JP2019173929A - Hydraulic control device for continuously variable transmission - Google Patents

Abstract

To always satisfactorily reduce pulsations of a pulley pressure supplied to a pulley of a continuously variable transmission while suppressing complication of control and cost increase.SOLUTION: In a hydraulic control device for a continuously variable transmission, a hydraulic damper is connected to at least either one of a first oil passage, which connects a first solenoid valve and a first pressure regulating valve, and a second oil passage, which connects a second solenoid valve and a second pressure regulating valve. In at least either one of the first and second oil passages, the oil flow resistance between the first or second solenoid valve and the oil inlet/outlet of the hydraulic damper is larger than the oil flow resistance between the oil inlet/outlet of the hydraulic damper and the first or second pressure regulating valve.SELECTED DRAWING: Figure 3

Description

  The present disclosure relates to a hydraulic control device for a continuously variable transmission that includes a primary pulley, a secondary pulley, and a belt that is wound around the primary pulley and the secondary pulley to transmit torque.

  Conventionally, belt-type continuously variable transmissions include a hydraulic control valve that controls pulley pressure to a primary pulley and a secondary pulley, and a controller that sets a base current command value to be output to a solenoid of the hydraulic control valve. (For example, refer to Patent Document 1). The controller of this continuously variable transmission has a predetermined differential pressure between the maximum peak pressure and the minimum peak pressure of at least one pulley pressure in order to suppress oil vibration judder generated in the drive shaft due to pulsation of pulley pressure. When the state equal to or greater than the value continues for a predetermined time, it is considered that the oil vibration that pulsates the pulley pressure has occurred, and a dither current is added to the base current command value. That is, in the continuously variable transmission described in Patent Document 1, by adding a dither current to the base current command value to the solenoid of the hydraulic control valve, the solenoid movable portion of the hydraulic control valve is moved in the dynamic friction region, An attempt is made to suppress the pulsation of pulley pressure by reducing the sliding resistance in the solenoid moving part and improving the response of the hydraulic system. Further, in the continuously variable transmission described in Patent Document 1, the base current command value is considered in consideration of the risk of side effects due to the decrease in the durability of the hydraulic control valve caused by moving the solenoid moving part in the dynamic friction region and the addition of a dither current. On the other hand, the range in which the dither current is applied is limited to the operation scene where the necessary conditions are satisfied.

JP 2017-223244 A

  However, it is not easy to add a dither current to the base current command value to the solenoid of the hydraulic control valve to satisfactorily suppress pulley pressure pulsation. This will increase the cost of the machine. In addition, if the range in which the dither current is added to the base current command value is limited to an operation scene where the necessary conditions are satisfied, an operation scene in which oil vibration judder is generated remains, and the continuously variable transmission It is not preferable for improving the performance and quality. Furthermore, in the continuously variable transmission described in Patent Document 1, the pulley pressure is directly regulated by a hydraulic control valve (solenoid valve), but it is required to supply a large amount of hydraulic fluid instantaneously to the pulley. When the pulley pressure is directly regulated by the hydraulic control valve in the continuously variable transmission, it is necessary to increase the size of the hydraulic control valve, which increases the cost and the size of the device. When a pressure regulating valve that regulates the original pressure based on the signal pressure from the solenoid valve to generate the pulley pressure is used, even if a dither current is added to the base current command value, the pulsation of the pulley pressure It is difficult to sufficiently suppress this.

  Therefore, the main object of the present disclosure is to always satisfactorily reduce the pulsation of the pulley pressure supplied to the pulley of the continuously variable transmission while suppressing complication of control and cost increase.

  A hydraulic control device for a continuously variable transmission according to the present disclosure is a hydraulic control device for a continuously variable transmission that includes a primary pulley, a secondary pulley, and a belt that is wound around the primary pulley and the secondary pulley to transmit torque. A primary solenoid valve that generates a first signal pressure; a second solenoid valve that generates a second signal pressure; and a primary pressure that is adjusted based on the first signal pressure from the first solenoid valve, A first pressure regulating valve that generates a first pulley pressure to the pulley, and a source pressure is adjusted based on the second signal pressure from the second solenoid valve to generate a second pulley pressure to the secondary pulley. A second pressure regulating valve, a first oil passage connecting the first solenoid valve and the first pressure regulating valve, and the second solenoid valve and the second pressure regulating valve. A second oil passage and a hydraulic damper connected to at least one of the first and second oil passages, and an oil inlet / outlet port of the hydraulic damper and at least one of the first and second solenoid valves Is greater than the oil flow resistance between the oil inlet / outlet of the hydraulic damper and at least one of the first and second pressure regulating valves.

  The present inventors have intensively studied to reduce the pulsation of the pulley pressure supplied to the pulley of the continuously variable transmission, and as a result, the pulsation of the first and second pulley pressures supplied to the primary pulley and the secondary pulley. Is superimposed on the first and second signal pressures in the first oil passage connecting the first solenoid valve and the first pressure regulating valve and in the second oil passage connecting the second solenoid valve and the second pressure regulating valve. Focused on. The present inventors then attenuate the vibration of the oil in the first and second oil passages so that the pulsation of the first and second pulley pressures on the first and second signal pressures is suppressed. It has been found that the pulsation of the first and second pulley pressures can always be satisfactorily reduced. Based on such research results, in the hydraulic control device of the present disclosure, a hydraulic damper is connected to at least one of the first and second oil passages, and the first or second solenoid valve and the oil inlet / outlet of the hydraulic damper are connected to each other. Is determined to be larger than the oil flow resistance between the oil inlet / outlet of the hydraulic damper and the first or second pressure regulating valve. As a result, according to the hydraulic control device of the present disclosure, the pulsation of the first and second pulley pressures supplied to the pulley of the continuously variable transmission can be constantly reduced satisfactorily while suppressing control complexity and cost increase. It becomes possible.

