JP2018150974A - Hydraulic pressure supply device of automatic transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make compatible both the improvement and the stabilization of the rise responsiveness of line pressure, in a hydraulic pressure supply device of an automatic transmission having a variable capacity type oil pump.SOLUTION: In a hydraulic pressure supply device 10 of an automatic transmission comprising: a variable capacity type oil pump 20 for generating hydraulic pressure used in the control of the automatic transmission; a regulator valve 40 for adjusting the discharge pressure of the oil pump to line pressure; and a feedback oil passage 57 for introducing the hydraulic pressure outputted from an output part C1 of the regulator valve into a control chamber 36 of the oil pump, the oil pump 20 is constituted so that the discharge pressure is lowered by a rise of the hydraulic pressure of the control chamber 36, and the discharge pressure is boosted by the lowering of the hydraulic pressure of the control chamber 36, and an oil supply limit part 80 for limiting the supply of oil to the control chamber 36 compared with discharged oil discharged from the control chamber 36 is arranged at the feedback oil passage 57.SELECTED DRAWING: Figure 1

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.

  As disclosed in Patent Literature 1 and Patent Literature 2 and the like, a variable displacement oil pump is used as a hydraulic pressure supply source of a hydraulic circuit for controlling friction engagement elements such as a clutch and a brake of an automatic transmission. Sometimes.

  The oil pumps disclosed in Patent Documents 1 and 2 change the eccentric amount of the cam ring with respect to the drive shaft in accordance with the hydraulic pressure in the control chamber of the hydraulic piston that presses the cam ring, and the larger the eccentric amount, the higher the discharge pressure. It is comprised so that it may become. 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. Further, in this case, 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, the discharge pressure of the oil pump is adjusted to a constant line pressure.

Japanese Unexamined Patent Publication No. 1-141954 JP-A-2-003780

  By the way, in the hydraulic pressure supply apparatus as described above, when the frictional engagement element is changed for shifting the automatic transmission, the line pressure is reduced by supplying oil to the engagement hydraulic chamber of the predetermined frictional engagement element. Decreases temporarily. At this time, the line pressure is increased to the command value by the feedback described above. However, if this increase takes time, it takes time to completely engage the friction engagement element, and the shift time increases and the friction engagement element slips. Will be invited. Therefore, in order to shorten the shift time or suppress the slip, it is required to improve the responsiveness related to the increase in the line pressure.

  In addition, the command value of the line pressure itself may increase depending on the engine output, etc. In this case as well, in order to perform highly accurate hydraulic control according to the command value, the actual line pressure is reduced. High responsiveness is required to raise the command value.

  However, in the control of the line pressure, if an attempt is made to increase the rising response, there is a problem that the line pressure becomes unstable due to overshoot or hunting, and the accuracy of the shift control tends to be lowered.

  SUMMARY OF THE INVENTION An object of the present invention is to improve both line pressure increase response and stability 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 variable displacement oil pump that generates hydraulic pressure used for controlling an automatic transmission, a regulator valve that adjusts the discharge pressure of the oil pump to a line pressure, and the hydraulic pressure that is output from the output portion of the regulator valve A hydraulic pressure supply device for an automatic transmission comprising a feedback oil passage leading to a pump control chamber,
The oil pump is configured such that the discharge pressure decreases as the hydraulic pressure in the control chamber increases, and the discharge pressure increases as the hydraulic pressure in the control chamber decreases.
The feedback oil passage is provided with an oil supply limiting unit that restricts oil supply to the control chamber as compared with oil discharged from the control chamber.

The invention according to claim 2 is the invention according to claim 1,
The feedback oil passage includes a first oil passage portion and a second oil passage portion connected in parallel to each other,
The oil supply restriction portion is provided in the first oil passage portion and the second oil passage portion, and a check that restricts passage of oil in a direction from the output portion side toward the control chamber side. And a valve.

The invention according to claim 3 is the invention according to claim 2,
A drain oil passage for draining oil from the feedback oil passage via a throttle means is connected to the output side portion of the feedback oil passage from the orifice and the check valve.

The invention according to claim 4 is the invention according to claim 2,
The regulator valve includes a drain port that drains oil discharged from the control chamber to the feedback oil passage in a state where output from the output unit is stopped and regulates drain when output from the output unit. It is characterized by.

The invention according to claim 5 is the invention according to claim 1,
A drain oil passage for draining drained oil from the control chamber is connected to the feedback oil passage via a relief valve,
The oil supply restricting portion includes an orifice provided on the output portion side of a connection portion with the drain oil passage in the feedback oil passage.

