WO2018163767A1

WO2018163767A1 - Hydraulic pressure suppky device for automatic transmission

Info

Publication number: WO2018163767A1
Application number: PCT/JP2018/005663
Authority: WO
Inventors: 弘一松浦; 竜洋南; 昌宏鍛冶; 貴士石山
Original assignee: マツダ株式会社
Priority date: 2017-03-10
Filing date: 2018-02-19
Publication date: 2018-09-13
Also published as: JP2018150974A

Abstract

This hydraulic pressure supply device (10) for an automatic transmission comprises: a variable displacement oil pump (20); a regulator valve (40) for regulating the discharge pressure of the oil pump to a predetermined pressure; and a feedback oil passage (57) for conducting hydraulic pressure outputted from the regulator valve (output port C1) to the control chamber (36) of the oil pump. The oil pump is configured such that an increase in hydraulic pressure in the control chamber causes a decrease in the discharge pressure and such that a decrease in hydraulic pressure in the control chamber causes an increase in the discharge pressure. The hydraulic pressure supply device (10) further comprises an oil supply limiting device (80) provided in the feedback oil passage and limiting oil supply to the control chamber more than oil discharge from the control chamber.

Description

Hydraulic transmission device for automatic transmission

The present invention relates to a hydraulic pressure supply device for an automatic transmission.

As disclosed in

Patent Documents

1 and 2, a variable displacement oil pump is used as a hydraulic supply source of a hydraulic circuit for controlling frictional engagement elements (clutch, brake, etc.) of an automatic transmission mounted on a vehicle. May be used. The discharge pressure of the oil pump is the original pressure of oil supplied to each part of the automatic transmission as line pressure.

An oil pump disclosed in

Patent Documents

1 and 2 includes a drive shaft that is rotationally driven, a rotor that is coupled to the drive shaft, a cam ring that is disposed radially outside the rotor, and an inner peripheral surface of the cam ring. And a plurality of vanes which are provided so as to be capable of advancing and retreating in the radial direction with respect to the rotor and defining a pump chamber. The cam ring is pressed by a piston inserted into the cylinder so that the amount of eccentricity of the cam ring with respect to the drive shaft (rotor) changes. That is, the amount of eccentricity changes according to the hydraulic pressure of the control chamber in the cylinder, and the larger the amount of eccentricity, the higher the discharge pressure of the oil pump. Oil discharged from the oil pump is supplied to a hydraulic circuit. The oil is also supplied to the control chamber in the cylinder via a regulator valve. That is, the hydraulic pressure output from the output portion of the regulator valve is fed back to the control chamber. In some cases, the cam ring is disposed in the housing, and a control chamber in which hydraulic pressure is fed back from the regulator valve is formed between the housing and the cam ring.

In such a hydraulic pressure supply device, the regulator valve transmits the feedback hydraulic pressure (feedback hydraulic pressure) according to the discharge pressure of the oil pump, the control chamber of the oil pump (the control chamber in the cylinder, the housing and the cam ring). Including the control room between). In this way, the regulator valve adjusts the discharge pressure of the oil pump to a predetermined pressure.

For example, when the line pressure is controlled to a preset target value (for example, a constant value), when the discharge pressure of the oil pump rises, the feedback hydraulic pressure rises accordingly, and the cam ring is eccentric. The amount decreases. Thereby, the discharge pressure of the oil pump decreases. When the discharge pressure of the oil pump is decreased, the feedback hydraulic pressure is decreased, so that the eccentric amount of the cam ring is increased. As a result, the discharge pressure of the oil pump increases. By always performing such hydraulic pressure feedback, the discharge pressure (line pressure) of the oil pump is adjusted to a predetermined pressure (the target value).

Japanese Utility Model Publication No. 1-141954 JP-A-2-003780

By the way, in the above-described hydraulic pressure supply device, when the frictional engagement element is switched for shifting of the automatic transmission, oil is supplied to the engagement hydraulic chamber of one or more frictional engagement elements to be engaged at the time of the shift. Supplied. By supplying this oil, the line pressure temporarily decreases from the target value during the supply. Thus, even if the line pressure decreases, the line pressure increases due to the feedback of the hydraulic pressure, and returns to the target value.

However, if it takes time to increase the line pressure due to the feedback, it takes time to completely fasten the frictional engagement element to be fastened, which causes an increase in shift time and slipping of the frictional engagement element. End up. In order to suppress such an increase in shift time and slipping of the frictional engagement element, it is required to improve the responsiveness related to the increase in line pressure.

In addition, the target value of the line pressure itself may be increased and changed depending on the output of the engine, etc. In this case, in order to perform highly accurate hydraulic control so that the line pressure becomes the target value, High responsiveness is required to raise the actual line pressure to the target value.

However, in the line pressure control, if the responsiveness of the line pressure increase is increased, the line pressure becomes unstable due to overshoot or hunting, and the shift control accuracy of the automatic transmission decreases. It becomes easy.

The present invention has been made in view of such a point, and an object of the present invention is to improve the response of a rise in line pressure in a hydraulic pressure supply device for an automatic transmission having a variable displacement oil pump. And the stabilization of the line pressure.

In order to achieve the above object, according to the present invention, a variable displacement oil pump for generating hydraulic pressure used for controlling the automatic transmission, and a discharge of the oil pump, for a hydraulic pressure supply device for an automatic transmission, are provided. A regulator valve that adjusts the pressure to a predetermined pressure; and a feedback oil passage that guides the hydraulic pressure output from the output portion of the regulator valve to the control chamber of the oil pump. The oil pump increases the hydraulic pressure in the control chamber. The discharge pressure is reduced, and the discharge pressure is increased by lowering the hydraulic pressure in the control chamber, and is provided in the feedback oil passage to discharge oil from the control chamber. Compared with the control room, the oil supply restriction device for restricting the oil supply is further provided.

With the above configuration, when the oil pressure in the control chamber of the oil pump is reduced and the discharge pressure (line pressure) of the oil pump is increased toward a predetermined pressure, oil drainage from the control chamber is almost limited. Can be done. Thereby, high responsiveness can be obtained with respect to an increase in line pressure. As a result, the shift time of the automatic transmission can be shortened and the slip of the frictional engagement element can be suppressed, and highly accurate hydraulic control is performed so that the line pressure becomes the predetermined pressure (desired line pressure). Can do.

Also, after the line pressure has risen too much and exceeded the predetermined pressure, the oil pressure in the control chamber of the oil pump is increased to decrease the line pressure toward the predetermined pressure. At this time, the oil supply restriction device restricts the oil supply to the control chamber, so that the line pressure is gradually reduced. As a result, hunting of the line pressure is suppressed and the line pressure can be stabilized at an early stage, thereby realizing highly accurate shift control.

