs, the third input port B3 of the regulator valve 40 is opened and communicated with the first drain port D1. As a result, surplus oil is drained via the second input line 55 and the first drain line 59, so that the other ports (first control port A1, second control port A2, first input port B1, and It is possible to restrict the excessive oil from flowing into the second input port B2), thereby ensuring the reliability of the line pressure control by the regulator valve 40.

  As described above, when the first line pressure control is performed, the supply destination of the feedback hydraulic pressure from the regulator valve 40 is appropriately switched between the first control chamber 36 and the second control chamber 38 of the oil pump. Thus, since the discharge amount of the oil pump 20 is appropriately adjusted by appropriately changing the discharge capacity of the oil pump 20, it is possible to prevent the oil pump 20 from discharging an excessive amount of oil.

  Therefore, for example, when the oil temperature is high to some extent and the viscous resistance acting on the cam ring 30 is small, the displacement response of the cam ring 30 to the hydraulic pressure supply to the first control chamber 36 or the second control chamber 38 of the oil pump 20 is high. When sufficient responsiveness is obtained with respect to control for changing the discharge capacity of the oil pump 20, waste of oil can be suppressed by performing the first line pressure control. Thereby, the drive loss of the oil pump 20 is reduced, which can contribute to the improvement of the fuel consumption performance of the engine.

[Second line pressure control]
The second line pressure control performed in the hydraulic pressure supply device 10 in the second state will be described more specifically with reference to FIG.

  In the second state of the hydraulic pressure supply device 10, in the switching mechanism 68, the second control valve 88 is energized, and the hydraulic pressure is supplied to the control port E 1 of the switching valve 70 via the opened second control valve 88. . In this state, in the switching valve 70, the spool 72 is fixed at the right position in the figure, the input port F1 communicates with the drain input port H1, the output port G1 communicates with the second drain output port I2, and the first drain. The output port I1 is closed.

  As a result, when the input line 83 and the second connection line 85 are connected, the hydraulic pressure is input to the third drain port D3 of the regulator valve 40 via the input line 83 and the second connection line 85, and the second By connecting the 1 connection line 84 and the 4th drain line 87, the drain via the 1st connection line 84 and the 4th drain line 87 becomes possible from 1st input port B1 of the regulator valve 40.

  In the second state shown in FIG. 4, the hydraulic pressure supply to the first input port B <b> 1 of the regulator valve 40 is blocked by the switching valve 70. On the other hand, in order to supply hydraulic pressure to the first control chamber 36 of the oil pump 20, it is necessary to supply hydraulic pressure to the first input port B1.

  Therefore, in the second state, the hydraulic pressure supply to the first control chamber 36 is always restricted, and the hydraulic pressure is exclusively supplied to the second control chamber 38. Therefore, in the second state, the eccentric amount of the cam ring 30 is maximized, and the discharge capacity of the oil pump 20 is fixed to the maximum amount.

  As a result, the discharge pressure of the oil pump 20 tends to be higher than in the first state, and the input pressure to the first control port A1 tends to be higher. Therefore, in the second state, the spool 42 of the regulator valve 40 has an input pressure to the first control port A1, that is, a discharge pressure of the oil pump 20, in an axial region closer to the right side of the drawing than in the first state. The axis direction is moved accordingly.

  In the second state, the second output port C2 of the regulator valve 40 is communicated with the third drain port D3. As a result, the hydraulic pressure input from the second connection line 85 to the third drain port D3 via the switching valve 70 is output from the second output port C2 and passes through the second feedback line 58 to the oil pump 20. It is supplied to the second control chamber 38.

  In the second state, the first output port C1 of the regulator valve 40 is communicated with the first input port B1. Accordingly, the oil discharged from the first control chamber 36 of the oil pump 20 is drained via the first feedback line 57, the first connection line 84, and the fourth drain line 87.

  Further, in the second state, the third input port B3 of the regulator valve 40 is opened and is in communication with the first drain port D1, whereby draining via the first drain line 59 is performed. The opening degree of the third input port B3 varies according to the displacement of the spool 42, that is, according to the discharge pressure of the oil pump 20. Thereby, the drain flow rate via the first drain line 59 increases as the discharge pressure of the oil pump 20 increases, and decreases as the discharge pressure of the oil pump 20 decreases.

  Thus, in the second line pressure control, the line pressure is controlled by adjusting the drain flow rate via the first drain line 59 while the discharge capacity of the oil pump 20 is fixed to the maximum amount. Therefore, for example, when the oil pump 20 has a low oil temperature and the viscous resistance acting on the cam ring 30 is high, the discharge capacity of the oil pump 20 cannot be changed with good responsiveness according to the feedback hydraulic pressure. By performing the two-line pressure control, the discharge amount of the oil pump 20 can be stabilized.

  Therefore, when the responsiveness of the discharge capacity control of the oil pump 20 with respect to the feedback hydraulic pressure becomes low, such as when it is cold, the second line pressure control is performed to stabilize the discharge pressure of the oil pump 20 and consequently the line pressure. Thus, the accuracy and responsiveness of the hydraulic control of the automatic transmission can be improved.

[Control system]
As shown in FIG. 5, various controls related to the operation of the hydraulic pressure supply device 10 described above are performed by the control device 100. The control device 100 is configured with, for example, a microprocessor as a main part.