  According to the first aspect of the present invention, when the line pressure is increased to a desired pressure by lowering the hydraulic pressure in the control chamber of the variable displacement oil pump, the oil is quickly discharged from the control chamber. Therefore, high responsiveness can be obtained with respect to an increase in the line pressure, thereby shortening the shift time, suppressing the slip of the frictional engagement element, and performing highly accurate hydraulic control according to the desired line pressure. Can do.

  In addition, when the line pressure is reduced to the desired pressure by increasing the oil pressure in the control chamber of the oil pump after the line pressure is quickly increased and exceeds the desired pressure as described above, the oil supply to the control chamber is reduced. By being limited, the line pressure is gradually reduced. Therefore, hunting of the line pressure is suppressed and the line pressure can be stabilized at an early stage, thereby realizing highly accurate shift control.

  According to the second aspect of the present invention, when the oil pressure in the control chamber of the oil pump is increased to decrease the line pressure, the orifice provided in the first oil passage portion of the feedback oil passage and the oil passage The line pressure can be gradually lowered by restricting the oil supply to the control chamber by the check valve provided in the second oil passage.

  On the other hand, when lowering the hydraulic pressure in the control chamber of the oil pump and increasing the line pressure, the check valve in the second oil passage is opened so that oil can be quickly discharged from the control chamber. This makes it possible to obtain high responsiveness with respect to an increase in line pressure.

  When the invention according to claim 3 is applied to the invention according to claim 2, when the oil pressure in the control chamber of the oil pump is reduced to increase the line pressure, the oil discharged from the control chamber of the oil pump is drained. By draining through the oil passage, it is possible to promote smooth drainage and improve the response to increase in line pressure.

  When the oil pressure in the control chamber of the oil pump is increased to reduce the line pressure, 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, the influence of the output fluctuation of the regulator valve on the hydraulic pressure of the control chamber can be reduced. Further, at this time, excessive drainage is suppressed by the throttle means, so that it is possible to prevent the oil supply to the control chamber from being excessively delayed or insufficient.

  When the invention according to claim 4 is applied to the invention according to claim 2, when the oil pressure in the control chamber of the oil pump is lowered to increase the line pressure, the oil discharged from the control chamber to the feedback oil passage By draining from the drain port of the regulator valve, it is possible to promote smooth drainage and improve the response to increase in line pressure.

  Also, when increasing the oil pressure in the control chamber of the oil pump to lower the line pressure, the drain from the drain port of the regulator valve is regulated so that the oil pressure discharged from the oil pump passes through the regulator valve. In the oil cycle fed back to the control room of the oil pump, waste of oil can be suppressed. Therefore, it is possible to reduce the amount of oil supplied from the oil pump to the regulator valve, and hence reduce the discharge amount of the oil pump, thereby reducing the drive loss of the automatic transmission, thereby reducing the fuel consumption performance of the vehicle. It becomes easy to contribute to improvement.

  According to the fifth aspect of the present invention, when the oil pressure in the control chamber of the oil pump is increased to decrease the line pressure, the oil supply to the control chamber is limited by the orifice provided in the feedback oil passage. As a result, the line pressure can be gradually reduced.

  On the other hand, when the line pressure is increased by lowering the hydraulic 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, thereby increasing the line pressure. High responsiveness can be obtained. In addition, since it is possible to achieve both the promotion of oil drainage and the above-described restriction of oil supply without providing a parallel oil passage portion in the feedback oil passage, the oil passage configuration can be simplified.

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 which shows the same hydraulic pressure supply apparatus in the state of oil draining from the control chamber of an oil pump. The circuit diagram which shows the same hydraulic pressure supply apparatus in the oil supply state to a control room. The circuit diagram which shows a part of hydraulic pressure supply apparatus which concerns on a 1st comparative example and a 2nd comparative example. The graph which shows transition of the line pressure at the time of the speed change in a 1st comparative example and a 2nd comparative example. The graph which shows transition of the line pressure at the time of the gear shift in 1st Embodiment. The graph which shows transition of the line pressure at the time of the command value rise in a 1st comparative example and a 2nd comparative example. The graph which shows transition of the line pressure at the time of the command value rise in 1st Embodiment. The figure which shows the structural example of the principal part of the feedback line in 1st Embodiment. 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 which shows the same hydraulic pressure supply apparatus in the state of oil draining from the control chamber of an oil pump. The circuit diagram which shows the same hydraulic pressure supply apparatus in the oil supply state to a control room. The circuit diagram which shows the hydraulic pressure supply apparatus of the automatic transmission which concerns on 3rd Embodiment of this invention. The circuit diagram which shows the same hydraulic pressure supply apparatus in the state of oil draining from the control chamber of an oil pump. The circuit diagram which shows the same hydraulic pressure supply apparatus in the oil supply state to a control room.