In an embodiment of the hydraulic pressure supply device for the automatic transmission, the feedback oil passage includes a first oil passage portion and a second oil passage portion connected in parallel to each other, and the oil supply restriction device includes the first oil passage portion. An orifice provided in one oil passage and a check valve provided in the second oil passage and restricting the passage of oil in a direction from the output portion toward the control chamber.

Thus, when the oil pressure in the control chamber of the oil pump is increased to reduce the line pressure, the orifice provided in the first oil passage portion of the feedback oil passage and the check valve provided in the second oil passage portion As a result, the supply of oil to the control chamber is limited, so that the line pressure can be gradually reduced.

On the other hand, when the oil pressure in the control chamber of the oil pump is lowered to increase the line pressure, the check valve in the second oil passage is opened, so that oil can be quickly discharged from the control chamber.

Therefore, while realizing the oil supply restriction device with a simple configuration, it is possible to achieve both improvement in response to increase in line pressure and stabilization of the line pressure.

When the oil supply restriction device has the orifice and the check valve, oil is supplied from the feedback oil path to the output side of the orifice and the check valve in the feedback oil path through a throttle. A drain oil passage for draining may be connected.

As a result, when the oil pressure in the control chamber of the oil pump is decreased to increase the line pressure, the oil discharged from the control chamber is drained through the drain oil passage, thereby facilitating smooth drainage. Thus, it is possible to further improve the response of the increase in line pressure.

Further, when the oil pressure in the control chamber of the oil pump is increased to reduce the line pressure, the excess oil flowing through the feedback oil passage from the output portion of the regulator valve toward the control chamber is drained through the drain oil passage. Thus, it is possible to reduce the influence of the output fluctuation of the regulator valve on the hydraulic pressure of the control chamber. In addition, since excessive oil drainage is suppressed by the throttle, it is possible to prevent the oil supply to the control chamber from being significantly delayed or insufficient.

In the case where the oil supply restriction device has the orifice and the check valve, the regulator valve discharges oil discharged from the control chamber to the feedback oil passage in a state where output of hydraulic pressure from the output unit is stopped. It may be configured to have a drain port that drains and regulates the drain of oil in the feedback oil passage when the hydraulic pressure is output from the output unit.

With this configuration, when the oil pressure in the control chamber of the oil pump is decreased to increase the line pressure, the oil discharged from the control chamber to the feedback oil passage is drained from the drain port of the regulator valve, thereby allowing smooth discharge. Oil is promoted, and the response of the increase in line pressure can be further improved.

Also, when the oil pressure in the control chamber of the oil pump is increased to reduce the line pressure, the drain of the oil in the feedback oil passage from the drain port is restricted, so that the control is performed via the feedback oil passage. Waste of oil supplied to the chamber can be suppressed. As a result, it is possible to reduce the amount of oil supplied from the oil pump to the regulator valve, and thus reduce the discharge amount of the oil pump. Therefore, the drive loss of the automatic transmission can be reduced, and the fuel efficiency performance of the vehicle equipped with the automatic transmission can be improved.

In another embodiment of the oil pressure supply device for the automatic transmission, the oil supply restriction device is a relief valve provided in the feedback oil passage, and is closed when oil pressure is output from the output portion of the regulator valve, In a state where the output of hydraulic pressure from the output unit is stopped, the relief valve is opened, and the oil discharged from the control chamber to the feedback oil passage is provided in the feedback oil passage, and the relief valve opened is provided. A drain oil passage for draining is connected, and the oil supply restriction device further includes an orifice provided on the output portion side of a connection portion with the drain oil passage in the feedback oil passage.

As a result, when the oil pressure in the control chamber of the oil pump is increased to lower the line pressure, the relief valve is closed and the oil supply to the control chamber is limited by the orifice provided in the feedback oil passage. Thus, the line pressure can be gradually reduced.

On the other hand, when the line pressure is increased by lowering the oil pressure in the control chamber of the oil pump, the relief valve is opened, so that the drained oil from the control chamber is drained quickly, and this increases the line pressure. Responsiveness can be obtained. In addition, it is possible to achieve both the promotion of oil drainage and the limitation of oil supply without providing a plurality of oil passage portions connected in parallel to the feedback oil passage, thereby simplifying the configuration of the feedback oil passage. Can be achieved.

As described above, according to the hydraulic pressure supply device for an automatic transmission according to the present invention, the feedback oil passage is provided with the oil supply restriction device for restricting the oil supply to the control chamber as compared with the oil discharged from the control chamber of the oil pump. By doing so, it is possible to achieve both improvement in responsiveness of increase in line pressure and stabilization of the line pressure.

It is a circuit diagram which shows the hydraulic pressure supply apparatus of the automatic transmission which concerns on 1st Embodiment. FIG. 2 is a view corresponding to FIG. 1 showing a state in which oil is discharged from the control chamber of the oil pump in the first embodiment. FIG. 2 is a view corresponding to FIG. 1 illustrating a state in which oil supply to the control chamber of the oil pump is performed in the first embodiment. It is a circuit diagram which shows a part of hydraulic pressure supply apparatus which concerns on a 1st comparative example. It is a figure which shows a part of hydraulic pressure supply apparatus which concerns on a 2nd comparative example. It is a graph which shows transition of the line pressure at the time of gear shifting of the automatic transmission in the 1st comparative example. It is a graph which shows transition of the line pressure at the time of the speed change of the automatic transmission in the 2nd comparative example. It is a graph which shows transition of the line pressure at the time of the speed change of the automatic transmission in the said 1st Embodiment. It is a graph which shows transition of the line pressure at the time of the target value rise in the 1st comparative example. It is a graph which shows transition of the line pressure at the time of target value rise in the 2nd comparative example. It is a graph which shows transition of the line pressure at the time of the target value rise in the said 1st Embodiment. It is a figure which shows an example of the specific structure of the oil supply restriction | limiting apparatus in the said 1st Embodiment, Comprising: The state in which oil supply to the control chamber of an oil pump is performed is shown. 9A shows a state in which oil is discharged into the control chamber of the oil pump in the oil supply restriction device of FIG. 9A. It is a circuit diagram which shows the hydraulic pressure supply apparatus of the automatic transmission which concerns on 2nd Embodiment. FIG. 11 is a view corresponding to FIG. 10 illustrating a state in which oil is discharged from the control chamber of the oil pump in the second embodiment. FIG. 11 is a view corresponding to FIG. 10 illustrating a state in which oil supply to the control chamber of the oil pump is performed in the second embodiment. It is a circuit diagram which shows the hydraulic pressure supply apparatus of the automatic transmission which concerns on 3rd Embodiment. FIG. 14 is a view corresponding to FIG. 13 showing a state where oil is discharged from the control chamber of the oil pump in the third embodiment. FIG. 14 is a view corresponding to FIG. 13 illustrating a state in which oil supply to the control chamber of the oil pump is performed in the third embodiment.