  The control device 100 includes an oil temperature sensor 101 that detects the temperature of oil supplied from the hydraulic pressure supply device 10 to the hydraulic circuit 2, a vehicle speed sensor 102 that detects the vehicle speed, and an accelerator pedal depression amount (accelerator opening). Signals from the accelerator opening sensor 103 to be detected and the range sensor 104 to detect the range of the automatic transmission selected by the driver are input.

  The oil temperature sensor 101 is disposed in the oil pan 66 of the automatic transmission, for example, and detects the temperature of the oil stored in the oil pan 66. Information on the vehicle speed detected by the vehicle speed sensor 102 and the accelerator opening detected by the accelerator opening sensor 103 is a predetermined shift in the shift control when the forward travel range (D range) is selected. It is used to determine the target gear position based on the map.

  In addition to the above sensors, a brake switch for detecting depression of the brake pedal, an engine speed sensor for detecting the engine speed, a turbine speed sensor for detecting the turbine speed of the torque converter, and starting the engine Therefore, signals from various devices such as an engine switch operated by the driver may be input to the control device 100.

  Moreover, the control apparatus 100 controls the hydraulic control unit 110 used for hydraulic control of an automatic transmission based on various input signals. In addition to the first control valve 64 and the second control valve 88 described above, the hydraulic control unit 110 includes a plurality of control valves 120 used for controlling the hydraulic pressure supply to the frictional engagement elements of the automatic transmission. The operation of each control valve 64, 88, 120 of the hydraulic control unit 110 is controlled based on a control signal input from the control device 100.

  Shift control of the automatic transmission by the control device 100 is performed according to the driving state of the vehicle. In the shift control, for example, a plurality of friction engagement elements are selectively engaged by controlling supply / exhaust of hydraulic pressure to / from the hydraulic chamber of each friction engagement element. A step is formed.

  In the present embodiment, the control device 100 controls the operation of the hydraulic pressure supply device 10 described above by controlling the first control valve 64 and the second control valve 88 based on various input signals. More specifically, the control device 100 selects one of the above-described first line pressure control (see FIGS. 2 and 3) or second line pressure control (see FIG. 4), and the selected control. According to the mode, the line pressure (see FIGS. 1 to 4) supplied from the oil pump 20 to the hydraulic circuit 2 is controlled.

  For the line pressure control by the control device 100, the sensors 101, 102, 103, and 104 detect a predetermined state in which the line pressure tends to decrease. When the predetermined state is detected, the control device 100 selects the second line pressure control and controls the line pressure.

  Hereinafter, specific examples of the line pressure control by the control device 100 will be described with reference to the flowcharts shown in FIGS. 6 to 11 are repeatedly executed while the oil pump 20 is being driven, that is, while the engine is being driven.

[First control example]
The control operation of the first control example will be described with reference to the flowchart shown in FIG.

  In the first control example, first, in step S1, it is determined whether or not the oil temperature T detected by the oil temperature sensor 101 is lower than a predetermined temperature T0.

  If the result of determination in step S1 is that the oil temperature T is lower than the predetermined temperature T0, the second line pressure control (see FIG. 4) with the second control valve 88 opened is performed (step S2), and the oil temperature T Is equal to or higher than the predetermined temperature T0, the first line pressure control (see FIGS. 2 and 3) with the second control valve 88 closed is performed (step S3).

  In both the first line pressure control and the second line pressure control, the control of the line pressure is performed by controlling the discharge pressure of the first control valve 64 as described above.

  According to the first control example, when the oil temperature T is low and the viscosity is high, for example, when the temperature is cold, the viscous resistance acting on the cam ring 30 of the oil pump 20 is large, and the response of the discharge capacity control of the oil pump 20 is high. The second line pressure control is performed in a state where the discharge capacity of the oil pump 20 is fixed, similarly to the conventional line pressure control in which a fixed displacement type oil pump is used (step S2).

  For this reason, it is possible to suppress a decrease in the discharge amount of the oil pump 20 even at a low oil temperature at which the responsiveness of the discharge capacity control of the oil pump 20 tends to be low, thereby stabilizing the discharge pressure of the oil pump 20. And, in turn, the line pressure can be stabilized.

  Further, when the oil temperature T rises to such an extent that sufficient responsiveness can be obtained with respect to the discharge capacity control of the oil pump 20, the first line in which the discharge capacity of the oil pump 20 is appropriately adjusted according to the feedback hydraulic pressure. Pressure control is performed (step S3).

  In the first line pressure control, oil drainage from the first drain line 59 is basically restricted (see FIGS. 2 and 3), so that waste of oil is suppressed, thereby driving the oil pump 20. Loss can be reduced.

  As described above, according to the first control example, by stabilizing the line pressure supplied to the hydraulic circuit 2, it is possible to improve the accuracy and responsiveness of the hydraulic control of the automatic transmission and to drive the oil pump 20. By reducing the loss, it is possible to contribute to improving the fuel efficiency of the engine.

[Second control example]
The control operation of the second control example will be described with reference to the flowchart shown in FIG.

  In the second control example, first, in step S11, it is determined whether or not a predetermined time has elapsed since the driving of the engine or the oil pump 20 was started.

  As a result of the determination in step S11, the second line pressure control (see FIG. 4) is performed until a predetermined time elapses (step S12). Thus, after the engine or the oil pump 20 is started, the discharge capacity of the oil pump 20 is fixed until the oil temperature T rises to such an extent that sufficient response can be obtained with respect to the discharge capacity control of the oil pump 20. By selecting the first line pressure control (see FIGS. 2 and 3), the line pressure can be stabilized.