  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 apparatus 10 for an automatic transmission according to a first embodiment will be described with reference to FIGS.

  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.

  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 70, and a discharge port 22 b that discharges the oil boosted 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.

  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.

  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.

  A counter 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. The counter chamber 38 is connected to an oil drain passage 64 for draining oil that has flowed into the counter chamber 38.

  When the hydraulic pressure supplied to the control chamber 36 is increased, the cam ring 30 is displaced toward the facing chamber 38 against the urging force of the spring 32, 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 36 is reduced, the cam ring 30 is displaced in the urging direction 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 is reduced, so that the discharge pressure of the oil pump 20 decreases.

  As described above, the oil pump 20 is configured such that the discharge pressure decreases as the hydraulic pressure in the control chamber 36 increases, and the discharge pressure increases as the hydraulic pressure in the control chamber 36 decreases. Therefore, 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 predetermined hydraulic circuit 2 that controls supply / discharge of oil to / from each friction engagement element (not shown) of the automatic transmission. An accumulator 71 is connected to the main line 51, thereby suppressing oil vibration in the main line 51.

  A sub-line 52 is connected to the main line 51 at a portion downstream from the accumulator 71 (on the hydraulic circuit 2 side). The sub line 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 on the downstream side (regulator valve 40 side).

  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, an output port C1, and an emergency drain port C2.

  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), and the hydraulic pressure input to the second control port A2 is The spool 42 is biased toward the same side as the elastic force of the return spring 44 (the right side in FIG. 1).

  The first control port A1 is on the first control line 54, the second control port A2 is on the second control line 56, the first input port B1 is on the first input line 53, and the second input port B2 is on the second input line 55. Are connected to each other.

  An orifice 72 is provided in the first control line 54. Thus, the oil whose flow rate is limited by the orifice 72 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 second control line 56 is provided with a pressure reducing valve 73, a hydraulic control valve 74, and an orifice 75. As a result, the hydraulic pressure input to the second control line 56 is reduced by the pressure reducing valve 73 and then controlled to a predetermined pressure by the hydraulic control valve 74. The oil hydraulically controlled by the hydraulic control valve 74 is supplied to the second control port A2 with the flow rate limited by the orifice 75.

  For example, an electromagnetic valve is used as the hydraulic control valve 74. 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 hydraulic control valve 74.

  The axial position of the spool 42 of the regulator valve 40 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 hydraulic control valve 74 as described above. It is adjusted by the balance between the hydraulic pressure and the elastic force of the return spring 44.

  The emergency drain port C <b> 2 is connected to the oil pan 70 via the emergency drain line 62. The emergency drain port C2 communicates with the second input port B2 when 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 from the emergency drain port C2 via the second input port B2, so that excess oil flows into the first control port A1, the second control port A2, and the first input port B1. Therefore, 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 a 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 passes through the feedback line 57 to the control chamber of the oil pump 20. 36 is fed back.

  The feedback line 57 includes a first oil passage portion 58 and a second oil passage portion 59 that are connected in parallel to each other.

  An orifice 81 is provided in the first oil passage portion 58. Thus, in the first oil passage portion 58, the direction from the output port C1 side of the regulator valve 40 toward the control chamber 36 side of the oil pump 20 (oil supply direction to the control chamber 36), and the output port from the control chamber 36 side. The oil flow rate is limited by the orifice 81 in any direction toward the C1 side (the direction of oil drained from the control chamber 36).

  A check valve 82 is provided in the second oil passage portion 59. The check valve 82 regulates the passage of oil in the oil supply direction (the direction from the output port C1 side of the regulator valve 40 toward the control chamber 36 side of the oil pump 20). Thereby, the passage of oil in the second oil passage portion 59 is allowed only in the oil discharge direction (the direction from the control chamber 36 side to the output port C1 side).

  As described above, in the feedback line 57, the above-described orifice 81 and the check valve 82 constitute an oil supply restriction unit 80 that restricts the oil supply to the control chamber 36 compared to the oil discharged from the control chamber 36.