Hereinafter, exemplary embodiments will be described in detail with reference to the drawings.

(First embodiment)
FIG. 1 shows a hydraulic pressure supply device 10 for an automatic transmission according to a first embodiment. The automatic transmission and hydraulic pressure supply device 10 is mounted on a vehicle.

The hydraulic pressure supply device 10 includes a variable displacement oil pump 20 as a hydraulic pressure supply source that generates hydraulic pressure used for controlling the automatic transmission, and a regulator valve 40 that adjusts the discharge pressure of the oil pump 20 to a predetermined pressure. It has. The discharge pressure of the oil pump 20 becomes the original pressure of oil supplied to each part of the automatic transmission as a line pressure.

The oil pump 20 is disposed on the outer side in the radial direction of the rotor 26, a housing 22 having a ring-shaped cross section that accommodates components described below, a drive shaft 24 that is rotationally driven, a rotor 26 that is coupled to the drive shaft 24, and 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 to contact the inner peripheral surface of the cam ring 30.

The housing 22 has a suction port 22a for sucking oil into the housing 22 from the oil pan 70, and a discharge port 22b for discharging oil boosted by the oil pump 20 to the outside of the housing 22.

In this embodiment, the drive shaft 24 is rotationally driven by a crankshaft of an engine mounted on the vehicle. 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 rotates 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 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 eccentric with respect to the axis of the rotor 26 (axis of the drive shaft 24). That is, the biasing direction of the spring 32 with respect to the cam ring 30 is a direction in which the eccentric amount of the cam ring 30 with respect to the axis of the rotor 26 is increased (leftward in FIG. 1).

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

Further, each vane 34 is held by the rotor 26 so that it can advance and retreat in the radial direction with respect to the rotor 26. Each vane 34 is configured such that the end of each vane 34 on the outer side in the radial direction of the rotor 26 slides on the inner peripheral surface of the cam ring 30 while the rotor 26 rotates.

During the rotation of the rotor 26, a plurality of pump chambers 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 are 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 position in the circumferential direction. 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 discharge port when the volume is decreased after increasing once. It communicates with 22b. Thereby, the oil sucked 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.

Between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22, a control chamber 36 to which hydraulic pressure for controlling the discharge pressure of the oil pump 20 is supplied is provided. The control chamber 36 is disposed on the opposite side of the spring 32 with the cam ring 30 interposed therebetween.

Further, an opposing chamber 38 that faces the control chamber 36 is provided between the outer peripheral surface of the cam ring 30 and the inner peripheral surface of the housing 22. A spring 32 is disposed in the facing chamber 38. The control chamber 36 and the facing chamber 38 are partitioned by, for example, a resin seal member 37. An oil drain passage 64 for draining the oil that has flowed into the counter chamber 38 is connected to the counter chamber 38.

When the hydraulic pressure supplied to the control chamber 36 increases, the cam ring 30 is displaced toward the facing chamber 38 against the urging force of the spring 32, thereby reducing the amount of eccentricity of the cam ring 30 with respect to the axis of the rotor 26. .

On the other hand, when the hydraulic pressure supplied to the control chamber 36 decreases, the cam ring 30 is displaced toward the control chamber 36 by the urging force of the spring 32, 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 pressure of the oil pump 20 increases. Conversely, when the amount of eccentricity of the cam ring 30 decreases, the volume difference between the pump chambers 35 decreases, and the discharge pressure of the oil pump 20 decreases.

As described above, the oil pump 20 is configured such that the discharge pressure of the oil pump 20 decreases as the hydraulic pressure in the control chamber 36 increases, while the discharge pressure increases as the hydraulic pressure in the control chamber 36 decreases. ing. Thereby, the discharge pressure of the oil pump 20 can be adjusted by controlling the hydraulic pressure in the control chamber 36.

The discharge port 22b of the oil pump 20 is connected via a main line 51 to a hydraulic circuit 2 that controls the supply and discharge of oil to and from the engagement hydraulic chamber of the friction engagement element of the automatic transmission. An accumulator 71 is connected to the main line 51, thereby suppressing oil vibration in the main line 51.

A subline 52 is connected to a portion of the main line 51 on the downstream side (hydraulic circuit 2 side) of the accumulator 71. This subline 52 is an oil passage that guides the discharge pressure of the oil pump 20 to the regulator valve 40.

The 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 at the downstream side (regulator valve 40 side) of the subline 52.

The regulator valve 40 includes a spool 42 that is movable in the axial direction, and a return spring 44 that biases the spool 42 toward one axial side of the spool 42 (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, an output port C1 (an output portion of the regulator valve 40), and an emergency drain port C2. .

The hydraulic pressure input to the first control port A1 presses the spool 42 toward the side opposite to the urging force of the return spring 44 (left side in FIG. 1). The hydraulic pressure input to the second control port A2 presses the spool 42 toward the same side as the urging force of the return spring 44 (the right side in FIG. 1).

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 input line 53. The second input port B2 is connected to the second input line 55.

The first control line 54 is provided with an orifice 72. Thus, oil is supplied to the first control port A1 in a state where the flow rate is limited by the orifice 72. Further, a hydraulic pressure corresponding to the discharge pressure (line pressure) of the oil pump 20 is input to the first control port A1.

The second control line 56 is provided with a pressure reducing valve 73, a hydraulic control valve 74, and an orifice 75. Accordingly, the hydraulic pressure supplied to the second control line 56 is controlled by the hydraulic control valve 74 so as to have a preset pressure after being reduced by the pressure reducing valve 73. The oil hydraulically controlled by the hydraulic control valve 74 is supplied to the second control port A2 in a state where the flow rate is limited by the orifice 75.

In the present embodiment, as the hydraulic control valve 74, an electromagnetic valve capable of controlling the output of the hydraulic control valve 74 (the hydraulic pressure input to the second control port A2) according to a control signal to the hydraulic control valve 74 is used. It is done. The hydraulic pressure (the set pressure) input to the second control port A2 is set to a value such that the line pressure becomes a preset target value (the predetermined pressure).

The axial position of the spool 42 of the regulator valve 40 is determined by the input hydraulic pressure (line pressure) to the first control port A1, the input hydraulic pressure (the set pressure) to the second control port A2, and the biasing force of the return spring 44. It depends on the balance.

The emergency drain port C 2 is connected to the oil pan 70 through the emergency drain line 62. The emergency drain port C2 communicates with the second input port B2 in a state where the second input port B2 is opened. The second input port B2 is opened when the line pressure rises abnormally. At this time, excess oil is drained via the second input port B2, the emergency drain port C2, and the emergency drain line 62, so that the first control port A1, the second control port A2, and the first input port are drained. It is possible to restrict excessive oil from flowing into B1. As a result, the reliability of the line pressure control by the regulator valve 40 is ensured.