  As a result of the determination in step S11, when a predetermined time has elapsed, the process proceeds to step S13, in which it is determined whether or not the automatic transmission is being shifted.

  If the result of determination in step S13 is that a shift is being performed, the second line pressure control (see FIG. 4) with a fixed discharge capacity is performed (step S14), and if the shift is not being performed, the feedback hydraulic pressure The first line pressure control (see FIGS. 2 and 3) is performed to change the discharge capacity in accordance with (step S15).

  According to the second control example, when the line pressure temporarily decreases due to the change of the frictional engagement element performed for shifting, the discharge capacity of the oil pump 20 is fixed (step S14). It can be avoided that the timing at which the line pressure decreases due to the decrease in the response of the discharge capacity control overlaps with the timing at which the line pressure decreases due to the shift.

  For this reason, it is possible to suppress the line pressure from being extremely reduced at the time of shifting, thereby improving the responsiveness and accuracy of the shifting control.

  Further, when no speed change is being performed, the first line pressure control in which the discharge capacity of the oil pump 20 is appropriately adjusted according to the feedback hydraulic pressure is performed (step S15), so that waste of oil is suppressed. As a result, the drive loss of the oil pump 20 can be reduced.

  As described above, according to the second control example, it is possible to improve both the accuracy and responsiveness of the shift control of the automatic transmission and the improvement of the fuel consumption performance of the engine.

[Third control example]
The control operation of the third control example will be described with reference to the flowchart shown in FIG.

  In the third control example, first, in step S21, it is determined whether or not a predetermined time has elapsed since the driving of the engine or the oil pump 20 was started.

  As a result of the determination in step S21, the second line pressure control (see FIG. 4) is performed until a predetermined time elapses (step S22). Thus, after the engine or the oil pump 20 is started, the discharge capacity of the oil pump 20 is fixed until the oil temperature T rises to such an extent that sufficient response can be obtained with respect to the discharge capacity control of the oil pump 20. By selecting the first line pressure control (see FIGS. 2 and 3), the line pressure can be stabilized.

  As a result of the determination in step S21, when a predetermined time has elapsed, the process proceeds to step S23, in which it is determined whether or not a shift to a specific shift stage is being performed.

  The specific shift speed here means one or a plurality of shift speeds that require a large oil flow rate for fastening the frictional engagement element. In other words, the oil flow rate when the engagement hydraulic pressure for forming the specific shift stage is supplied to the friction engagement element is larger than the oil flow rate when the engagement hydraulic pressure for forming the other shift stage is supplied to the friction engagement element. Is also big. Therefore, when shifting to a specific shift stage, the flow rate of oil supplied to the hydraulic circuit 2 is likely to decrease and the line pressure is more likely to decrease than when shifting to another shift stage.

  Note that the oil flow rate when the engagement hydraulic pressure is supplied to the friction engagement element is, for example, the difference between the volume of the hydraulic chamber at the start of the shift and the volume of the hydraulic chamber at the completion of the shift, and presses the friction plate of the friction engagement element. It depends on the pressure receiving area of the piston.

  If the result of determination in step S23 is that a shift to a specific shift stage is being performed, second line pressure control (see FIG. 4) with a fixed discharge capacity is performed (step S24), and the shift to the specific shift stage is performed. If not, the first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity in accordance with the feedback hydraulic pressure is performed (step S25).

  According to the third control example, since the discharge capacity of the oil pump 20 is fixed when the line pressure is particularly likely to decrease due to the shift to the specific gear position (step S24), the response of the discharge capacity control of the oil pump 20 It is possible to avoid overlapping of the timing at which the line pressure is reduced due to the decrease in performance and the timing at which the line pressure is reduced due to the shift to the specific gear.

  For this reason, it is possible to prevent the line pressure from being extremely lowered during the shift to the specific shift stage, thereby improving the responsiveness and accuracy of the shift control during the shift to the specific shift stage.

  Further, the first line pressure in which the discharge capacity of the oil pump 20 is appropriately adjusted according to the feedback hydraulic pressure when no shift is being performed and when shifting to a shift stage where the amount of decrease in the line pressure may be relatively small. By performing the control (step S25), waste of oil is suppressed, and thereby the driving loss of the oil pump 20 can be reduced.

[Fourth control example]
The control operation of the fourth control example will be described with reference to the flowchart shown in FIG.

  In the fourth control example, first, in step S31, it is determined whether or not the oil temperature T detected by the oil temperature sensor 101 is lower than a predetermined temperature T0.

  As a result of the determination in step S31, if the oil temperature T is lower than the predetermined temperature T0, the process proceeds to step S32. If the oil temperature T becomes equal to or higher than the predetermined temperature T0, the discharge capacity of the oil pump 20 is changed according to the feedback hydraulic pressure. First line pressure control (see FIGS. 2 and 3) is performed (step S34).

  In step S32, it is determined whether or not the automatic transmission is shifting. As a result of the determination in step S32, when the shift is being performed, the second line pressure control (see FIG. 4) with the discharge capacity of the oil pump 20 fixed is performed (step S33), and the shift is not being performed. The first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity in accordance with the feedback hydraulic pressure is performed (step S34).