  A drain line 60 serving as a drain oil passage is connected to the feedback line 57 at a portion upstream of the orifice 81 and the check valve 82 (on the output port C1 side). The drain line 60 is branched from the feedback line 57 upstream of 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 can be drained via the drain line 60.

  The drain line 60 is provided with an orifice 76 as a throttle means. The orifice 76 restricts the flow rate of oil drained through the drain line 60.

  In the hydraulic pressure supply device 10 configured as described above, when the line pressure is controlled to a predetermined pressure, the output of the hydraulic control valve 74 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 FIG. 1 when the line pressure increases, and moves to the right in FIG. 1 when the line pressure decreases.

  In accordance with such axial movement of the spool 42, the first input port B1 of the regulator valve 40 is appropriately switched between the closed state shown in FIG. 2 and the open state shown in FIG.

  As shown in FIG. 2, when the first input port B1 is closed and is not in communication with the output port C1, output 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. On the other hand, in the second oil passage 59, the oil flowing from the control chamber 36 toward the output port C1 passes through the open check valve 82. Accordingly, a larger amount of oil flows in the second oil passage portion 59 than in the first oil passage portion 58.

  The drained oil that has passed through the first oil passage 58 or the second oil passage 59 in this way is drained via the drain line 60. Thereby, smooth oil draining from the control chamber 36 is promoted. Therefore, the discharge pressure of the oil pump 20, that is, the line pressure can be quickly increased by quickly reducing the hydraulic pressure in the control chamber 36.

  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 discharge port 22b of the oil pump 20 passes through the main line 51, the sub line 52, and the first input line 53. Then, the oil supplied to the first input port B1 is led from the output port C1 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 prohibited from passing through the second oil passage portion 59 by the check valve 82, and the flow rate in the first oil passage portion 58 by the orifice 81. This limits the oil supply to the control chamber 36. Therefore, the discharge pressure of the oil pump 20, that is, the line pressure can be gradually reduced by gradually increasing the hydraulic pressure in the control chamber 36.

  At this time, the excess oil flowing through the feedback line 57 is led 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 is stabilized, so that the influence of the output fluctuation of the regulator valve 40 on the hydraulic pressure of the control chamber 36 is reduced. it can.

  Further, at this time, since the drain amount from the feedback line 57 to the drain line 60 is limited by the orifice 76, 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 excessively delayed or insufficient.

  The effects of the first embodiment will be described more specifically with comparison with the first comparative example shown in FIG. 4A and the second comparative example shown in FIG.

  As shown to Fig.4 (a), the hydraulic pressure supply apparatus which concerns on a 1st comparative example is the 2nd oil path part 59 and the oil supply restriction | limiting part of the feedback line 57 from the above-mentioned hydraulic pressure supply apparatus 10 (refer FIGS. 1-3). Except for 80 (orifice 81 and check valve 82), other configurations are the same as in the first embodiment.

  As shown in FIG. 4B, the hydraulic pressure supply device according to the second comparative example is the same as the hydraulic pressure supply device 10 (see FIGS. 1 to 3), the second oil passage portion 59 and the check valve of the feedback line 57. This is similar to the first embodiment in that the orifice 81 is provided in the feedback line 57.

  The graph of FIG. 5A is the first comparative example, the graph of FIG. 5B is the second comparative example, and the graph of FIG. 6 is the first embodiment, the line pressure command value Po is the predetermined value P1. It shows the transition of the actual line pressure P when the automatic transmission is shifted in the controlled vehicle running state.

  As shown in FIG. 5A, in the first comparative example, when the shift is started at time t1, the actual line pressure P is set to the command value Po by supplying oil to a predetermined friction engagement element. Although it temporarily decreases so as to be lower than (P1), the oil pressure from the control chamber 36 of the oil pump 20 to the feedback line 57 is promptly performed without being restricted, so that the line pressure P is quickly increased. Be raised.

  The line pressure P that has risen rapidly in this manner exceeds the command value P1, thereby switching from the oil drained state from the control chamber 36 to the oil supply state to the control chamber 36. In the first comparative example in which the oil supply restriction unit 80 is not provided in the feedback line 57, this oil supply is also quickly performed without being restricted. Therefore, the line pressure P rapidly decreases and falls below the command value P1 again, and the control chamber 36 is switched from the oil supply state to the oil discharge state.

  Thus, in the first comparative example, hunting in which the line pressure P repeats a rapid increase and a rapid decrease is likely to occur. For this reason, it takes time for the line pressure P to stabilize at the command value P1, and the hydraulic pressure supplied to the frictional engagement element becomes unstable during that time, which may reduce the accuracy of the shift control.