The output port C1 is connected to the control chamber 36 of the oil pump 20 via a feedback line 57 as a feedback oil path. The output port C1 communicates with the first input port B1 when the first input port B1 is open. In the state where the output port C1 is in communication with the first input port B1, the line pressure input to the first input port B1 is output as it is from the output port C1, and the hydraulic pressure output from the output port C1 passes through the feedback line 57. Through the control chamber 36 of the oil pump 20.

The feedback line 57 is provided with an oil supply restriction device 80 that restricts oil supply to the control chamber 36 as compared with oil discharged from the control chamber 36.

Specifically, the feedback line 57 has a first oil passage 58 and a second oil passage 59 connected in parallel to each other. The oil supply restriction device 80 includes an orifice 81 provided in the first oil passage portion 58 and a check valve 82 provided in the second oil passage portion 59.

In the first oil passage section 58, the orifice 81 causes the direction from the output port C1 side to the control chamber 36 side (oil supply direction to the control chamber 36) and the direction from the control chamber 36 side to the output port C1 side (control). The oil flow rate is limited in any of the directions of oil draining from the chamber 36).

The check valve 82 is a valve that regulates the passage of oil in the direction from the output port C1 side toward the control chamber 36 (oil supply direction to the control chamber 36). By the check valve 82, the second oil passage portion 59 allows passage of oil only in the direction from the control chamber 36 side to the output port C1 side (oil drain direction from the control chamber 36).

As described above, in the feedback line 57, the oil supply to the control chamber 36 is performed by the orifice 81 of the first oil passage portion 58 and the check valve 82 of the second oil passage portion 59 compared to the oil discharged from the control chamber 36. Is limited.

A drain line 60 is connected to the portion of the feedback line 57 closer to the output port C1 than the orifice 81 and the check valve 82. The drain line 60 is connected to a portion of the feedback line 57 that is closer to the output port C 1 than the parallel portion of the first oil passage portion 58 and the second oil passage portion 59. As a result, the oil flowing through the feedback line 57 is drained via the drain line 60.

The drain line 60 is provided with an orifice 76 (throttle). The orifice 76 restricts the flow rate of oil drained through the drain line 60. As described above, the drain line 60 is a drain oil passage that drains oil from the feedback line 57 through the throttle.

In the hydraulic pressure supply device 10 configured as described above, when the line pressure is controlled to the predetermined pressure, the output of the hydraulic control valve 74 (the set pressure) 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 movement of the spool 42 in the axial direction is performed exclusively according to the hydraulic pressure input to the first control port A1. It will be.

The hydraulic pressure input to the first control port A1 varies according to the variation in the discharge pressure of the oil pump 20, that is, the variation in the line pressure. Therefore, the spool 42 of the regulator valve 40 moves to the left in FIG. 1 when the line pressure increases, and moves to the right in FIG. 1 when the line pressure decreases.

According to the axial movement of the spool 42, the first input port B1 of the regulator valve 40 is switched between the closed state shown in FIG. 2 and the open state shown in FIG. That is, the first input port B1 is closed when the line pressure decreases with respect to the predetermined pressure, and is open when the line pressure increases with respect to the predetermined pressure.

As shown in FIG. 2, when the first input port B1 is closed and is not in communication with the output port C1, the output of hydraulic pressure from the output port C1 to the feedback line 57 is stopped. As a result, oil supply to the control chamber 36 of the oil pump 20 is stopped, so that oil is discharged from the control chamber 36 to the feedback line 57.

At this time, in the first oil passage portion 58 of the feedback line 57, the oil flowing from the control chamber 36 side toward the output port C1 side passes through the orifice 81. In the second oil passage portion 59, the oil flowing from the control chamber 36 side toward the output port C1 side passes through the check valve 82 that is opened. Accordingly, a larger amount of oil flows in the second oil passage portion 59 than in the first oil passage portion 58.

The oil that has flowed through the first oil passage 58 and the second oil passage 59 in this way (oil drained from the control chamber 36) is drained via the drain line 60. Thereby, smooth oil drainage from the control chamber 36 is promoted. Therefore, the hydraulic pressure in the control chamber 36 can be quickly reduced, and the discharge pressure (line pressure) of the oil pump 20 can be quickly increased.

On the other hand, as shown in FIG. 3, when the first input port B1 is opened and communicated with the output port C1, the main port 51, the subline 52, and the first input line are connected from the discharge port 22b of the oil pump 20. The oil supplied to the first input port B 1 via 53 is led from the output port C 1 to the feedback line 57, and further led to the control chamber 36 of the oil pump 20 via the feedback line 57.

The oil flowing through the feedback line 57 from the output port C1 side toward the control chamber 36 side is restricted from passing through the second oil passage portion 59 by the check valve 82, and flows through the first oil passage portion 58 by the orifice 81. Is limited. Thereby, the oil supply to the control chamber 36 is restricted as compared with the oil drained from the control chamber. Therefore, the hydraulic pressure in the control chamber 36 can be gradually increased, and the discharge pressure (line pressure) of the oil pump 20 can be gradually decreased.

Further, at the time of refueling to the control chamber 36, the surplus portion flowing through the feedback line 57 is guided to the drain line 60 and drained. As a result, the amount of oil supplied to the control chamber 36 through the first oil passage portion 58 of the feedback line 57 can be stabilized, and as a result, the influence of the output fluctuation of the regulator valve 40 on the hydraulic pressure of the control chamber 36 can be reduced. Can be reduced.

Furthermore, when refueling the control chamber 36, the drain amount from the feedback line 57 to the drain line 60 is limited by the orifice 76, so that excessive drain is suppressed. Therefore, by supplying an appropriate amount of oil from the feedback line 57 to the control chamber 36, it is possible to prevent the oil supply to the control chamber 36 from being significantly delayed or insufficient.

Here, the effects of the first embodiment will be described in more detail while comparing with the first comparative example shown in FIG. 4A and the second comparative example shown in FIG. 4B.

As shown in FIG. 4A, the hydraulic pressure supply device according to the first comparative example is different from the above-described hydraulic pressure supply device 10 in the feedback line 57 in the parallel portion of the first oil passage portion 58 and the second oil passage portion 59 and the oil supply. The configuration is the same as that of the first embodiment except that the limiting device 80 is not provided.

As shown in FIG. 4B, the hydraulic pressure supply device according to the second comparative example also includes a parallel portion of the first oil path portion 58 and the second oil path portion 59 in the feedback line 57 and the oil supply restriction device with respect to the hydraulic pressure supply device 10. The difference is that 80 is not provided. However, in the hydraulic pressure supply device according to the second comparative example, the feedback line 57 is provided with an orifice 81 similar to the orifice 81 of the first oil passage portion 58 in the first embodiment.