  According to the fourth control example, in a situation where the line pressure is particularly likely to be lowered by performing a shift in a state where the responsiveness of the discharge capacity control of the oil pump 20 is lowered due to the low oil temperature, Since the discharge capacity of the pump 20 is fixed (step S33), the timing at which the line pressure decreases due to a decrease in the responsiveness of the discharge capacity control of the oil pump 20 overlaps with the timing at which the line pressure decreases due to shifting. Can be avoided.

  For this reason, it is possible to suppress the line pressure from being extremely reduced during a shift in a low oil temperature state, thereby improving the responsiveness and accuracy of the shift control.

  Further, when the oil temperature is relatively high and when the gear shift is not performed, the first line pressure control is performed in which the discharge capacity of the oil pump 20 is appropriately adjusted according to the feedback hydraulic pressure (step S34). ), Waste of oil is suppressed, and the driving loss of the oil pump 20 can be reduced.

  Note that, in step S32 of the fourth control example shown in FIG. 9, it may be determined whether or not a shift to the specific gear stage is being performed, as in step S23 of the third control example shown in FIG. . In this case, the second line pressure control in which the discharge capacity of the oil pump 20 is fixed is performed at the time of shifting to the specific shift speed, thereby suppressing the line pressure from being extremely reduced. It is possible to improve the responsiveness and accuracy of the shift control at the time of shifting to.

[Fifth control example]
The control operation of the fifth control example will be described with reference to the flowchart shown in FIG.

  In the fifth control example, first, in step S41, it is determined whether or not the oil temperature T detected by the oil temperature sensor 101 is lower than a predetermined first temperature T1.

  If the result of determination in step S41 is that the oil temperature T is lower than the first temperature T1, second line pressure control (see FIG. 4) with the discharge capacity of the oil pump 20 fixed is performed (step S44). Thereby, even at the time of low oil temperature where the responsiveness of the discharge capacity control of the oil pump 20 tends to be low, it is possible to suppress the discharge amount of the oil pump 20 from being lowered. It is possible to stabilize the line pressure.

  On the other hand, as a result of the determination in step S41, if the oil temperature T is equal to or higher than the first temperature T1, it is determined in step S42 whether the oil temperature T is lower than the second temperature T2 that is higher than the first temperature T1. Is done.

  If the oil temperature T is equal to or higher than the second temperature T2 as a result of the determination in step S42, the first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity of the oil pump 20 according to the feedback hydraulic pressure is performed. (Step S45).

  On the other hand, as a result of the determination in step S42, if the oil temperature T is in the temperature region that is equal to or higher than the first temperature T1 and lower than the second temperature T2, it is determined in step S43 whether or not the automatic transmission is being shifted. Is done.

  As a result of the determination in step S43, when the shift is being performed, the second line pressure control (see FIG. 4) with the discharge capacity of the oil pump 20 fixed is performed (step S44), and the shift is not being performed. The first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity in accordance with the feedback hydraulic pressure is performed (step S45).

  According to the fifth control example, when the oil temperature T is lower than the first temperature T1, the response of the discharge capacity control of the oil pump 20 is particularly low, and the line pressure is likely to decrease regardless of whether or not there is a shift. In addition, when the gear shift is performed in a temperature range where the oil temperature T is not completely increased (a temperature range that is equal to or higher than the first temperature T1 and lower than the second temperature T2), the line pressure is suddenly increased. In a situation where the reduction is likely to occur, the line pressure is controlled while the discharge capacity of the oil pump 20 is fixed (step S44), so that the line pressure can be stabilized.

  Further, in a high oil temperature state where the oil temperature T is equal to or higher than the second temperature T2 and in a state where no shift is performed, the first line in which the discharge capacity of the oil pump 20 is appropriately adjusted according to the feedback hydraulic pressure. By performing the pressure control (step S45), waste of oil is suppressed, and thereby the driving loss of the oil pump 20 can be reduced.

  Note that, in step S43 of the fifth control example shown in FIG. 10, it may be determined whether or not a shift to the specific gear is being performed, as in step S23 of the third control example shown in FIG. . In this case, when the shift to the specific gear stage is performed in a state where the oil temperature is in a relatively low temperature region (a temperature region that is equal to or higher than the first temperature T1 and lower than the second temperature T2), the discharge capacity of the oil pump 20 is reduced. By performing the fixed second line pressure control, it is possible to suppress the line pressure from being extremely lowered, and thereby it is possible to improve the responsiveness and accuracy of the shift control at the time of shifting to the specific shift stage. .

[Sixth control example]
The control operation of the sixth control example will be described with reference to the flowchart shown in FIG.

  In the sixth control example, first, in step S51, it is determined whether or not the oil temperature T detected by the oil temperature sensor 101 is lower than a predetermined first temperature T1.

  If the result of determination in step S51 is that the oil temperature T is less than the first temperature T1, it is determined in step S52 whether or not the automatic transmission is being shifted. If the result of determination in step S52 is that a shift is being performed, the second line pressure control (see FIG. 4) with a fixed discharge capacity of the oil pump 20 is performed (step S55), and the shift is not being performed. The first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity of the oil pump 20 according to the feedback hydraulic pressure is performed (step S56).

  On the other hand, as a result of the determination in step S51, if the oil temperature T is equal to or higher than the first temperature T1, it is determined in step S53 whether the oil temperature T is lower than the second temperature T2 that is higher than the first temperature T1. Is done.