  As shown in FIG. 5B, also in the second comparative example, when the shift is started at time t1, the line pressure P decreases so as to be lower than the command value Po (P1). Then, in order to increase the line pressure P, oil is discharged from the control chamber 36, but this oil is restricted by the orifice 81 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 command value P1, and as a result, it takes time until the predetermined frictional engagement element is completely engaged, thereby increasing the shift time. Or slip occurs 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 has decreased due to the start of shifting (time t1), the oil discharged from the control chamber 36 is increased in order to increase the line pressure P. When the check is performed, the check valve 82 in the refueling restriction unit 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 command value P1. .

  Further, when the line pressure P exceeds the command value P1 and the control chamber 36 is switched from the oil drained state to the oil supply state, the oil supply is limited by the oil supply limiting unit 80, so that the line pressure P gradually decreases. . Therefore, hunting of the line pressure P is suppressed, and the line pressure P is easily stabilized at the command value P1 or in the vicinity thereof.

  As described above, in the first embodiment, the line pressure P that has dropped with the start of shifting can be quickly raised and stabilized to the desired pressure P1, so that the shifting time can be shortened and slipping of the frictional engagement element can be suppressed. And, the accuracy of the shift control can be improved.

  7A is the first comparative example (see FIG. 4A), FIG. 7B is the second comparative example (see FIG. 4B), and FIG. 8 is the first embodiment. Regarding the form, the transition of the actual line pressure P when the command value Po of the line pressure is raised from the first value P1 to a second value higher than this is shown.

  As shown in FIG. 7A, in the first comparative example, when the command value Po is switched from the first value P1 to the second value P2 at time t2, the actual line pressure P is increased according to this command. Therefore, the oil pressure from the control chamber 36 of the oil pump 20 to the feedback line 57 is promptly performed without being restricted, so that the line pressure P is quickly increased.

  The line pressure P that has increased rapidly in this manner exceeds the second value P2, thereby switching from the oil drained state from the control chamber 36 to the oil supply state to the control chamber 36. In the first comparative example, this refueling is also performed promptly without being restricted. Therefore, the line pressure P rapidly decreases and falls below the second value P2 again, and the control chamber 36 switches from the oil supply state to the oil discharge state. It is done.

  As described above, in the first comparative example, hunting is likely to occur even when the command value Po of the line pressure P is increased. Therefore, it takes time until the line pressure P stabilizes at the second value P2, and during that time, The accuracy of hydraulic control is likely to decrease.

  As shown in FIG. 7B, also in the second comparative example, when the command value Po is switched from the first value P1 to the second value P2 at time t2, the line pressure P is increased according to this command. In addition, oil supply from the control chamber 36 is performed, but this drainage is limited by an orifice 81 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 second value P2, and therefore, the hydraulic pressure supplied to the fastening hydraulic chamber and thus the fastening force is insufficient in the predetermined frictional engagement element. By doing so, slipping easily occurs.

  On the other hand, in the first embodiment, as shown in FIG. 8, when oil is discharged from the control chamber 36 in order to increase the line pressure P in accordance with the increase in the command value Po (time t2), the oil supply restriction is performed. The check valve 82 in the section 80 is opened, and the 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 second value P2.

  When the line pressure P exceeds the second value P2 and the control chamber 36 is switched from the oil drained state to the oil supply state, the oil supply is restricted by the oil supply restricting unit 80, so that the line pressure P gradually increases. descend. Therefore, hunting of the line pressure P is suppressed, and the line pressure P can be easily stabilized at the second value P2 or in the vicinity thereof.

  As described above, in the first embodiment, the line pressure P can be quickly increased and stabilized to the desired pressure P2 as the command value Po increases, so that the slip of the frictional engagement element can be suppressed, or the desired line can be controlled. High precision hydraulic control according to the pressure can be performed.

[Configuration example of the main part of the feedback line]
FIG. 9A and FIG. 9B are diagrams illustrating an example of a specific configuration of a main part of the feedback line 57 in the first embodiment. Since the configuration other than the main part of the feedback line 57 is as described above, the description thereof is omitted here, and the illustration is omitted in FIGS. 9A and 9B.

  In the configuration example shown in FIGS. 9A and 9B, the feedback line 57 is provided with an oil supply restriction unit 150 as an oil supply restriction unit. The oil supply restriction unit 150 is obtained by integrating the orifice 81 and the check valve 82 described above.