It is a schematic block diagram of the vehicle carrying the power transmission device containing the hydraulic control apparatus of the continuously variable transmission of this indication. It is a schematic block diagram of the power transmission device containing the hydraulic control apparatus of this indication. It is a systematic diagram showing a hydraulic control device of this indication. (A) And (b) is a graph which shows a mode that a primary sheave pressure and a secondary sheave pressure change during the action | operation of a continuously variable transmission. (A) And (b) is a graph which shows a mode that a primary sheave pressure and a secondary sheave pressure change during the action | operation of a continuously variable transmission.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram of a vehicle 10 equipped with a power transmission device 20 including a hydraulic control device 70 of a continuously variable transmission 40 according to the present disclosure. A vehicle 10 shown in the figure is a front wheel drive vehicle having an engine (internal combustion engine) 12 mounted on the front portion of the vehicle, and transmits a power from the engine 12 to left and right drive wheels (front wheels) DW. In addition to 20, an engine electronic control unit (hereinafter referred to as “EG ECU”) 14 that controls the engine 12 and a brake electronic control unit (hereinafter referred to as “brake ECU”) 16 that controls an electronically controlled hydraulic brake unit (not shown) 16. And a shift electronic control unit (hereinafter referred to as “TMECU”) 21 for controlling the power transmission device 20.

  The EGECU 14 includes a microcomputer (not shown) having a CPU, ROM, RAM, etc., various drive circuits, etc., and a crankshaft position sensor (not shown) for detecting the rotational position of the crankshaft of the engine 12 and the depression amount of the accelerator pedal 91 (accelerator opening) The accelerator pedal position sensor 92 for detecting the degree of acceleration (Acc), the master cylinder pressure sensor 94 for detecting the master cylinder pressure corresponding to the depression amount of the brake pedal 93, signals from various sensors such as the vehicle speed sensor 99, and the like from the brake ECU 16 and the TMECU 21 Input signals. Based on these signals, the EGECU 14 controls an electronically controlled throttle valve, fuel injection valve, spark plug, etc. (not shown). Further, the EGECU 14 calculates the rotational speed Ne of the engine 12 based on the detection value of the crankshaft position sensor.

  The brake ECU 16 also includes a microcomputer having a CPU, ROM, RAM, etc. (not shown), various drive circuits, and the like, and inputs signals from various sensors such as the master cylinder pressure sensor 94 and the vehicle speed sensor 99, signals from the EGECU 14, and the like. Based on these signals, the brake ECU 16 controls a brake actuator (hydraulic actuator) (not shown) and the like.

  The TMECU 21 also includes a microcomputer (not shown) having a CPU, ROM, RAM, etc., various drive circuits, and the like, and a shift position sensor for detecting an operation position of the shift lever 95 for selecting a desired shift position from a plurality of shift positions. 96, a signal from various sensors such as an accelerator pedal position sensor 92 and a vehicle speed sensor 99, a signal from the EGECU 14 and the brake ECU 16, and the like are input. The TMECU 21 controls the power transmission device 20 based on these signals.

  As shown in FIG. 2, the power transmission device 20 is connected to the engine 12 that is horizontally disposed so that the crankshaft of the engine 12 and the left and right drive shafts 59 connected to drive wheels (not shown) are substantially parallel to each other. Is configured as a transaxle. As shown in FIGS. 1 and 2, the power transmission device 20 includes a housing (first case) 22a, a transaxle case (second case) 22b, and a rear case (third case) 22c that are integrally coupled. 22, a starting device 23 housed in the transmission case 22, a mechanical oil pump 30, a forward / reverse switching mechanism 35, a belt-type continuously variable transmission (hereinafter referred to as “CVT”) 40, and a gear mechanism 50. , A differential gear (differential mechanism) 57, a hydraulic control device 70, and the like.

  The starting device 23 is configured as a fluid starting device having a lock-up function, and is accommodated in the housing 22a. As shown in FIG. 2, the starting device 23 includes a pump impeller 23p connected to the crankshaft of the engine 12 via a front cover 23f as an input member, and a turbine runner 23t always connected to the input shaft 41 of the CVT 40. A stator 23s disposed inside the pump impeller 23p and the turbine runner 23t to rectify the flow of hydraulic fluid (ATF) from the turbine runner 23t to the pump impeller 23p; a one-way clutch 23o that restricts the rotational direction of the stator 23s in one direction; It has a damper mechanism 24, a lock-up clutch 25, and the like. The pump impeller 23p, the turbine runner 23t, and the stator 23s function as a torque converter by the action of the stator 23s when the rotational speed difference between the pump impeller 23p and the turbine runner 23t is large, and function as a fluid coupling when the rotational speed difference between the two decreases. To do. However, in the starting device 23, the stator 23s and the one-way clutch 23o may be omitted, and the pump impeller 23p and the turbine runner 23t may function as only a fluid coupling.

  For example, the damper mechanism 24 is connected to the input element connected to the lockup clutch 25, the intermediate element connected to the input element via the plurality of first elastic bodies, and connected to the intermediate element via the plurality of second elastic bodies. And an output element fixed to the turbine hub. The lockup clutch 25 selectively locks up and releases the lockup that mechanically connects the pump impeller 23p and the turbine runner 23t, that is, the front cover 23f and the input shaft 41 of the CVT 40 (via the damper mechanism 24). To be executed. The lockup clutch 25 may be a hydraulic single-plate friction clutch as shown in the figure, or a hydraulic multi-plate friction clutch.

  The oil pump 30 includes a pump assembly including a pump body 31 and a pump cover 32 disposed between the starting device 23 and the forward / reverse switching mechanism 35, an inner rotor (external gear) 33, and an outer rotor (internal gear). 34 is a so-called gear pump. The pump body 31 and the pump cover 32 are fixed to the housing 22a and the transaxle case 22b. The inner rotor 33 is connected to the pump impeller 23p through a hub. As a result, when the inner rotor 33 is rotated by the power from the engine 12, the hydraulic oil (ATF) in the oil pan (hydraulic oil storage unit) 60 is sucked through the strainer 65 and boosted by the oil pump 30. The hydraulic oil is supplied (discharged) to the hydraulic control device 70 (see FIG. 3).

  The forward / reverse switching mechanism 35 is housed in the transaxle case 22b, and includes a double pinion planetary gear 36, a clutch C1 as a hydraulic friction engagement element, and a brake B1. The planetary gear 36 includes a sun gear fixed to the input shaft 41 of the CVT 40, a ring gear, a pinion gear meshing with the sun gear, and a carrier supporting the pinion gear meshing with the ring gear and coupled to the primary shaft 42 of the CVT 40. The clutch C1 releases the carrier of the planetary gear 36 so as to be rotatable with respect to the input shaft 41 (sun gear), and when the hydraulic pressure from the hydraulic control device 70 is supplied to the engagement oil chamber, the carrier is removed from the input shaft 41. Connect to. Further, the brake B1 releases the ring gear of the planetary gear 36 so as to be rotatable with respect to the transaxle case 22b, and when the hydraulic pressure from the hydraulic control device 70 is supplied to the engagement oil chamber, the brake B1 transmits the ring gear to the transaxle case. It is fixed so that it cannot rotate with respect to 22b.