  As a result of the determination in step S53, if the oil temperature T is equal to or higher than the second temperature T2, the first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity of the oil pump 20 according to the feedback hydraulic pressure is performed. (Step S56).

  On the other hand, as a result of the determination in step S53, if the oil temperature T is in the temperature region that is equal to or higher than the first temperature T1 and lower than the second temperature T2, it is determined in step S54 whether or not a shift to the specific gear is being performed. Determined.

  If the result of determination in step S54 is that a shift to a specific shift stage is being performed, second line pressure control (see FIG. 4) with the discharge capacity of the oil pump 20 fixed is performed (step S55), and the shift is performed. When not being performed and when shifting to a gear other than the specific gear is being performed, the first line pressure control (see FIGS. 2 and 3) for changing the discharge capacity in accordance with the feedback hydraulic pressure is performed. Performed (step S56).

  According to the sixth control example, since the oil temperature T is lower than the first temperature T1, the shift to any gear stage is performed in a state where the response of the discharge capacity control of the oil pump 20 is particularly low. Identified in a situation where the line pressure is likely to suddenly drop, and in a state where the temperature T of the oil is not completely increased (a temperature range above the first temperature T1 and below the second temperature T2). In a situation where the line pressure is likely to suddenly decrease due to the shift to the gear position, the line pressure is controlled while the discharge capacity of the oil pump 20 is fixed (step S55). Stabilization can be achieved.

  In addition, a high oil temperature state in which the oil temperature T is equal to or higher than the second temperature T2, a state in which no gear shift is performed, and the oil temperature T is lower than the second temperature T2, but the gear shift to a specific gear stage is performed. In a state where it is not performed, the first line pressure control in which the discharge capacity of the oil pump 20 is appropriately adjusted according to the feedback hydraulic pressure is performed (step S56), so that waste of oil is suppressed, whereby the oil pump The drive loss of 20 can be reduced.

[Second Embodiment]
A hydraulic pressure supply device 210 for an automatic transmission according to a second embodiment will be described with reference to FIGS. In addition, in 2nd Embodiment, while abbreviate | omitting description about the structure which is common in 1st Embodiment, the same code | symbol is attached | subjected in FIGS.

[overall structure]
As shown in FIG. 12, the hydraulic pressure supply device 210 includes a variable displacement oil pump 220 as a hydraulic pressure supply source that generates hydraulic pressure used for control of the automatic transmission, and a discharge pressure of the oil pump 220 as a line pressure. And a regulator valve 240 to be adjusted.

[Oil pump]
The oil pump 220 includes a housing 22, a drive shaft 24, a rotor 26, a cam ring 30, a plurality of vanes 34, and a plurality of pump chambers 35 similar to the oil pump 20 (see FIG. 1) of the first embodiment. Further, a spring 232 as an urging means is interposed between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22. The cam ring 30 is biased by the spring 232 so as to be always eccentric with respect to the axis of the rotor 26.

  Between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22, a control chamber 236 to which hydraulic pressure for controlling the discharge capacity of the oil pump 220 is supplied is provided. Unlike the first embodiment, the oil pump 220 of the second embodiment is provided with only one control chamber 236. The control chamber 236 is disposed on the opposite side of the spring 232 with the cam ring 30 interposed therebetween.

  A counter chamber 238 that faces the control chamber 236 is provided between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22. The spring 232 is disposed in the facing chamber 238. The control chamber 236 and the facing chamber 238 are partitioned by, for example, a resin seal member 237. The counter chamber 238 is connected to an oil drain passage 258 for draining oil that has flowed into the counter chamber 238.

  When the hydraulic pressure supplied to the control chamber 236 is increased, the cam ring 30 is displaced toward the facing chamber 238 against the urging force of the spring 232, whereby the eccentric amount of the cam ring 30 with respect to the axis of the rotor 26 is increased. Decrease.

  On the other hand, when the hydraulic pressure supplied to the control chamber 236 is reduced, the cam ring 30 is displaced in the urging direction of the spring 232, thereby increasing the amount of eccentricity of the cam ring 30 with respect to the axis of the rotor 26.

  When the amount of eccentricity of the cam ring 30 increases, the volume difference between the pump chambers 35 increases, and thereby the discharge capacity of the oil pump 220 increases. Conversely, when the eccentric amount of the cam ring 30 is reduced, the volume difference between the pump chambers 35 is reduced, so that the discharge capacity of the oil pump 220 is reduced.

  As described above, the control chamber of the oil pump 220 of the second embodiment is only the control chamber 236 to which the feedback hydraulic pressure for reducing the discharge capacity is supplied, and the discharge capacity is increased by increasing the hydraulic pressure of the control chamber 236. Decreases, and the hydraulic pressure in the control chamber 236 decreases, so that the discharge capacity increases. Therefore, it is possible to control the discharge capacity of the oil pump 220 only by controlling the hydraulic pressure in one control chamber 236, thereby improving the responsiveness related to the control of the discharge capacity and simplifying the oil path configuration. Can be achieved.

  As in the first embodiment, the discharge port 22b of the oil pump 220 is a predetermined hydraulic circuit 2 that controls the supply and discharge of oil to and from each friction engagement element (not shown) of the automatic transmission via the main line 51. The main line 51 is connected to a subline 252 that guides the discharge pressure of the oil pump 220 to the regulator valve 240.