The graph shown in FIG. 5A shows that in the first comparative example, the shift of the automatic transmission is performed when the vehicle travels in which the line pressure target value Po (see the alternate long and short dash line) is controlled to a predetermined pressure P1 (here, a constant value). Shows the transition of the actual line pressure P when.

The graph shown in FIG. 5B shows that in the second comparative example, the shift of the automatic transmission is performed when the vehicle travels in which the line pressure target value Po (see the alternate long and short dash line) is controlled to a predetermined pressure P1 (here, a constant value). Shows the transition of the actual line pressure P when.

In the graph shown in FIG. 6, in the first embodiment, the shift of the automatic transmission is changed when the vehicle travels in which the line pressure target value Po (see the alternate long and short dash line) is controlled to a predetermined pressure P1 (here, constant value). The transition of the actual line pressure P when performed is shown.

In FIG. 5A, FIG. 5B, and FIG. 6, it is assumed that the shift of the automatic transmission is started at time t1. As a result, the line pressure P becomes lower than the predetermined pressure P1 by supplying oil to the engagement hydraulic chambers of the one or more friction engagement elements to be engaged at the time of the gear change. Therefore, the first input port B1 of the regulator valve 40 is closed, and oil is discharged from the control chamber 36 to the feedback line 57.

As shown in FIG. 5A, in the first comparative example, when the shift of the automatic transmission is started at time t1 and the line pressure P becomes lower than the predetermined pressure P1, the feedback line is supplied from the control chamber 36 of the oil pump 20. Oil draining to 57 is promptly performed without restriction. As a result, the line pressure P increases rapidly.

The line pressure P thus rapidly increased exceeds the predetermined pressure P1, thereby opening the first input port B1 of the regulator valve 40 and supplying oil to the control chamber 36 via the feedback line 57. In the first comparative example, since the oil supply restriction device 80 is not provided in the feedback line 57, the oil supply to the control chamber 36 is also performed quickly without being restricted, as is the case of the oil drained from the control chamber 36. For this reason, the line pressure P drops rapidly and again falls below the predetermined pressure P1, and the oil is discharged from the control chamber 36 again.

Thus, in the first comparative example, hunting that repeats a rapid rise and fall of the line pressure P is likely to occur. Therefore, it takes time until the line pressure P stabilizes at the predetermined pressure P1, and during this time, the hydraulic pressure supplied to the engagement hydraulic chamber of the friction engagement element to be engaged becomes unstable, and the shift control of the automatic transmission is performed. Accuracy may be reduced.

As shown in FIG. 5B, in the second comparative example, when the shift of the automatic transmission is started and the line pressure P becomes lower than the predetermined pressure P1, oil is discharged from the control chamber 36. Oil is limited by an orifice 83 (see FIG. 4B) provided in the feedback line 57.

For this reason, in the second comparative example, it takes time for the line pressure P to rise to the predetermined pressure P1, and thus it takes time to completely fasten the frictional engagement element to be fastened. Time may increase or slip may occur due to insufficient fastening force of the frictional engagement element.

On the other hand, in the first embodiment, as shown in FIG. 6, after the line pressure P decreases due to the start of shifting (time t1), oil is discharged from the control chamber 36 in order to increase the line pressure P. In this case, the check valve 82 in the oil supply restriction device 80 is opened, and quick oil draining via the feedback line 57 and the drain line 60 is performed, so that the line pressure P quickly rises to the predetermined pressure P1.

Then, when the line pressure P exceeds the predetermined pressure P1, the oil supply to the control chamber 36 is switched. Since this oil supply is restricted by the oil supply restriction device 80, the line pressure P gradually decreases. As a result, the hunting of the line pressure P is suppressed, and the line pressure P can be quickly stabilized at the predetermined pressure P1 or a value close to the predetermined pressure P1.

As described above, in the first embodiment, the line pressure P that has decreased with the start of shifting can be quickly increased and stabilized to a desired pressure (predetermined pressure P1). The slip of the frictional engagement element to be fastened can be suppressed. Therefore, the accuracy of the shift control of the automatic transmission can be improved.

The graph of FIG. 7A shows the actual line pressure P when the line pressure target value Po is increased from a predetermined pressure P1 (hereinafter referred to as a first predetermined pressure P1) to a second predetermined pressure P2 in the first comparative example. Shows the transition.

The graph of FIG. 7B shows the transition of the actual line pressure P when the target value Po of the line pressure is increased from the first predetermined pressure P1 to the second predetermined pressure P2 in the second comparative example.

The graph of FIG. 8 shows a transition of the actual line pressure P when the target value Po of the line pressure is increased from the first predetermined pressure P1 to the second predetermined pressure P2 in the first embodiment.

It is possible to change the target value Po of the line pressure as described above by changing the hydraulic pressure (the set pressure) input to the second control port A2 by changing the control signal to the hydraulic control valve 74. After the target value Po is changed to the second predetermined pressure P2, the first input port B1 is closed when the line pressure P is lower than the second predetermined pressure P2, and the line pressure P is the second pressure P2. When it rises with respect to the predetermined pressure P2, it will be in an open state.

7A, 7B and 8, when the target value Po is increased from the first predetermined pressure P1 to the second predetermined pressure P2 at time t2, the line pressure P becomes lower than the second predetermined pressure P2. The first input port B1 of the regulator valve 40 is closed, and oil is discharged from the control chamber 36 to the feedback line 57.

As shown in FIG. 7A, in the first comparative example, when the target value Po is increased from the first predetermined pressure P1 to the second predetermined pressure P2 at time t2, the control chamber 36 of the oil pump 20 returns to the feedback line 57. Is drained. This draining of oil is promptly performed without restriction, and the line pressure P increases rapidly.

The line pressure P thus rapidly increased exceeds the second predetermined pressure P2, whereby the first input port B1 of the regulator valve 40 is opened, and oil is supplied to the control chamber 36 via the feedback line 57. . In the first comparative example, the oil supply to the control chamber 36 is also performed quickly without being restricted, similarly to the oil drain from the control chamber 36, so the line pressure P drops rapidly and the second predetermined pressure P2 is set again. The oil is discharged from the control chamber 36 again.

Thus, in the first comparative example, hunting is likely to occur even when the target value of the line pressure is increased. For this reason, it takes time for the line pressure P to stabilize at the second predetermined pressure P2, and the accuracy of the hydraulic control during that time is likely to decrease.

As shown in FIG. 7B, in the second comparative example, when the target value Po is increased from the first predetermined pressure P1 to the second predetermined pressure P2 at time t2, oil is discharged from the control chamber 36. Since this drainage is limited by the orifice 83, it takes time for the line pressure P to rise to the second predetermined pressure P2, and the accuracy of hydraulic control tends to be reduced.