  Thus, when the brake B1 is released and the clutch C1 is engaged, the power transmitted to the input shaft 41 can be transmitted to the primary shaft 42 of the CVT 40 as it is to advance the vehicle. If the brake B1 is engaged and the clutch C1 is released, the rotation of the input shaft 41 is converted in the reverse direction and transmitted to the primary shaft 42 of the CVT 40, and the vehicle can be moved backward. Furthermore, if the clutch C1 and the brake B1 are released, the connection between the input shaft 41 and the primary shaft 42 can be released.

  The CVT 40 includes a primary pulley 43 provided on a primary shaft (first axis) 42 as a driving side rotation axis, and a secondary shaft (second axis) 44 as a driven side rotation axis arranged in parallel with the primary shaft 42. A secondary pulley 45 provided, a transmission belt 46 wound around a pulley groove of the primary pulley 43 and a pulley groove of the secondary pulley 45, and a primary cylinder (hydraulic actuator for setting the groove width of the primary pulley 43) (First hydraulic cylinder) 47 and a secondary cylinder (second hydraulic cylinder) 48 that is a hydraulic actuator for setting the groove width of the secondary pulley 45. The primary pulley 43 includes a fixed sheave 43a formed integrally with the primary shaft 42, and a movable sheave 43b supported by the primary shaft 42 so as to be slidable in the axial direction via a ball spline. The secondary pulley 45 is supported by a fixed sheave 45a formed integrally with the secondary shaft 44, and is supported by the secondary shaft 44 through a ball spline so as to be slidable in the axial direction, and by a return spring 49 which is a compression spring. And a movable sheave 45b biased in the direction.

  The primary cylinder 47 is formed behind the movable sheave 43 b of the primary pulley 43, and the secondary cylinder 48 is formed behind the movable sheave 45 b of the secondary pulley 45. The primary cylinder 47 and the secondary cylinder 48 are supplied with hydraulic pressure from the hydraulic control device 70 in order to set the groove width between the primary pulley 43 and the secondary pulley 45. Thus, by controlling the hydraulic pressure supplied to the primary cylinder 47 and the secondary cylinder 48, the power transmitted from the engine 12 to the primary shaft 42 via the starting device 23 and the forward / reverse switching mechanism 35 is steplessly changed. Thus, it is possible to transmit to the secondary shaft 44. The power transmitted to the secondary shaft 44 is transmitted to the left and right drive wheels via the gear mechanism 50, the differential gear 57, and the drive shaft.

  The gear mechanism 50 includes a counter drive gear 51 that rotates integrally with the secondary shaft 44, and a counter shaft that extends in parallel with the secondary shaft 44 and the drive shaft 59 and is rotatably supported by the transmission case 22 via a bearing. (Third axis) 52, a counter driven gear 53 fixed to the counter shaft 52 and meshing with the counter drive gear 51, and a drive pinion gear (molded integrally with the counter shaft 52 or fixed to the counter shaft 52) A final drive gear) 54 and a differential ring gear (final driven gear) 55 that meshes with the drive pinion gear 54 and is connected to the differential gear 57.

  FIG. 3 is a system diagram showing a main part of the hydraulic control device 70. As shown in the figure, the hydraulic control device 70 is connected to the above-described oil pump 30 that is driven by power from the engine 12 and sucks and discharges hydraulic oil from the oil pan 60 through the strainer 65. is there. As shown in FIG. 3, the hydraulic control device 70 includes a valve body 700 having a plurality of oil passages, a primary regulator valve 71, a modulator valve 72, a first linear solenoid valve SLP, a second linear solenoid valve SLS, a primary A sheave pressure control valve (first pressure regulating valve) 73, a secondary sheave pressure control valve (second pressure regulating valve) 74, a first hydraulic damper 75, a second hydraulic damper 76, and the like are included.

  The primary regulator valve 71 is connected to the discharge port of the oil pump 30 through an oil passage, and moves forward and backward by adjusting the hydraulic oil from the oil pump 30 based on a signal pressure from a signal pressure output valve (not shown). A line pressure PL that is a source pressure of the hydraulic pressure supplied to the clutch C1, the brake B1, the primary cylinder 47, the secondary cylinder 48, and the like of the switching mechanism 35 is generated. As the signal pressure output valve of the primary regulator valve 71, for example, a shuttle valve that selects and outputs the higher one of the hydraulic pressures output from the first and second linear solenoid valves SLP, SLS, or a modulator valve 72 ( A linear solenoid valve that adjusts hydraulic oil from the oil pump 30 side) and outputs a hydraulic pressure corresponding to the accelerator opening Acc of the vehicle 10 or the opening of the throttle valve is used. Further, the modulator valve 72 adjusts (decreases) the hydraulic oil (line pressure PL) from the primary regulator valve 71 to generate a substantially constant modulator pressure Pmod.

  The first linear solenoid valve SLP is a normally open solenoid valve, and adjusts hydraulic oil from the modulator valve 72 (oil pump 30 side) based on the current value applied to the electromagnetic part to adjust the first signal pressure Pslp. Is generated. As shown in FIG. 3, the first linear solenoid valve SLP includes an input port I communicating with a supply oil passage for a modulator pressure Pmod formed in the valve body 700, in addition to an electromagnetic part, a spool, a spring, and the like. An output port O communicating with the first oil passage L1 formed in 700, and a feedback port F communicating with the first oil passage L1 (output port O) via the oil passage L1f formed in the valve body 700. . That is, the first linear solenoid valve SLP regulates the first signal pressure Pslp while feeding back the first signal pressure Pslp output from the output port O to the feedback port F.

  The second linear solenoid valve SLS is a normally-open solenoid valve, and adjusts hydraulic fluid from the modulator valve 72 (oil pump 30 side) based on the current value applied to the electromagnetic part to adjust the second signal pressure Psls. Is generated. As shown in FIG. 3, the second linear solenoid valve SLS includes an input port I communicating with a supply oil passage for the modulator pressure Pmod formed in the valve body 700 in addition to an electromagnetic part, a spool, a spring, and the like. An output port O communicating with the first oil passage L1 formed in 700, and a feedback port F communicating with the second oil passage L2 (output port O) via the oil passage L2f formed in the valve body 700. . That is, the second linear solenoid valve SLS regulates the second signal pressure Psls while feeding back the second signal pressure Psls output from the output port O to the feedback port F.