  Similarly to the first subline 52 of the first embodiment, the subline 252 is on the downstream side (regulator valve 240 side) of the first input line 53, the first control line 54, the second input line 55, and the second control line. Branches to 56.

[Regulator valve]
The regulator valve 240 includes a spool 242 that is movable in the axial direction and a return spring 244 that applies a biasing force to the spool 242 toward one side in the axial direction (the right side in FIG. 12).

  The regulator valve 240 includes a first control port A1, a second control port A2, a feedback input port B1, a drain input port B3, an output port C1, a first drain port D1, and a second drain port D2. Yes.

  In the regulator valve 240 of the second embodiment, the first control port A1, the second control port A2, the feedback input port B1, the drain input port B3, the output port C1, the first drain port D1, and the second drain port D2 are , The first control port A1, the second control port A2, the first input port B1, the third input port B3, the first output port C1, the first drain in the regulator valve 40 (see FIG. 1) of the first embodiment, respectively. It is a port corresponding to the port D1 and the second drain port D2.

  The regulator valve 240 is not provided with ports corresponding to the second input port B2, the second output port C2, and the third drain port D3 (see FIG. 1) of the first embodiment. Thereby, compared with 1st Embodiment, while the number of ports is reduced, the spool 242 is made compact in the length direction. Therefore, compared with 1st Embodiment, the responsiveness regarding the sliding of the spool 242 can be improved.

  As in the first embodiment, the first control port A1 is connected to the first control line 54, the second control port A2 is connected to the second control line 56, and the drain input port B3 is connected to the second input line 55. Yes. Similarly to the first embodiment, the first drain port D1 is connected to the oil pan 66 via the first drain line 59, and the second drain port D2 is connected to the oil pan 66 via the second drain line 60, respectively.

  A hydraulic pressure corresponding to the discharge pressure (line pressure) of the oil pump 220 is input to the first control port A1. The hydraulic pressure input to the first control port A1 biases the spool 242 toward the side opposite to the elastic force of the return spring 244 (left side in FIG. 12). The first control port A1 is supplied with oil whose flow rate is limited by the orifice 62.

  The second control line 56 is provided with a pressure reducing valve 63, a first control valve 64, and an orifice 65 similar to those in the first embodiment. The hydraulic pressure controlled by the first control valve 64 according to the command value of the line pressure is input to the second control port A2. The hydraulic pressure input to the second control port A2 urges the spool 242 toward the same side as the elastic force of the return spring 244 (the right side in FIG. 12). Note that oil whose flow rate is limited by the orifice 65 is supplied to the second control port A2.

  The output port C <b> 1 is connected to the control chamber 236 of the oil pump 220 via a feedback line 257 as a feedback oil path that guides feedback hydraulic pressure to the control chamber 236. The output port C1 selectively communicates with either the feedback input port B1 or the second drain port D2 according to the position of the spool 242.

  The feedback input port B 1 is connected to the first input line 53. Further, unlike the first embodiment, the first input line 53 is provided with a second control valve 270 as an opening / closing means for opening and closing the feedback line 257.

  As the second control valve 270, for example, an electromagnetic valve such as an on / off solenoid valve is used. The second control valve 270 is opened and closed according to the control signal. As the second control valve 270, for example, a normally open type electromagnetic valve that is opened when not energized and closed when energized is used.

  When oil is supplied from the first input line 53 to the first input port B1 in a state where the output port C1 communicates with the feedback input port B1 and the second control valve 270 is opened, the oil is output to the output port C1. C1 is fed back to the control chamber 236 of the oil pump 220 via the feedback line 257.

  On the other hand, when the output port C1 communicates with the second drain port D2, the oil in the feedback line 257 can be drained via the second drain line 60.

  The first drain port D1 communicates with the drain input port B3 in a state in which the drain input port B3 is opened, thereby enabling draining via the first drain line 59.

  In the regulator valve 240, the axial position of the spool 242 depends on the input hydraulic pressure to the first control port A 1 according to the actual line pressure, the input hydraulic pressure to the second control port A 2 controlled by the first control valve 64, and It is appropriately adjusted according to the balance with the elastic force of the return spring 244.

  The hydraulic pressure input to the first control port A1 varies according to the variation of the discharge pressure of the oil pump 220, that is, the variation of the line pressure. Therefore, the spool 242 of the regulator valve 240 moves to the left in the figure when the line pressure increases, and moves to the right in the figure when the line pressure decreases.

[Line pressure control]
In the state where the second control valve 270 is opened, the supply / discharge oil state of the control chamber 236 of the oil pump 220 is the first state shown in FIGS. 13 and 14. In the first state, the various components of the hydraulic pressure supply device 210 function to perform first line pressure control (discharge capacity variable control).

  As shown in FIGS. 13 and 14, in the first line pressure control, the discharge capacity of the oil pump 220 is changed by supplying and discharging hydraulic pressure to and from the control chamber 236 of the oil pump 220, and the oil pressure is changed accordingly. The line pressure is controlled by adjusting the discharge amount of the pump 220.

  On the other hand, in the state where the second control valve 270 is closed, the supply / discharge oil state of the control chamber 236 of the oil pump 220 is the second state shown in FIG. In the second state, the various components of the hydraulic pressure supply device 210 function to perform second line pressure control (discharge capacity fixing control).