  The oil supply restriction unit 150 includes a housing 151 provided on the feedback line 57 and a first communication that communicates the internal space of the housing 151 with an oil passage portion on the upstream side (the output port C1 side of the regulator valve 40) of the feedback line 57. A port 152 and a second communication port 153 that allows the internal space of the housing 151 to communicate with an oil passage on the downstream side of the feedback line 57 (on the control chamber 36 side of the oil pump 20).

  The first communication port 152 and the second communication port 153 are disposed so as to face each other, and an oil passage space S1 that connects between the first communication port 152 and the second communication port 153 is formed in the housing 151. ing. A check valve 82 is accommodated in the housing 151 so as to be slidable in the opposing direction of the first communication port 152 and the second communication port 153.

  The check valve 82 has a bottomed cylindrical shape having a hole 183 that opens to the first communication port 152 side and a bottom 184 that closes the hole 183 from the second communication port 153 side. A spring 185 that urges the check valve 82 toward the second communication port 153 is accommodated in the hole 183. A plurality of grooves 186 extending in the axial direction are provided on the outer peripheral surface of the check valve 82 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 check valve 82.

  In a state where the groove 186 communicates with the second communication port 153, an oil path portion extending from the first communication port 152 to the second communication port 153 through the groove 186 is formed in the oil channel space S 1 in the housing 151. The The said oil path part is a part corresponded to the 2nd oil path part 59 (refer FIGS. 1-3) mentioned above.

  The orifice 81 is provided through the bottom 184 of the check valve 82, whereby the orifice 81 and the 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 so that the internal space of the hole 183 communicates with the second communication port 153.

  Thus, an oil passage portion is formed in the oil passage space S1 in the housing 151 from the first communication port 152 to the second communication port 153 via the internal space of the hole 183 and the orifice 81. The oil passage portion is a portion corresponding to the first oil passage portion 58 (see FIGS. 1 to 3) described above.

  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 first communication port 152 side leads to the inside of the housing 151. The check valve 82 moves to the second communication port 153 side by the hydraulic pressure supplied to the valve 185 and the urging force of the spring 185, the second communication port 153 is closed by the bottom 184 of the check valve 82, and the groove 186. The second communication port 153 side is closed. As a result, the oil flowing from the first communication port 152 to the second communication port 153 always passes through the orifice 81.

  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 unit 150, 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 housing from the second communication port 153 side. The check valve 82 moves to the first communication port 152 side against the urging force of the spring 185 by the hydraulic pressure supplied into the engine 151, and both the first communication port 152 and the second communication port 153 are opened. Is done.

  At this time, the orifice 81 and the groove 186 in the check valve 82 are in communication with both the first communication port 152 and the second communication port 153, and thereby, in the housing 151, both in the orifice 81 and the groove 186. The oil flowing from the second communication port 153 side to the first communication port 152 side can be passed. Therefore, the oil discharged from the control chamber 36 to the feedback line 57 is quickly drained via the drain line 60 (see FIG. 2) without the flow rate being restricted by the oil supply restriction unit 150.

  According to the configuration of the oil supply restriction unit 150 described above, the two oil passages corresponding to the first oil passage portion 58 and the second oil passage portion 59 (see FIGS. 1 to 3) described above are replaced with oil in the housing 151. Since it can be formed in a concentrated manner in the road space S1, the oil path configuration can be made compact.

  In addition, the structure of the oil supply restriction | limiting unit 150 demonstrated above is only an example to the last, and the specific structure of the oil supply restriction | limiting part 80 (refer FIG. 1) in 1st Embodiment is not specifically limited.

[Second Embodiment]
A hydraulic pressure supply device 110 for an automatic transmission according to a second embodiment will be described with reference to FIGS.

  Note that in the second embodiment, the description of the configuration common to the first embodiment is omitted, and the same reference numerals are given in FIGS. 10 to 12.

  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 (see FIGS. 1 to 3) 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 a drain port D1 is added. Is the same as in the first embodiment.

  A drain line 120 is connected to the drain port D1, and the oil in the feedback line 57 can be drained via 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 state where the output is stopped by closing the first input port B1. . In this output stop state, the drain port D1 is opened and communicated with the output port C1.

  At this time, the oil drained from the control chamber 36 of the oil pump 20 to the feedback line 57 is drained through the drain port D1 of the regulator valve 40, whereby a smooth drain from the control chamber 36 is achieved. Oil is urged. Therefore, with respect to the increase in line pressure, it is possible to improve the responsiveness as in the first embodiment.

  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. In this output state, the drain port D1 is closed and is not in communication with the output port C1.