  The primary sheave pressure control valve 73 regulates the line pressure PL based on the first signal pressure Pslp from the first linear solenoid valve SLP, and the primary sheave pressure (first pulley pressure) Pp to the primary pulley 43, that is, the primary cylinder 47. Is generated. As shown in FIG. 3, the primary sheave pressure control valve 73 includes a spool 730 disposed in the valve body 700 so as to be movable in the axial direction, a spring 732 for biasing the spool 730, an input port 73i, and an output port. 73o, a signal pressure input port 73s, and a feedback port 73f.

  The spool 730 has two lands formed at intervals in the axial direction. The spring 732 is disposed in a spring chamber 735 that is defined on the opposite side of the two lands of the spool 730, and biases the spool 730 upward in FIG. The input port 73 i is formed so as to communicate with the space between the two lands of the spool 730 and communicates with a supply oil passage for the line pressure PL formed in the valve body 700. The output port 73o communicates with the hydraulic oil inlet of the primary cylinder 47 via an oil passage L3 formed in the valve body 700. The signal pressure input port 73s communicates with the spring chamber 735 and also communicates with the output port O of the first linear solenoid valve SLP via the first oil passage L1 formed in the valve body 700. The feedback port 73f faces a pressure receiving surface formed at the two land side ends of the spool 730 and communicates with an oil passage L3 connecting the output port 73o and the hydraulic oil inlet of the primary cylinder 47.

  When the primary sheave pressure control valve 73 is attached, the spool 730 is biased upward in FIG. 3 by the spring 732, that is, opposite to the spring chamber 735, and the input port 73 i and the output port 73 o are It communicates completely through the space between lands. When the line pressure PL is supplied to the input port 73i in the attached state (the left half state in the figure), the line pressure PL is supplied as the feedback pressure to the feedback port 73f, and the spool 730 is biased by the spring 732. Against this, it moves to the spring chamber 735 side so as to close the input port 73i. Accordingly, the first signal pressure Pslp is adjusted by the first linear solenoid valve SLP, the thrust applied to the spool 730 by the action of the first signal pressure Pslp, the biasing force of the spring 732, and the action of the feedback pressure are applied to the spool 730. By balancing the applied thrust, the primary sheave pressure Pp can be adjusted to a desired value while instantaneously supplying a large flow rate of hydraulic oil to the primary cylinder 47. That is, the primary sheave pressure control valve 73 feedbacks the primary sheave pressure Pp output from the output port 73o to the feedback port 73f based on the first signal pressure Pslp from the first linear solenoid valve SLP. Adjust Pp.

  The secondary sheave pressure control valve 74 regulates the line pressure PL based on the second signal pressure Psls from the second linear solenoid valve SLS, and the secondary sheave pressure (second pulley pressure) Ps to the secondary pulley 45, that is, the secondary cylinder 48. Is generated. As shown in FIG. 3, the secondary sheave pressure control valve 74 includes a spool 740 that is movably disposed in the axial direction in the valve body 700, a spring 742 that biases the spool 740, an input port 74i, and an output port. 74o, a signal pressure input port 74s, and a feedback port 74f.

  The spool 740 has two lands formed at intervals in the axial direction. The spring 742 is disposed in a spring chamber 745 that is defined on the opposite side of the two lands of the spool 740, and biases the spool 740 upward in FIG. The input port 74 i is formed so as to communicate with the space between the two lands of the spool 740 and communicates with a supply oil passage for the line pressure PL formed in the valve body 700. The output port 74o communicates with the hydraulic oil inlet of the secondary cylinder 48 via an oil passage L4 formed in the valve body 700. The signal pressure input port 74 s communicates with the spring chamber 745 and also communicates with the output port O of the second linear solenoid valve SLS via the second oil passage L <b> 2 formed in the valve body 700. The feedback port 74f faces a pressure receiving surface formed at the two land-side ends of the spool 740 and communicates with an oil passage L4 connecting the output port 74o and the hydraulic oil inlet of the secondary cylinder 48.

  In the attached state of the secondary sheave pressure control valve 74, the spool 740 is biased upward in FIG. 3 by the spring 742, that is, opposite to the spring chamber 745, and the input port 74i and the output port 74o are It communicates completely through the space between lands. When the line pressure PL is supplied to the input port 74i in this attached state (the left half state in the figure), the line pressure PL is supplied as a feedback pressure to the feedback port 74f, and the spool 740 is biased by the spring 742. Against this, it moves to the spring chamber 745 side so as to close the input port 74i. Accordingly, the second signal pressure Psls is adjusted by the second linear solenoid valve SLS, and the thrust applied to the spool 740 by the action of the second signal pressure Psls, the urging force of the spring 742, and the action of the feedback pressure are applied to the spool 740. By balancing the applied thrust, the secondary sheave pressure Pp can be adjusted to a desired value while instantaneously supplying a large flow rate of hydraulic oil to the secondary cylinder 48. That is, the secondary sheave pressure control valve 74 feedbacks the secondary sheave pressure Ps output from the output port 74o to the feedback port 74f based on the second signal pressure Psls from the second linear solenoid valve SLS. Adjust Ps.

  The first hydraulic damper 75 includes a piston P that is disposed in the valve body 700 so as to be movable in the axial direction so as to define an oil chamber together with the valve body 700, and a spring SP that biases the piston P. . As shown in FIG. 3, the hydraulic oil outlet Dio of the first hydraulic damper 75 is connected to the output port O of the first linear solenoid valve SLP and the primary sheave pressure control valve 73 via an oil passage L5 formed in the valve body 700. Is connected to the first oil passage L1 that connects to the signal pressure input port 73s.

  The second hydraulic damper 76 also includes a piston P disposed in the valve body 700 so as to be movable in the axial direction so as to define an oil chamber together with the valve body 700, and a spring SP that biases the piston P. . As shown in FIG. 3, the hydraulic oil outlet Dio of the second hydraulic damper 76 is connected to the output port O of the second linear solenoid valve SLS and the secondary sheave pressure control valve 74 via an oil passage L <b> 6 formed in the valve body 700. Is connected to the second oil passage L2 that connects to the signal pressure input port 74s. The first and second hydraulic dampers 75 and 76 may have a dedicated case for accommodating the piston P and the spring SP.