  As shown in FIG. 15, in the second line pressure control, the oil supply to the control chamber 236 of the oil pump 220 is restricted, so that the discharge capacity of the oil pump 220 is fixed and the oil pump 220 is discharged. The line pressure is controlled by adjusting the flow rate of the oil drained without being supplied to the hydraulic circuit 2.

  As described above, the hydraulic pressure supply device 210 includes the first line pressure control means including the various components responsible for the first line pressure control and the second line pressure including the various components responsible for the second line pressure control. Control means. The second control valve 270 functions as a switching mechanism that switches the supply / discharge oil state of the control chamber 236 between the first state and the second state.

[First line pressure control]
The first line pressure control in the second embodiment will be described more specifically with reference to FIGS. 13 and 14.

  When the first line pressure control is performed, the output port C1 of the regulator valve 240 communicates with the feedback input port B1 shown in FIG. 13 according to the axial movement of the spool 242 and shown in FIG. It is appropriately switched between a state communicating with the second drain port D2.

  As shown in FIG. 13, when the feedback input port B1 communicates with the output port C1 and the second drain port D2 is closed, the oil supplied to the feedback input port B1 is fed from the output port C1 to the feedback line. It is guided to the control chamber 236 of the oil pump 220 via 257. As a result, when the feedback hydraulic pressure is supplied to the control chamber 236, the amount of eccentricity of the cam ring 30 and hence the discharge capacity of the oil pump 220 are reduced.

  On the other hand, as shown in FIG. 14, when the feedback input port B1 is closed, the hydraulic pressure supply from the feedback input port B1 to the feedback line 257, and hence the hydraulic pressure supply to the control chamber 236 is stopped. As a result, the hydraulic pressure in the control chamber 236 decreases, so that the eccentric amount of the cam ring 30 and thus the discharge capacity of the oil pump 220 increase.

  At this time, since the output port C1 is in communication with the second drain port D2, the oil discharged from the control chamber 236 to the feedback line 257 is drained via the feedback line 257 and the second drain line 60. Is done. Thereby, smooth oil draining from the control chamber 236 is promoted.

  When the line pressure is abnormally increased while the first line pressure control is being performed, the drain input port B3 of the regulator valve 240 is opened and communicated with the first drain port D1. As a result, surplus oil is drained via the second input line 55 and the first drain line 59, so that the other ports (first control port A1, second control port A2, and feedback input port B1). Therefore, the reliability of the line pressure control by the regulator valve 240 is ensured.

  As described above, when the first line pressure control is performed, the discharge capacity of the oil pump 220 is appropriately set by changing the feedback hydraulic pressure supplied to the control chamber 236 according to the discharge pressure of the oil pump 220. By changing, the discharge amount of the oil pump 220 is adjusted as appropriate, so that it is possible to prevent the oil pump 220 from discharging an excessive amount of oil.

  Therefore, for example, when the oil temperature is high to some extent and the viscous resistance acting on the cam ring 30 is small, the cam ring 30 has a high displacement response to the hydraulic pressure supply to the control chamber 236, and the control for changing the discharge capacity of the oil pump 220 is performed. When sufficient responsiveness is obtained, waste of oil can be suppressed by performing the first line pressure control. Thereby, the drive loss of the oil pump 220 is reduced, which can contribute to the improvement of the fuel efficiency performance of the engine.

[Second line pressure control]
The second line pressure control in the second embodiment will be described more specifically with reference to FIG.

  When the second line pressure control is performed, the hydraulic pressure supply to the feedback input port B1 of the regulator valve 240 is blocked by the second control valve 270, and the hydraulic pressure supply to the control chamber 236 is always regulated. . Therefore, the eccentric amount of the cam ring 30 is maximized, and the discharge capacity of the oil pump 220 is fixed to the maximum amount.

  As a result, the discharge pressure of the oil pump 220 tends to be higher than when the first line pressure control is being performed, and the input pressure to the first control port A1 tends to be higher. Therefore, in the second state shown in FIG. 15, the spool 242 of the regulator valve 240 is connected to the first control port A1 in the axial direction region closer to the right side of the drawing than in the first state shown in FIGS. The axial movement is performed according to the input pressure, that is, the discharge pressure of the oil pump 220.

  In the second state, the drain input port B3 of the regulator valve 240 is opened and communicated with the first drain port D1, whereby draining via the first drain line 59 is performed. The opening degree of the drain input port B3 varies according to the displacement of the spool 242, that is, according to the discharge pressure of the oil pump 220. As a result, the drain flow rate via the first drain line 59 increases as the discharge pressure of the oil pump 220 increases, and decreases as the discharge pressure of the oil pump 220 decreases.

  Thus, in the second line pressure control, the line pressure is controlled by adjusting the drain flow rate via the first drain line 59 while the discharge capacity of the oil pump 220 is fixed to the maximum amount. Therefore, when the discharge capacity of the oil pump 220 cannot be changed with good responsiveness according to the feedback hydraulic pressure, for example, when the oil temperature is low and the viscous resistance acting on the cam ring 30 is high during cold, By performing the two-line pressure control, the discharge amount of the oil pump 220 can be stabilized.

  Therefore, when the responsiveness of the discharge capacity control of the oil pump 220 to the feedback hydraulic pressure becomes low, such as when it is cold, the second line pressure control is performed to stabilize the discharge pressure of the oil pump 220, and thus stabilize the line pressure. Thus, the accuracy and responsiveness of the hydraulic control of the automatic transmission can be improved.