  At this time, the oil flowing from the input port B1 to the output port C1 is not drained from the drain port D1. The oil flowing through the feedback line 57 is also supplied to the control chamber 36 of the oil pump 20 without being drained on the way.

  In this way, since the drain is regulated when refueling the control chamber 36, the oil pressure discharged from the oil pump 20 is fed back to the control chamber 36 of the oil pump 20 via the regulator valve 40. Useless oil consumption can be suppressed.

  Therefore, according to the second embodiment, it is possible to reduce the amount of oil supplied from the discharge port 22b of the oil pump 20 to the input port B1 of the regulator valve 40, and thus to reduce the discharge amount of the oil pump 20. Since the driving loss of the automatic transmission is reduced, it is easy to contribute to the improvement of the fuel consumption performance of the vehicle.

  Also in the second embodiment, the specific configuration of the oil supply restriction unit 80 shown in FIGS. 10 to 12 is not particularly limited, but as an example of the structure of the oil supply restriction unit 80, the above-described oil supply restriction unit 150 (FIG. 9 (a) and FIG. 9 (b)) may be employed.

[Third Embodiment]
A hydraulic pressure supply device 210 for an automatic transmission according to a third embodiment will be described with reference to FIGS.

  Note that in the third embodiment, the description of the configuration common to the first embodiment is omitted, and the same reference numerals are given in FIGS. 13 to 15.

  As shown in FIG. 13, in the third embodiment, the feedback line 57 is connected to the first oil passage portion 58 and the second oil passage portion 59 (see FIGS. 1 to 3) connected in parallel in the first embodiment. Instead, a first oil passage portion 257 and a second oil passage portion 258 connected in series with each other are provided.

  The first oil passage portion 257 and the second oil passage portion 258 are connected to each other via an oil supply restriction unit 280 as an oil supply restriction portion. The end of the first oil passage 257 opposite to the oil supply restriction unit 280 is connected to the output port C1 of the regulator valve 40, and the end of the second oil passage 258 opposite to the oil supply restriction unit 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 restriction unit 280.

  The oil supply restriction unit 280 includes a housing 281 having an oil passage space S2 therein, 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 feedback line 57. A second communication port 283 that allows the oil passage space S2 in the housing 281 to communicate with the second oil passage portion 258, and a third communication port 284 that allows the drain line 260 to communicate with the oil passage space S2 in the housing 281. Yes.

  The first communication port 282 and the second communication port 283 are disposed so as to face each other. 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 shape having a hole portion 291 that opens to the first communication port 282 side and a bottom portion 292 that closes the hole portion 291 from the second communication port 283 side. The outer peripheral surface of the relief valve 290 is disposed to face the third communication port 284.

  A spring 293 that biases the relief valve 290 toward the second communication port 283 is accommodated in the hole 291 of the relief valve 290. One or more grooves 294 extending in the axial direction are provided on the outer peripheral surface of the relief valve 290. The groove portion 294 communicates with the third communication port 284. The groove portion 294 is closed on the first communication port 282 side in the axial direction, and can communicate with the second communication port 283 according to the position of the relief valve 290.

  In a state where the groove portion 294 communicates with the second communication port 283, an oil passage portion extending from the second communication port 283 to the third communication port 284 through the groove portion 294 is formed in the oil passage space S2 in the housing 281. The The oil passage portion is connected to the drain line 260 at the third communication port 284, and the oil passage portion and the drain line 260 allow oil discharged from the control chamber 36 of the oil pump 20 to pass through the relief valve 290. A drain oil passage for draining is configured.

  An orifice 295 is provided in the bottom 292 of the relief valve 290 so as to penetrate therethrough, whereby the orifice 295 and the 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 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 through the internal space of the hole 291 and the orifice 295. The oil passage portion constitutes an oil passage portion that connects the first oil passage portion 257 and the second oil passage portion 258 in the feedback line 57.

  In the oil passage space S <b> 2 in the housing 281, the oil passage portion between the second communication port 283 and the bottom portion 292 of the relief valve 290 constitutes a connection portion 285 with the drain oil passage in the feedback line 57. Therefore, in the feedback line 57, the orifice 295 is disposed on the upstream side (the output port C1 side of the regulator valve 40) from the connection portion 285 with the drain oil passage.