  Both the first and second linear solenoid valves SLP and SLS described above are controlled by the TMECU 21. The CPU of the TMECU 21 corresponds to both of them so that currents corresponding to the first and second signal pressures Pslp and Psls are applied from the auxiliary battery (not shown) to the electromagnetic parts of the first and second linear solenoid valves SLP and SLS. The drive circuit (not shown) is controlled. More specifically, the TMECU 21 sets the target pressure Pptag of the primary sheave pressure Pp according to the target gear ratio of the CVT 40 determined from the accelerator opening Acc, the vehicle speed V, and the rotational speed Ne of the engine 12, and sets the target pressure Ppttag to the target pressure Ppttag. Based on this, the target value of the first signal pressure Pslp is set. Further, the TMECU 21 controls a drive circuit (not shown) of the first linear solenoid valve SLP so that a current corresponding to the target value is applied. Thereby, primary sheave pressure control valve 73 generates primary sheave pressure Pslp corresponding to the target gear ratio of CVT 40.

  Further, the TMECU 21 is configured such that the slip of the transmission belt 46 of the CVT 40 is suppressed by the secondary sheave pressure Ps based on the torque transmitted to the input shaft 41 (for example, the estimated value of the output torque of the engine 12 transmitted from the EGECU 14). The target belt clamping pressure Psag, which is the target pressure of the secondary sheave pressure Ps, is set, and the target value of the second signal pressure Psls is set based on the target belt clamping pressure Psag. Furthermore, the TMECU 21 controls a drive circuit (not shown) of the second linear solenoid valve SLS so that a current corresponding to the target value is applied. Thereby, the secondary sheave pressure control valve 74 generates a secondary sheave pressure Ps corresponding to the clamping pressure to be applied to the transmission belt 46 from the secondary pulley 45 (the fixed sheave 45a and the movable sheave 45b).

  Now, when the belt-type CVT 40 as described above is operating, the primary sheave pressure Pp regulated by the primary sheave pressure control valve 73 and the secondary sheave pressure regulated by the secondary sheave pressure control valve 74. Low frequency (for example, about 1-2 Hz) pulsation may occur in Ps. Such pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps mainly occurs when the primary sheave pressure Pp and the secondary sheave pressure Ps are changed, and the amplitude of the pulsation increases as the amount of change of both increases. . Therefore, in order to improve the performance and quality of the CVT 40 and the NV performance of the vehicle 10 equipped with the CVT 40, it is necessary to reduce the pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps. However, a practical and useful means for reducing the pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps has not been provided so far.

  The inventors have conducted intensive research and analysis to reduce the pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps supplied to the primary pulley 43 and the secondary pulley 45 of the CVT 40 by modifying the hardware. As a result of research and analysis, the present inventors have found that the pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps is the first oil passage L1 that connects the first linear solenoid valve SLP and the primary sheave pressure control valve 73, Attention was focused on the first and second signal pressures Pslp and Psls in the second oil passage L2 connecting the second linear solenoid valve SLS and the secondary sheave pressure control valve 74.

  For example, when the secondary sheave pressure Ps regulated by the secondary sheave pressure control valve 74 pulsates, vibration of the spool 740 due to the pulsation or the secondary sheave pressure Ps is supplied as feedback pressure from the oil passage L4 to the feedback port 74f. As a result, the hydraulic oil in the spring chamber 745 vibrates (pulsates). As a result, the hydraulic oil in the second oil passage L2 also vibrates (pulsates), and the second signal pressure Psls is fed back from the second oil passage L2 to the feedback port F so that it is output from the second linear solenoid valve SLS. The pulsation of the secondary sheave pressure Ps is superimposed on the second signal pressure Psls. Such a phenomenon can also occur on the primary sheave pressure control valve 73 and the first oil passage L1 side as well.

  The present inventors assume that such vibration coupling is one of the main factors of the pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps. First, the first and second linear solenoid valves SLP, SLS are used. The first and second hydraulic dampers 75 and 76 are connected to the first and second oil passages L1 and L2 so as to attenuate the vibrations of the first and second signal pressures Pslp and Psls output from the primary sheave pressure Pp. And the vibration state of the secondary sheave pressure Ps was confirmed. At this time, the first oil passage is so promoted that the hydraulic oil output from the first and second linear solenoid valves SLP, SLS is promoted to flow into the hydraulic oil inlet / outlet Dio of the first and second hydraulic dampers 75, 76. The signal pressure of the junction of L1 and the oil passage L5 and the signal pressure input port 73s of the primary sheave pressure control valve 73 and the junction of the second oil passage L2 and the oil passage L6 and the signal pressure of the secondary sheave pressure control valve 74 An orifice was installed between the input port 74s. Each orifice has an oil passage area of the first or second oil passage L1, L2, an oil passage area of the oil passage L5 or L6, an opening area of the hydraulic oil inlet / outlet Dio of the first or second hydraulic damper 75, 76, and a signal. The opening area is smaller than the opening area of the pressure input port 73s or 74s.

  However, even if the vibrations of the first and second signal pressures Pslp and Psls output from the first and second linear solenoid valves SLP and SLS are attenuated by the first and second hydraulic dampers 75 and 76 as described above, the primary When the first and second signal pressures Pslp and Psls are changed so that the sheave pressure Pp and the secondary sheave pressure Ps change, the primary sheave pressure Pp and the secondary sheave pressure Ps are relatively reduced as shown in FIG. A large pulsation occurred. Further, when the amount of change in the first and second signal pressures Pslp and Psls is increased, the pulsation amplitudes of the primary sheave pressure Pp and the secondary sheave pressure Ps become very large as shown in FIG. .

  After obtaining such a result, the present inventors conduct further research and analysis so that the pulsation of the primary sheave pressure Pp or the secondary sheave pressure Ps on the first and second signal pressures Pslp and Psls is suppressed. Further, it has been found that the pulsation of the primary sheave pressure Pp and the secondary sheave pressure Ps can always be satisfactorily reduced by attenuating the vibration of the hydraulic oil in the first and second oil passages L1, L2. That is, the present inventors connect the first or second hydraulic dampers 75 and 76 to the first and second oil passages L1 and L2 in the hydraulic control device 70 described above, and the first linear solenoid valve SLP and the first hydraulic solenoid valve SLP. The oil flow resistance between the hydraulic oil inlet / outlet Dio of the first hydraulic damper 75 is larger than the oil flow resistance between the hydraulic oil inlet / outlet Dio and the primary sheave pressure control valve 73, and the second linear solenoid valve SLS and the first The oil flow resistance between the hydraulic oil inlet / outlet Dio of the hydraulic damper 75 is made larger than the oil flow resistance between the hydraulic oil inlet / outlet Dio and the primary sheave pressure control valve 73.