On the other hand, in the first embodiment, as shown in FIG. 8, the line pressure P becomes lower than the second predetermined pressure P2, which is the new target value Po, due to the increase of the target value Po (time t2). After that, when oil is discharged from the control chamber 36 in order to increase the line pressure P, the check valve 82 in the oil supply restriction device 80 is opened, and quick oil is discharged via the feedback line 57 and the drain line 60. Is performed, the line pressure P quickly rises to the second predetermined pressure P2.

Then, when the line pressure P exceeds the second predetermined pressure P2 and is switched to refueling to the control chamber 36, the refueling is restricted by the refueling restriction device 80, so that the line pressure P gradually decreases. As a result, the hunting of the line pressure P is suppressed, and the line pressure P can be quickly stabilized to the second predetermined pressure P2 or a value close to the second predetermined pressure P2.

Thus, in the first embodiment, the line pressure P can be quickly increased as the target value Po increases, and can be stabilized at a desired pressure (second predetermined pressure P2). High-precision hydraulic control according to the desired line pressure can be performed.

9A and 9B show an example of a specific configuration of the oil supply restriction device 80 according to the first embodiment. Note that the configuration of the hydraulic pressure supply device 10 other than the oil supply restriction device 80 is as described above, and therefore, the description thereof is omitted here and the illustration thereof is omitted in FIGS. 9A and 9B.

9A and 9B, the oil supply restriction device 80 is configured in a unit shape and provided in the feedback line 57. The oil supply restriction device 80 is an integrated unit of an orifice 81 and a check valve 82.

The oil supply restriction device 80 includes a housing 151 provided on the feedback line 57. The housing 151 includes a first communication port 152 that communicates an internal space (an oil passage space S1 described later) of the housing 151 with an oil passage portion of the feedback line 57 closer to the output port C1 than the housing 151, and a housing. A second communication port 153 that communicates with the oil passage portion closer to the control chamber 36 than 151 is provided.

The first communication port 152 and the second communication port 153 are arranged to face each other in the length direction of the feedback line 57. An oil passage space S 1 that connects the first communication port 152 and the second communication port 153 is formed in the housing 151. Further, a check valve 82 is accommodated in the housing 151 so as to be slidable in a direction opposite to the first communication port 152 and the second communication port 153.

The check valve 82 has a bottomed cylindrical valve body 181 that extends in the length direction of the feedback line 57 and is opened to the first communication port 152 side. The valve body 181 has a hole 183 that extends in the length direction of the feedback line 57 and opens to the first communication port 152 side, and a bottom 184 that closes the opening of the hole 183 on the second communication port 153 side. Is provided. A spring 185 that urges the valve body 181 toward the second communication port 153 is accommodated in the hole 183. A plurality of grooves 186 extending in the axial direction of the valve body 181 are provided on the outer peripheral surface of the valve body 181 at intervals in the circumferential direction. Each groove portion 186 always communicates with the first communication port 152 and can communicate with the second communication port 153 according to the position of the valve body 181 in the axial direction.

In a state where each groove portion 186 communicates with the second communication port 153, an oil passage portion that extends from the first communication port 152 to the second communication port 153 through the groove portion 186 is formed in the oil passage space S1 in the housing 151. Is done. This oil passage portion corresponds to the aforementioned second oil passage portion 59 (see FIGS. 1 to 3).

The orifice 81 is provided so as to penetrate the bottom 184 of the valve body 181, whereby the orifice 81 and the valve body 181 (check valve 82) are integrated. The orifice 81 has a smaller diameter than the first communication port 152, the second communication port 153, and the hole 183. The orifice 81 is provided at the bottom 184 so that the internal space of the hole 183 communicates with the second communication port 153.

Thereby, in the oil passage space S1 in the housing 151, an oil passage portion is formed from the first communication port 152 to the second communication port 153 via the internal space of the hole 183 and the orifice 81. This oil passage portion corresponds to the aforementioned first oil passage portion 58 (see FIGS. 1 to 3).

As shown in FIG. 9A, when oil flows from the output port C1 side of the regulator valve 40 toward the control chamber 36 side of the oil pump 20 in the feedback line 57, the oil is supplied from the first communication port 152 into the housing 151. The valve body 181 moves to the second communication port 153 side by the hydraulic pressure and the urging force of the spring 185, and the second communication port 153 is blocked by the bottom 184 of the valve body 181. At this time, the 2nd communicating port 153 and the groove part 186 will be in a non-communication state. Thereby, all of the oil flowing from the first communication port 152 to the second communication port 153 passes through the orifice 81 (first oil passage portion 58) (see FIG. 3).

At this time, the flow rate of oil flowing from the output port C1 side to the control chamber 36 side in the feedback line 57 is limited by the orifice 81 of the oil supply limiting device 80, thereby limiting the oil supply to the control chamber 36.

On the other hand, as shown in FIG. 9B, when oil flows from the control chamber 36 side of the oil pump 20 toward the output port C1 side of the regulator valve 40 in the feedback line 57, the oil is supplied from the second communication port 153 into the housing 151. Due to the hydraulic pressure, the valve body 181 moves against the urging force of the spring 185 toward the first communication port 152 side, the second communication port 153 is opened, and the second communication port 153 and the groove 186 are connected. It becomes a disconnected state.

At this time, the orifice 81 and the groove 186 are in communication with both the first communication port 152 and the second communication port 153. As a result, the oil flowing from the second communication port 153 side to the first communication port 152 side can be passed through both the orifice 81 and the groove portion 186. Therefore, the oil discharged from the control chamber 36 to the feedback line 57 is quickly drained through the drain line 60 without being restricted by the oil supply restriction device 80 (see FIG. 2).

According to the oil supply restriction device 80 configured as described above, the two oil passage portions corresponding to the first oil passage portion 58 and the second oil passage portion 59 can be formed in the oil passage space S 1 in the housing 151. it can. As a result, in combination with the integration of the orifice 81 and the check valve 82, the parallel portion of the first oil passage 58 and the second oil passage 59 in the feedback line 57 can be made compact. .

Note that the configuration of the above-described oil supply restriction device 80 is merely an example, and the specific configuration of the oil supply restriction device 80 in the first embodiment is not particularly limited.

(Second Embodiment)
10 to 12 show a hydraulic pressure supply device 110 for an automatic transmission according to a second embodiment. The automatic transmission and hydraulic pressure supply device 110 in the second embodiment are also mounted on the vehicle. 10 to 12, the same portions as those in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted.

As shown in FIG. 10, in the second embodiment, a drain port D1 is provided in the regulator valve 40 in place of the drain line 60 in the first embodiment.

In the second embodiment, the configuration of the feedback line 57 is the same as that of the first embodiment except that the drain line 60 is not connected, and the configuration of the regulator valve 40 is that the drain port D1 is added. Except for this, it is the same as the first embodiment.

A drain line 120 is connected to the drain port D1, and the oil in the feedback line 57 is drained through the drain line 120 in a state where the drain port D1 and the output port C1 communicate with each other.