  The operation of the hydraulic pressure supply device 210 according to the second embodiment described above is similarly controlled by the control device 100 described in the first embodiment. In this control, instead of the second control valve 88 of the first embodiment, the opening / closing operation of the second control valve 270 of the second embodiment is controlled, so that the first line pressure control, the second line pressure control, The line pressure is controlled while appropriately selecting between the two. Thereby, also in 2nd Embodiment, the effect similar to 1st Embodiment is acquired.

  While the present invention has been described with reference to the above-described embodiments, the present invention is not limited to the above-described embodiments.

  For example, in the second embodiment described above, the opening / closing means for opening and closing the feedback line 257 may be configured by combining a spool valve and a control valve for controlling the spool position of the spool valve. In this case, it becomes easy to secure the flow rate of the oil supplied to the feedback input port B1.

  In the first and second embodiments described above, the present invention has been described by taking a hydraulic pressure supply device including a vane type variable displacement oil pump as an example. However, in the present invention, the types of variable displacement oil pumps are described. The specific configuration is not particularly limited as long as the discharge capacity is changed according to the hydraulic pressure supplied to the control chamber of the oil pump.

  As described above, according to the present invention, in a hydraulic pressure supply device for an automatic transmission equipped with a variable displacement oil pump, it is possible to stabilize the line pressure while reducing the drive loss of the oil pump. Therefore, there is a possibility of being suitably used in the manufacturing industry field of an automatic transmission provided with this type of hydraulic pressure supply device and in the manufacturing industry field of a vehicle equipped with the automatic transmission.

2 Hydraulic circuit 10 Hydraulic supply device 20 Variable displacement oil pump 30 Cam ring 36 First control chamber 38 Second control chamber 40 Regulator valve 51 Main line 52 First subline 57 First feedback line 58 Second feedback line 59 First drain Line 64 First control valve 68 Switching mechanism 70 Switching valve 81 Second sub line 84 First connection line 85 Second connection line 88 Second control valve 100 Control device (selection means)
DESCRIPTION OF SYMBOLS 101 Oil temperature sensor 102 Vehicle speed sensor 103 Accelerator opening sensor 104 Range sensor 210 Hydraulic supply device 220 Variable capacity type oil pump 236 Control chamber 240 Regulator valve 252 Subline 257 Feedback line 270 Second control valve

Claims (7)

A hydraulic supply device for an automatic transmission comprising a variable displacement oil pump that generates hydraulic pressure to be supplied to a hydraulic circuit for controlling the automatic transmission, and a regulator valve that adjusts the discharge pressure of the oil pump. And
A first line for controlling a line pressure supplied to the hydraulic circuit by changing a discharge capacity of the oil pump according to a feedback hydraulic pressure supplied from an output portion of the regulator valve to a control chamber of the oil pump. Pressure control means;
The second line pressure that controls the line pressure by adjusting the flow rate of the oil discharged from the oil pump and drained without being supplied to the hydraulic circuit with the discharge capacity of the oil pump fixed. Control means;
Detection means for detecting a predetermined state in which the line pressure is likely to decrease;
Selecting means for controlling the line pressure by any one selected from the first line pressure control means or the second line pressure control means,
The oil pump includes a first control chamber to which a feedback hydraulic pressure for reducing the discharge capacity of the oil pump is supplied, and a second control chamber to which a feedback hydraulic pressure for increasing the discharge capacity of the oil pump is supplied. Have
The first line pressure control means supplies oil to one of the first control chamber and the second control chamber and discharges oil from the other of the first control chamber and the second control chamber, The line pressure is controlled by changing the discharge capacity of the oil pump in accordance with the feedback oil pressure supplied to the second control chamber.
The second line pressure control means maintains the oil discharge state from the first control chamber and the oil supply state to the second control chamber and fixes the discharge capacity of the oil pump from the oil pump. By adjusting the flow rate of oil that is discharged and drained without being supplied to the hydraulic circuit, the line pressure is controlled,
The automatic pressure supply apparatus for an automatic transmission, wherein the selection means controls the line pressure by the second line pressure control means when the predetermined state is detected.   2. The hydraulic pressure supply device for an automatic transmission according to claim 1, wherein the predetermined state is a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature.   2. The hydraulic pressure supply device for an automatic transmission according to claim 1, wherein the predetermined state is a state in which a shift is being performed.   2. The hydraulic pressure supply for an automatic transmission according to claim 1, wherein the predetermined state is a state in which a temperature of oil used for controlling the line pressure is lower than a predetermined temperature and a gear shift is being performed. apparatus.   The predetermined state includes a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature region, and a state in which the temperature of the oil is in the predetermined temperature region and shifting is performed. The hydraulic pressure supply device for an automatic transmission according to claim 1.   The automatic transmission according to any one of claims 3 to 5, wherein the shift is a shift to a specific shift stage that requires a large oil flow rate to fasten the frictional engagement element. Hydraulic supply device.   The predetermined state includes a state in which the temperature of oil used for controlling the line pressure is lower than a predetermined temperature range and a shift to an arbitrary gear stage is performed, and the temperature of the oil is in the predetermined temperature range, and 2. The hydraulic pressure supply device for an automatic transmission according to claim 1, further comprising: a state in which a shift to a specific gear stage that requires a large oil flow rate for fastening the frictional engagement element is performed.

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