  When the first and second signal pressures Pslp and Psls are changed so that the primary sheave pressure Pp and the secondary sheave pressure Ps change in the hydraulic control device 70 in which such measures are taken, FIG. As shown, the pulsation amplitudes of the primary sheave pressure Pp and the secondary sheave pressure Ps are significantly smaller than the configuration corresponding to FIG. Further, when the amount of change in the first and second signal pressures Pslp and Psls is increased, the pulsation amplitudes of the primary sheave pressure Pp and the secondary sheave pressure Ps are as shown in FIG. 5 (b). Compared to the configuration corresponding to, it was significantly smaller.

  Based on such research results, in the hydraulic control device 70 of the present embodiment, the first linear solenoid valve SLP of the first oil passage L1 and the hydraulic oil inlet / outlet Dio of the first hydraulic damper 75 are more specifically described. An oil flow resistance is instantaneously generated between the merging portion between the first oil passage L1 and the oil passage L1f and the hydraulic oil inlet / outlet Dio (the merging portion between the first oil passage L1 and the oil passage L5) of the first hydraulic damper 75. A first orifice 77 to be increased is installed. Further, in the hydraulic control device 70, between the second linear solenoid valve SLS of the second oil passage L2 and the hydraulic oil inlet / outlet Dio of the second hydraulic damper 76, more specifically, the second oil passage L2 and the oil passage L2f, The second orifice 78 that instantaneously increases the oil flow resistance is installed between the merging portion and the hydraulic oil inlet / outlet Dio (the merging portion between the second oil passage L2 and the oil passage L6) of the second hydraulic damper 76. The

  The opening area of the first orifice 77 is the oil passage area of the first oil passage L1 (at least the range downstream from the junction with the oil passage L5), the oil passage area of the oil passage L5, and the operation of the first hydraulic damper 75. The opening area of the oil outlet / inlet Dio and the opening area of the signal pressure input port 73 s of the primary sheave pressure control valve 73 are smaller. In addition, the opening area of the second orifice 78 includes the oil passage area of the second oil passage L2 (at least the range downstream from the junction with the oil passage L6), the oil passage area of the oil passage L6, and the second hydraulic damper 76. The opening area of the hydraulic oil inlet / outlet Dio and the opening area of the signal pressure input port 74s of the secondary sheave pressure control valve 74 are smaller.

  Thereby, in the first hydraulic damper 75, the piston P moves in the vertical direction in FIG. 3 according to the vibration (pulsation) of the hydraulic oil in the spring chamber 735 of the primary sheave pressure control valve 73 (the volume of the oil chamber varies). By doing so, the vibration (pulsation) of the hydraulic oil in the spring chamber 735 is absorbed and attenuated. Similarly, in the second hydraulic damper 76, the piston P moves in the vertical direction in FIG. 3 according to the vibration (pulsation) of the hydraulic oil in the spring chamber 745 of the secondary sheave pressure control valve 74 (the volume of the oil chamber varies). By doing so, the vibration (pulsation) of the hydraulic oil in the spring chamber 745 is absorbed and attenuated. As a result, the first and second hydraulic dampers 75 and 76 suppress the superposition of the pulsation of the primary sheave pressure Pp or the secondary sheave pressure Ps to the first and second signal pressures Pslp and Psls. It becomes possible to attenuate the vibration of the hydraulic oil in the oil passages L1, L2.

  Further, the increase in the cost of the hydraulic control device 70 due to the additional installation of the first and second hydraulic dampers 75 and 76 and the first and second orifices 77 and 78 is controlled by the control of the hydraulic control device 70 and the primary sheave pressure Pp and the secondary. Compared to the development cost for reducing the pulsation of the sheave pressure Ps and the increase in the cost due to the increase in the specifications of the ECU, the cost is significantly reduced. Therefore, according to the hydraulic control device 70, the primary sheave pressure Pp and the secondary sheave are controlled regardless of the magnitude relationship and the magnitude of the change in the primary sheave pressure Pp and the secondary sheave pressure Ps while suppressing the complicated control and cost increase. Both pulsations of the sheave pressure Ps can be reduced extremely well.

  Further, by using the first and second orifices 77 and 78, oil flow resistance between the first or second linear solenoid valves SLP and SLS and the hydraulic oil inlet / outlet Dio of the first or second hydraulic dampers 75 and 76 is achieved. In addition, the oil flow resistance between the hydraulic oil inlet / outlet Dio and the primary sheave pressure control valve 73 or the secondary sheave pressure control valve 74 can be set more appropriately. However, in order to adjust these oil flow resistances, a plurality of orifices may be used, or a throttle mechanism other than the orifices may be employed. For example, the area of the oil passage of the valve body 700 is locally changed ( (Decrease).

  In the belt-type CVT 40, the secondary sheave pressure Ps applied to the secondary pulley 45 in order to apply the clamping pressure to the transmission belt 46 is often higher than the primary sheave pressure Ps. Further, since the primary pulley 43 and the secondary pulley 45 are connected to each other via the transmission belt 46, the pulsation of the primary sheave pressure Pp or the secondary sheave pressure Ps is reduced in either the primary pulley 43 or the secondary pulley 45. By doing so, the pulsation of the primary sheave pressure Pp or the secondary sheave pressure Ps can be reduced also on the other side. Therefore, the first hydraulic damper 75 and the first orifice 77 may be omitted from the hydraulic control device 70, and also in the hydraulic control device 70, the pulsations of the primary sheave pressure Pp and the secondary sheave pressure Ps are always reduced satisfactorily. Is possible. Further, the second hydraulic damper 76 and the second orifice 78 may be omitted from the hydraulic control device 70. In the hydraulic control device 70, the first and second linear solenoid valves SLP, SLS may be replaced with duty solenoid valves. Further, the opening area of the first and second orifices 77 and 78 is within an allowable range of pressure drop due to the leakage amount of hydraulic oil when the wear amount of the spools 730 and 740 and the valve body 700 is a predetermined limit wear amount. It may be a value determined to be within.