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

  As shown in FIG. 14, when the oil pressure in the control chamber 36 of the oil pump 20 is reduced to increase the line pressure, the oil discharged from the control chamber 36 of the oil pump 20 is discharged from the second oil passage portion 258 of the feedback line 57. The oil flows from the control chamber 36 side toward the oil supply restriction unit 280 side. At this time, in the oil supply restriction unit 280, 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, 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 oil flow from the second communication port 283 side to the first communication port 282 side is restricted by the orifice 295, while the second communication port 283 side to the third communication port. Oil flow to the 284 side is promoted. Therefore, the oil discharged from the control chamber 36 to the feedback line 57 is smoothly drained through the relief valve 290 and the drain line 260. Thereby, since smooth and quick oil draining becomes possible, it is possible to obtain high responsiveness 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 feedback line 57 is connected to the control chamber of the oil pump 20 from the output port C1 side of the regulator valve 40. Oil flows toward the 36 side. At this time, in the oil supply restriction unit 280, the relief valve 290 moves to the second communication port 283 side by the hydraulic pressure supplied from the first communication port 282 side into the housing 281 and the urging force of the spring 293, and the relief valve The second communication port 283 is blocked by the bottom portion 292 of the 290. As a result, the oil flowing from the first communication port 282 to the second communication port 283 always passes through the orifice 295.

  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 295 of the oil supply limiting unit 280, thereby limiting the oil supply to the control chamber 36. The pressure can be gradually lowered. For this reason, hunting of the line pressure is suppressed, and the line pressure is easily stabilized at a desired pressure at an early stage.

  In addition, according to the third embodiment, since the entire feedback line 57 is configured by the oil passage portions 257 and 258 connected in series, the oil passage portions 58 and 58 in parallel as in the first and second embodiments. Compared with the case where 59 (refer FIG.1 and FIG.10) is provided, the oil path structure of the feedback line 57 can be simplified.

  In the third embodiment, the configuration of the oil supply restriction unit 280 described above is merely an example, and various changes can be made to the configuration of the oil supply restriction unit. For example, a spool valve that performs the same function as the oil supply restriction unit 280 described above may be provided on the feedback line 57.

  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 above-described embodiment, 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 and specific configurations of the variable displacement oil pump are as follows. There is no particular limitation as long as the oil pressure in the control chamber of the oil pump is increased to lower the discharge pressure and the pressure in the control chamber is decreased to increase the discharge pressure. .

  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 achieve both improvement in response to increase in line pressure and stabilization. There is a possibility of being suitably used in the manufacturing industry field of an automatic transmission equipped 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 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 (throttle means)
80 Oil supply restriction part 81 Orifice 82 Check valve 110 Hydraulic supply device 150 Oil supply restriction unit 260 Drain line 280 Oil supply restriction unit 290 Relief valve 295 Orifice A1 First control port A2 Second control port B1 First input port C1 Output port (output) Part)
D1 Drain port

Claims (5)

A variable displacement oil pump that generates hydraulic pressure used for controlling an automatic transmission, a regulator valve that adjusts the discharge pressure of the oil pump to a line pressure, and the hydraulic pressure that is output from the output portion of the regulator valve A hydraulic pressure supply device for an automatic transmission comprising a feedback oil passage leading to a pump control chamber,
The oil pump is configured such that the discharge pressure decreases as the hydraulic pressure in the control chamber increases, and the discharge pressure increases as the hydraulic pressure in the control chamber decreases.
A hydraulic pressure supply device for an automatic transmission, wherein the feedback oil passage is provided with an oil supply restriction unit for restricting oil supply to the control chamber as compared with oil discharged from the control chamber. The feedback oil passage includes a first oil passage portion and a second oil passage portion connected in parallel to each other,
The oil supply restriction portion is provided in the first oil passage portion and the second oil passage portion, and a check that restricts passage of oil in a direction from the output portion side toward the control chamber side. The hydraulic pressure supply device for an automatic transmission according to claim 1, further comprising a valve.   The drain oil passage for draining oil from the feedback oil passage through a throttle means is connected to the output side portion of the feedback oil passage from the orifice and the check valve. 2. A hydraulic pressure supply device for an automatic transmission according to 2.   The regulator valve includes a drain port that drains oil discharged from the control chamber to the feedback oil passage in a state where output from the output unit is stopped and regulates drain when output from the output unit. The hydraulic pressure supply device for an automatic transmission according to claim 2. A drain oil passage for draining drained oil from the control chamber is connected to the feedback oil passage via a relief valve,
2. The hydraulic pressure of the automatic transmission according to claim 1, wherein the oil supply restriction portion includes an orifice provided on the output portion side of a connection portion with the drain oil passage in the feedback oil passage. Feeding device.

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