As shown in FIG. 11, when the hydraulic pressure in the control chamber 36 of the oil pump 20 is decreased to increase the line pressure, the regulator valve 40 is in a non-communication state with respect to the output port C1 when the first input port B1 is closed. Thus, the hydraulic pressure output from the output port C1 is stopped. In this output stop state, the drain port D1 is opened and communicated with the output port C1.

At this time, the oil discharged from the control chamber 36 of the oil pump 20 to the feedback line 57 passes through the first oil passage portion 58 and the second oil passage portion 59, and the drain port D 1 and the drain line 120 of the regulator valve 40. It is drained through. Thereby, smooth oil drainage from the control chamber 36 is promoted. Therefore, as in the first embodiment, the responsiveness can be improved with respect to an increase in line pressure.

On the other hand, as shown in FIG. 12, when the hydraulic pressure in the control chamber 36 of the oil pump 20 is increased to decrease the line pressure, the regulator valve 40 outputs the hydraulic pressure input to the first input port B1 from the output port C1. To do. When the hydraulic pressure is output from the output port C1, the drain port D1 is closed and the output port C1 is disconnected. In this non-communication state, the drain port D 1 regulates the drain of oil in the feedback line 57.

When oil pressure is output from the output port C1, the oil flowing from the first input port B1 to the output port C1 is not drained from the drain port D1. Further, the oil flowing through the feedback line 57 is supplied to the control chamber 36 of the oil pump 20 without being drained in the middle of the feedback line 57.

In this way, since oil drainage is restricted when refueling the control chamber 36, waste of oil supplied from the oil pump 20 to the control chamber 36 via the regulator valve 40 and the feedback line 57 can be suppressed. .

Therefore, according to the second embodiment, the amount of oil supplied from the discharge port 22b of the oil pump 20 to the first input port B1 of the regulator valve 40 is reduced, and further, the amount of discharge of the oil pump 20 is reduced. Can do. Therefore, the drive loss of the automatic transmission can be reduced, and the fuel consumption performance of the vehicle equipped with the automatic transmission can be improved.

In addition, the specific structure of the oil supply restriction | limiting apparatus 80 in 2nd Embodiment is not specifically limited, either. A configuration similar to the specific configuration described in the first embodiment (the configuration illustrated in FIGS. 9A and 9B) may be employed.

(Third embodiment)
13 to 15 show a hydraulic pressure supply device 210 for an automatic transmission according to a third embodiment. The automatic transmission and hydraulic pressure supply device 110 in the third embodiment are also mounted on the vehicle. 13 to 15, the same parts as those in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted.

As shown in FIG. 13, in the third embodiment, the feedback lines 57 are connected in series with each other in place of the first oil passage portion 58 and the second oil passage portion 59 connected in parallel with each other in the first embodiment. It has the 1st oil path part 257 and the 2nd oil path part 258 which were connected.

The first oil passage portion 257 and the second oil passage portion 258 are connected to each other via an oil supply restriction device 280 configured in a unit shape. The end of the first oil passage portion 257 opposite to the oil supply restriction device 280 is connected to the output port C1 of the regulator valve 40, and the end of the second oil passage portion 258 opposite to the oil supply restriction device 280 is The oil pump 20 is connected to the control chamber 36. Further, the feedback line 57 is connected to the drain line 260 via the oil supply limiting device 280.

The oil supply restriction device 280 has a housing 281 in which an oil passage space S2 is formed. The housing 281 includes a first communication port 282 that allows the oil passage space S2 in the housing 281 to communicate with the first oil passage portion 257 of the feedback line 57, and the oil passage space S2 to the second oil passage portion of the feedback line 57. A second communication port 283 that communicates with 258 and a third communication port 284 that communicates the oil passage space S2 with the drain line 260 are provided.

The first communication port 282 and the second communication port 283 are arranged to face each other in the length direction of the feedback line 57. A relief valve 290 is accommodated in the housing 281 so as to be slidable in the opposing direction of the first communication port 282 and the second communication port 283.

The relief valve 290 has a bottomed cylindrical valve body 297 that extends in the length direction of the feedback line 57 and opens to the first communication port 282 side. The valve body 297 is provided with a hole portion 291 that extends in the length direction of the feedback line 57 and opens to the first communication port 282 side, and a bottom portion 292 that closes the opening of the hole portion 291 on the second communication port 283 side. It has been. The outer peripheral surface of the valve body 297 is disposed to face the third communication port 284.

A spring 293 that biases the valve body 297 toward the second communication port 283 is accommodated in the hole 291 of the valve body 297. One or a plurality of groove portions 294 extending in the axial direction of the valve body 297 are provided in a portion of the outer peripheral surface of the valve body 297 on the second communication port 283 side. The end of the groove 294 on the first communication port 282 side is closed. The groove portion 294 can communicate with both the second communication port 283 and the third communication port 284 according to the position of the valve body 297 in the axial direction.

In a state where the groove portion 294 communicates with the second communication port 283 (a state where the relief valve 290 is opened), the groove portion 294 is inserted into the housing 281 from a portion between the second communication port 283 and the bottom portion 292 of the valve body 297. An oil passage portion that reaches the third communication port 284 via is formed. The oil passage portion is connected to the drain line 260 via the third communication port 284. The oil passage portion and the drain line 260 constitute a drain oil passage that drains the oil discharged from the control chamber 36 of the oil pump 20 to the feedback line 57 via the opened relief valve 290.

An orifice 295 is provided through the bottom 292 of the valve body 297, whereby the orifice 295 and the valve body 297 (relief valve 290) are integrated. The orifice 295 has a smaller diameter than the first communication port 282, the second communication port 283, the third communication port 284, and the hole portion 291. The orifice 295 is provided on the bottom 292 so that the internal space of the hole 291 communicates with the second communication port 283.

Thereby, in the oil passage space S2 in the housing 281, an oil passage portion is formed from the first communication port 282 to the second communication port 283 via the internal space of the hole 291 and the orifice 295. The oil passage portion constitutes an oil passage portion that connects the first communication port 282 and the second communication port 283 in the feedback line 57.

In the oil passage space S2 in the housing 281, a portion between the second communication port 283 and the bottom portion 292 of the valve body 297 constitutes a connection portion 285 of the feedback line 57 with the drain oil passage. Thereby, in the feedback line 57, the orifice 295 is arrange | positioned rather than the connection part 285 with the said drain oil path at the output port C1 side. Instead of the orifice 295, an orifice may be provided in the first oil passage portion 257 of the feedback line 57.

By the orifice 295 arranged in this way, in the feedback line 57, the flow of oil between the first oil passage portion 257 and the second oil passage portion 258, and the first oil passage portion 257 of the feedback line 57 and Oil flow to and from the drain line 260 is restricted.