  As described above, the hydraulic control device for a continuously variable transmission according to the present disclosure is wound around a primary pulley (43), a secondary pulley (45), the primary pulley (43), and the secondary pulley (45). In the hydraulic control device (70) of the continuously variable transmission (40) including the belt (46) for transmitting torque, the first solenoid valve (SLP) for generating the first signal pressure (Pslp) and the second signal A second solenoid valve (SLS) that generates a pressure (Psls), and a primary pressure (PL) that is regulated based on the first signal pressure (Pslp) from the first solenoid valve (SLP) to adjust the primary pulley ( 43) based on the first pressure regulating valve (73) for generating the first pulley pressure (Pp) and the second signal pressure (Psls) from the second solenoid valve (SLS). The second pressure regulating valve (74) for regulating the original pressure (PL) to generate the second pulley pressure (Ps) to the secondary pulley (45), the first solenoid valve (SLP), and the first A first oil passage (L1) connecting the pressure regulating valve (73); a second oil passage (L2) connecting the second solenoid valve (SLS) and the second pressure regulating valve (74); A hydraulic damper (75, 76) connected to at least one of the first and second oil passages (L1, L2), and the at least one of the first and second oil passages (L1, L2). Thus, the oil flow resistance between the first or second solenoid valve (SLP, SLS) and the oil inlet / outlet (Dio) of the hydraulic damper (75, 76) is the oil resistance of the hydraulic damper (75, 76). Doorway (Dio) and the first or second In which it is larger than the oil passing resistance between the pressure valve (73, 74).

  The present inventors have intensively studied to reduce the pulsation of the pulley pressure supplied to the pulley of the continuously variable transmission, and as a result, the pulsation of the first and second pulley pressures supplied to the primary pulley and the secondary pulley. Is superimposed on the first and second signal pressures in the first oil passage connecting the first solenoid valve and the first pressure regulating valve and in the second oil passage connecting the second solenoid valve and the second pressure regulating valve. Focused on. The present inventors then attenuate the vibration of the oil in the first and second oil passages so that the pulsation of the first and second pulley pressures on the first and second signal pressures is suppressed. It has been found that the pulsation of the first and second pulley pressures can always be satisfactorily reduced. Based on such research results, in the hydraulic control device of the present disclosure, a hydraulic damper is connected to at least one of the first and second oil passages, and the first or second solenoid valve and the oil inlet / outlet of the hydraulic damper are connected to each other. Is determined to be larger than the oil flow resistance between the oil inlet / outlet of the hydraulic damper and the first or second pressure regulating valve. As a result, according to the hydraulic control device of the present disclosure, the pulsation of the first and second pulley pressures supplied to the pulley of the continuously variable transmission can be constantly reduced satisfactorily while suppressing control complexity and cost increase. It becomes possible.

  Further, the first or second solenoid valve (SLP, SLS) of at least one of the first and second oil passages (L1, L2) and the oil inlet / outlet (Dio) of the hydraulic damper (75, 76) Orifices (77, 78) for increasing the oil flow resistance may be installed between the two. Thereby, the oil flow resistance between the first or second solenoid valve and the oil inlet / outlet of the hydraulic damper, and the oil flow resistance between the oil inlet / outlet of the hydraulic damper and the first or second pressure regulating valve are more appropriate. It becomes possible to set to.

  Furthermore, the opening area of the orifice (77, 78) may be smaller than the opening area of the signal pressure input port (73s, 74s) of the first or second pressure regulating valve (73, 74). As a result, the vibration of the oil in the first and second oil passages can be attenuated so that the pulsation of the first and second pulley pressures on the first and second signal pressures is suppressed by the hydraulic damper. Become.

  The second pressure regulating valve (SLS) generates the second pulley pressure (Ps) corresponding to the clamping pressure to be applied to the belt (46) from the secondary pulley (45). The oil inlet / outlet (Dio) of the hydraulic damper (76) is connected to the second oil passage (L2) between the second solenoid valve (SLS) and the second pressure regulating valve (74). May be. That is, the pulsation of the first and second pulley pressures is mainly generated when the first and second pulley pressures are changed, and the pulsation amplitude increases as the amount of change in the first and second pulley pressures increases. Become. In general, the second pulley pressure applied to the second pulley in order to apply the clamping pressure to the belt is often higher than the first pulley pressure. Furthermore, the primary pulley and the secondary pulley Therefore, if the pulsation of the first or second pulley pressure is reduced in one of the primary pulley and the secondary pulley, the pulsation of the first or second pulley pressure is also reduced in the other. be able to. Therefore, a hydraulic damper is connected to the second oil passage corresponding to the secondary pulley to attenuate the vibration of the oil in the second oil passage so that the pulsation of the second pulley pressure on the second signal pressure is suppressed. However, the pulsation of the first and second pulley pressures can always be satisfactorily reduced.

  Further, the first pressure regulating valve (SLP) may generate the first pulley pressure (Pp) according to a target gear ratio of the continuously variable transmission (40), and the hydraulic damper ( 75) The oil outlet / inlet (Dio) may be connected to the first oil passage (L1) between the first solenoid valve (SLP) and the first pressure regulating valve (73). In this way, by connecting a hydraulic damper to the first oil passage corresponding to the primary pulley, the vibration of the oil in the first oil passage is damped so that the pulsation of the first pulley pressure on the first signal pressure is suppressed. Even in this case, the pulsations of the first and second pulley pressures can always be satisfactorily reduced.

  The first pressure regulating valve may be configured such that (SLP) generates the first pulley pressure (Pp) corresponding to a target speed ratio of the continuously variable transmission (40). The two pressure regulating valve (SLS) may generate the second pulley pressure (Ps) corresponding to the clamping pressure to be applied from the secondary pulley (45) to the belt (46), The hydraulic damper may include a first hydraulic damper (75) connected to the first oil path (L1) and a second hydraulic damper (76) connected to the second oil path (L2), An oil outlet / inlet (Dio) of the first hydraulic damper (75) is connected to the first oil passage (L1) between the first solenoid valve (SLP) and the first pressure regulating valve (73). The oil inlet / outlet (Dio) of the second hydraulic damper (76) may be Serial may be connected to the second oil passage (L2) between the second solenoid valve (SLS) and the second pressure regulating valve (74). Thereby, regardless of the magnitude relationship between the first and second pulley pressures and the magnitude of the amount of change, it is possible to reduce both the pulsations of the first and second pulley pressures very well.

  Further, the first and second solenoid valves (SLP, SLS) feed back the first or second signal pressure while feeding back the first or second signal pressure (Pslp, Psls) output from the output port (O). Pressures (Pslp, Psls) may be regulated, and the first and second pressure regulating valves (73, 74) are the first or second pulleys output from the output ports (73o, 74o). The first or second pulley pressure (Pp, Ps) may be regulated while feeding back the pressure (Pp, Ps).

  And the invention of this indication is not limited to the above-mentioned embodiment at all, and it cannot be overemphasized that various changes can be made within the range of the extension of this indication. Furthermore, the above-described embodiment is merely a specific form of the invention described in the Summary of Invention column, and does not limit the elements of the invention described in the Summary of Invention column.

  The invention of the present disclosure can be used in the manufacturing industry of belt-type continuously variable transmissions.

  10 vehicle, 12 engine, 14 engine electronic control unit (EGECU), 16 brake electronic control unit brake (brake ECU), 20 power transmission device, 21 transmission electronic control unit (TMECU), 22 transmission case, 22a housing, 22b transaxle Case, 22c Rear case, 23 Starter, 23b Turbine runner, 23f Front cover, 23o One-way clutch, 23p Pump impeller, 23s Stator, 23t Turbine runner, 24 damper mechanism, 25 Lock-up clutch, 30 Oil pump, 31 Pump body, 32 Pump cover, 33 inner rotor, 34 outer rotor, 35 forward / reverse switching mechanism, 36 planetary gear, 40 continuously variable transmission (CVT), 41 imp Shaft, 42 primary shaft, 43 primary pulley, 43a fixed sheave, 43b movable sheave, 44 secondary shaft, 45 secondary pulley, 45a fixed sheave, 45b movable sheave, 46 transmission belt, 47 primary cylinder, 48 secondary cylinder, 49 return spring, 50 gear mechanism, 51 counter drive gear, 52 counter shaft, 53 counter driven gear, 54 drive pinion gear, 55 diff ring gear, 57 differential gear, 59 drive shaft, 60 oil pan, 65 strainer, 70 hydraulic control device, 71 primary regulator valve, 72 Modulator valve, 73 Primary sheave pressure control valve, 74 Secondary sheave pressure control valve, 75 Hydraulic damper, 76 Second hydraulic damper, 77 First orifice, 78 Second orifice, 91 Accelerator pedal, 92 Accelerator pedal position sensor, 93 Brake pedal, 94 Master cylinder pressure sensor, 95 Shift lever, 96 Shift position sensor, 99 Vehicle speed Sensor, 700 Valve body, B1 brake, C1 clutch, Dio hydraulic oil inlet / outlet, F feedback port, I input port, L1 first oil passage, L2 second oil passage, L1f, L2f, L3, L4, L5, L6, O Output port, P piston, SLP first linear solenoid valve, SLS second linear solenoid valve, SP spring.

Claims (7)

In a hydraulic control device for a continuously variable transmission, including a primary pulley, a secondary pulley, and a belt wound around the primary pulley and the secondary pulley to transmit torque,
A first solenoid valve for generating a first signal pressure;
A second solenoid valve for generating a second signal pressure;
A first pressure regulating valve that regulates an original pressure based on the first signal pressure from the first solenoid valve to generate a first pulley pressure to the primary pulley;
A second pressure regulating valve that regulates an original pressure based on the second signal pressure from the second solenoid valve to generate a second pulley pressure to the secondary pulley;
A first oil passage connecting the first solenoid valve and the first pressure regulating valve;
A second oil passage connecting the second solenoid valve and the second pressure regulating valve;
A hydraulic damper connected to at least one of the first and second oil passages,
The oil flow resistance between the oil inlet / outlet of the hydraulic damper and at least one of the first and second solenoid valves is at least one of the oil inlet / outlet of the hydraulic damper and the first and second pressure regulating valves. A hydraulic control device for a continuously variable transmission that is larger than an oil flow resistance between the one and the other. The hydraulic control device for a continuously variable transmission according to claim 1,
An orifice for increasing the oil flow resistance is installed between the first or second solenoid valve of at least one of the first and second oil passages and the oil inlet / outlet of the hydraulic damper. Hydraulic control device for step transmission. The hydraulic control device for a continuously variable transmission according to claim 2,
The hydraulic control device for a continuously variable transmission, wherein an opening area of the orifice is smaller than an opening area of a signal pressure input port of the first or second pressure regulating valve. In the hydraulic control apparatus for a continuously variable transmission according to any one of claims 1 to 3,
The second pressure regulating valve generates the second pulley pressure according to a clamping pressure to be applied to the belt from the secondary pulley,
The oil pressure control device for a continuously variable transmission, wherein the oil inlet / outlet of the hydraulic damper is connected to the second oil passage between the second solenoid valve and the second pressure regulating valve. In the hydraulic control apparatus for a continuously variable transmission according to any one of claims 1 to 3,
The first pressure regulating valve generates the first pulley pressure according to a target gear ratio of the continuously variable transmission,
The oil pressure control device for a continuously variable transmission, wherein the oil outlet / inlet of the hydraulic damper is connected to the first oil passage between the first solenoid valve and the first pressure regulating valve. In the hydraulic control apparatus for a continuously variable transmission according to any one of claims 1 to 3,
The first pressure regulating valve generates the first pulley pressure according to a target gear ratio of the continuously variable transmission,
The second pressure regulating valve generates the second pulley pressure according to a clamping pressure to be applied to the belt from the secondary pulley,
The hydraulic damper includes a first hydraulic damper connected to the first oil passage, and a second hydraulic damper connected to the second oil passage,
An oil inlet / outlet port of the first hydraulic damper is connected to the first oil passage between the first solenoid valve and the first pressure regulating valve,
The oil pressure control device for a continuously variable transmission, wherein an oil inlet / outlet port of the second hydraulic damper is connected to the second oil passage between the second solenoid valve and the second pressure regulating valve. The hydraulic control device for a continuously variable transmission according to any one of claims 1 to 6,
The first and second solenoid valves regulate the first or second signal pressure while feeding back the first or second signal pressure output from an output port;
The first and second pressure regulating valves are hydraulic control devices for continuously variable transmissions that regulate the first or second pulley pressure while feeding back the first or second pulley pressure output from an output port.

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