As shown in FIG. 14, when the hydraulic pressure in the control chamber 36 of the oil pump 20 is decreased to increase the line pressure, the output of the hydraulic pressure from the output port C1 of the regulator valve 40 is stopped, and the control chamber The oil discharged from 36 flows through the second oil passage portion 258 of the feedback line 57 from the control chamber 36 side toward the oil supply restriction device 280. At this time, in the oil supply restriction device 280, the valve body 297 of the relief valve 290 moves toward the first communication port 282 against the urging force of the spring 293 by the hydraulic pressure supplied into the housing 281 from the second communication port 283 side. As a result, the relief valve 290 is opened. As a result, the second communication port 283 communicates with the third communication port 284.

When the relief valve 290 is thus opened, the feedback line 57 is connected to the drain line 260 via the groove 294. At this time, in the oil passage space S2 in the housing 281, the flow of oil from the second communication port 283 side to the first communication port 282 side is restricted by the orifice 295, so that the second communication port 283 passes through the groove 294. Thus, the flow of oil reaching the third communication port 284 is promoted. Therefore, the oil discharged from the control chamber 36 is smoothly drained through the relief valve 290 and the drain line 260. As a result, quick drainage is possible, and high responsiveness can be obtained with respect to an increase in line pressure.

On the other hand, as shown in FIG. 15, when the hydraulic pressure in the control chamber 36 of the oil pump 20 is increased to decrease the line pressure, the hydraulic pressure is output from the output port C1 of the regulator valve 40, and the feedback line 57 Then, oil flows from the output port C1 of the regulator valve 40 toward the control chamber 36 of the oil pump 20. At this time, in the oil supply restriction device 280, the valve body 297 of the relief valve 290 moves to the second communication port 283 side by the hydraulic pressure supplied into the housing 281 from the first communication port 282 and the urging force of the spring 293. Thus, the second communication port 283 is closed by the bottom 292 of the valve body 297. Thus, the relief valve 290 is closed. As a result, the oil flowing from the first communication port 282 to the second communication port 283 always passes through the orifice 295. That is, the orifice 295 allows oil from the output port C1 to flow toward the control chamber 36 when the relief valve 290 is closed.

When the relief valve 290 is closed, the flow rate of oil flowing from the output port C1 side to the control chamber 36 in the feedback line 57 is limited by the orifice 295, thereby limiting the oil supply to the control chamber 36. become. As a result, the line pressure can be gradually reduced. Therefore, hunting of the line pressure can be suppressed, and the line pressure can be stabilized at a desired pressure at an early stage.

In addition, according to the third embodiment, the feedback line 57 includes the first oil passage portion 257 and the second oil passage portion 258 connected in series with each other, and thus the feedback lines of the first and second embodiments. The configuration of the feedback line 57 can be simplified as compared with the case where the first oil passage portion 58 and the second oil passage portion 59 are connected in parallel as in the case of 57.

In addition, in 3rd Embodiment, the structure of the above-mentioned oil supply restriction | limiting apparatus 280 is only an example, and various changes are possible as the oil supply restriction | limiting apparatus 280. FIG. For example, a spool valve that performs the same function as the oil supply restriction device 280 may be provided on the feedback line 57.

The present invention is not limited to the embodiment described above, and can be substituted without departing from the spirit of the claims.

For example, in the above-described embodiment, the hydraulic pressure supply device including the vane type variable displacement type oil pump is taken as an example. However, the variable displacement type oil pump is configured to increase the hydraulic pressure in the control chamber of the oil pump. The type and specific configuration of the oil pump are not particularly limited as long as the discharge pressure of the oil pump is reduced, and the discharge pressure is increased by reducing the hydraulic pressure of the control chamber.

The above-described embodiment is merely an example, and the scope of the present invention should not be interpreted in a limited manner. The scope of the present invention is defined by the scope of the claims, and all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

INDUSTRIAL APPLICABILITY The present invention is useful for a hydraulic pressure supply device for an automatic transmission provided with a variable displacement type oil pump. It is particularly useful in the field of manufacturing vehicles.

2 Hydraulic circuit 10 Hydraulic supply device 20 Variable displacement oil pump 36 Control room 40 Regulator valve 57 Feedback line (feedback oil passage)
58 First oil passage 59 Second oil passage 60 Drain line (drain oil passage)
76 Orifice
80 Oil Supply Limiting Device 81 Orifice 82 Check Valve 110 Hydraulic Supply Device 260 Drain Line 280 Oil Supply Limiting Device 290 Relief Valve 295 Orifice A1 First Control Port A2 Second Control Port B1 First Input Port C1 Output Port (Output Unit)
D1 Drain port

Claims

A hydraulic pressure supply device for an automatic transmission,
A variable displacement oil pump that generates hydraulic pressure used to control the automatic transmission;
A regulator valve for adjusting the discharge pressure of the oil pump to a predetermined pressure;
A feedback oil passage for guiding the hydraulic pressure output from the output portion of the regulator valve to the control chamber of the oil pump;
The oil pump is configured such that the discharge pressure decreases as the hydraulic pressure in the control chamber increases, while the discharge pressure increases as the hydraulic pressure in the control chamber decreases.
A hydraulic pressure supply device for an automatic transmission, further comprising an oil supply restriction device provided in the feedback oil passage and configured to restrict oil supply to the control chamber as compared with oil discharged from the control chamber.
In the automatic transmission hydraulic pressure supply device according to claim 1,
The feedback oil passage has a first oil passage portion and a second oil passage portion connected in parallel to each other,
The oil supply restriction device is a check that is provided in an orifice provided in the first oil passage and the second oil passage and restricts passage of oil in a direction from the output portion toward the control chamber. And a hydraulic pressure supply device for an automatic transmission.
In the automatic transmission hydraulic pressure supply device according to claim 2,
A drain oil passage for draining oil from the feedback oil passage through a throttle is connected to a portion of the feedback oil passage closer to the output portion than the orifice and the check valve. Hydraulic supply device for the machine.
In the automatic transmission hydraulic pressure supply device according to claim 2,
The regulator valve drains the oil discharged from the control chamber to the feedback oil passage when the output of the oil pressure from the output portion is stopped, and when the oil pressure is output from the output portion, A hydraulic pressure supply device for an automatic transmission having a drain port for regulating drainage of oil.
In the automatic transmission hydraulic pressure supply device according to claim 1,
The oil supply restriction device is a relief valve provided in the feedback oil passage, is closed when hydraulic pressure is output from the output portion of the regulator valve, and is opened when hydraulic pressure output from the output portion is stopped. A relief valve
A drain oil path for draining oil discharged from the control chamber to the feedback oil path through the opened relief valve is connected to the feedback oil path,
Further, the oil supply limiting device further includes an orifice provided on the output portion side of a connection portion of the feedback oil passage with the drain oil passage.