JP2017053397A - Hydraulic control system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a miniaturized hydraulic control system.SOLUTION: A hydraulic control system 10 includes an oil pump 50, a first hydraulic control body 30a, a second hydraulic control body 20a, and a pressure reduction block 40. The first hydraulic control body 30a and the second hydraulic control body 20a include an in-port into which oil flows, an out-port for supplying the oil flowing from the in-port to an actuator, a solenoid valve 66 for controlling the oil supplied to the actuator from the out-port, and a control device for controlling the solenoid valve 66. The out-port of the first hydraulic control body 30a is connected with a first actuator AC1. The out-port of the second hydraulic control body 20a is connected with a second actuator AC2. The oil pressure-reduced by the pressure reduction block 40 is supplied to the in-port of the second hydraulic control body 20a. A first casing 31 of the first hydraulic control body 30a and a second casing 21 of the second hydraulic control body 20a are separated members with each other.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a hydraulic control system.

  Conventionally, a control valve that controls a controlled body such as an automatic transmission mounted on a vehicle by hydraulic pressure is known. For example, in the control valve of Patent Document 1, a plurality of electromagnetic control valves are all incorporated into one dedicated body.

JP 2001-263466 A

  In the control valve as described above, driving of a plurality of actuators is controlled. Here, when the required hydraulic pressure is different for each of the plurality of actuators, the oil having the highest hydraulic pressure among the required hydraulic pressures is supplied to the assembly of the electromagnetic control valves, and is appropriately decompressed and distributed to each electromagnetic control valve. . Therefore, when the controlled body has an actuator that requires a relatively high oil pressure, the oil pressure of the oil supplied to the assembly of the electromagnetic control valves becomes relatively high. As a result, the pressure resistance performance of the assembly of electromagnetic control valves needs to be relatively high, and there is a problem that the assembly of electromagnetic control valves tends to be large.

  Further, since a plurality of electromagnetic control valves are incorporated in one dedicated body, there is a problem that the degree of freedom of arrangement of the electromagnetic control valves is low, and the assembly of the electromagnetic control valves tends to be large.

  In view of the above problems, an aspect of the present invention is to provide a hydraulic control system having a structure that can be reduced in size.

  A hydraulic control system according to one aspect of the present invention is a hydraulic control system that controls, by hydraulic pressure, a controlled body that is mounted on a vehicle and has a plurality of actuators, and includes an oil pump and oil supplied from the oil pump. A first hydraulic control body that controls hydraulic pressure and supplies the hydraulic pressure to the actuator; and a pressure-reducing block that is connected to the oil pump and reduces the hydraulic pressure of the oil. And the second hydraulic pressure control body controls an import into which the oil flows, an out port that supplies the oil that has flowed in from the import to the actuator, and the oil that is supplied from the out port to the actuator. An electromagnetic valve; and a control device that controls the electromagnetic valve, wherein the actuator includes a first actuator. An outta of the first hydraulic control body is connected to the first actuator, and the outport of the second hydraulic control body is connected to the second actuator. The oil that has been decompressed by the decompression block is supplied to the import of the second hydraulic control body, and the first housing of the first hydraulic control body and the second housing of the second hydraulic control body, Are separate members.

  According to one aspect of the present invention, a hydraulic control system having a structure that can be miniaturized is provided.

FIG. 1 is a schematic diagram illustrating a schematic configuration of a hydraulic control system according to the present embodiment. FIG. 2 is a diagram illustrating a part of the controlled body. FIG. 3 is a schematic diagram showing the hydraulic control body of the present embodiment. FIG. 4 is a schematic diagram showing the hydraulic control body of the present embodiment. FIG. 5 is a diagram showing an opening / closing operation of the flow control valve of the present embodiment. FIG. 6 is a schematic diagram illustrating a schematic configuration of a hydraulic control system which is another example of the present embodiment.

  Hereinafter, a hydraulic control system according to an embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, a hydraulic control system 10 according to the present embodiment controls a controlled body CB mounted on a vehicle and having a plurality of actuators by hydraulic pressure. In the following description, a case where the controlled body CB is a continuously variable transmission (CVT) will be described as an example.

  The plurality of actuators included in the controlled body CB include a first actuator AC1 and a second actuator AC2. In FIG. 1, for example, one first actuator AC1 is provided, and three second actuators AC2 are provided, for example.

  The first actuator AC1 is, for example, a pulley drive actuator. That is, the controlled body CB has a pulley drive actuator. The second actuator AC2 is, for example, a forward / reverse switching actuator, a high / low gear switching actuator, a torque converter lockup control actuator, or the like.

  As shown in FIG. 2, the controlled body CB, which is a continuously variable transmission, includes two pulleys PL1 and PL2 and a belt BE that connects the two pulleys PL1 and PL2. The first actuator AC1, which is a pulley drive actuator, changes the lateral widths L1, L2 of the pulleys PL1, PL2. Thereby, the diameter of the pulley PL1 on which the belt BE is engaged and the diameter of the pulley PL2 can be changed, and a continuous continuously variable transmission can be realized.

  As shown in FIG. 1, the hydraulic control system 10 includes an oil pump 50, a supply oil passage 11, discharge oil passages 14a and 14b, a hydraulic control module 30, a hydraulic control assembly 20, a control unit 70, Is provided. The control unit 70 controls the hydraulic control system 10 as a whole. The control unit 70 controls a control device 63 of the first hydraulic control body 30a described later and a control device 63 of the second hydraulic control body 20a described later.

  The oil pump 50 pressurizes the oil O in the oil tank OT and supplies it to the hydraulic control assembly 20 and the hydraulic control module 30. The oil O pressurized by the oil pump 50 flows into the supply oil passage 11. In FIG. 1, the oil pump 50 is disposed at a position close to the hydraulic control assembly 20 among the hydraulic control module 30 and the hydraulic control assembly 20.

  The supply oil passage 11 includes a first supply oil passage 12 that connects the oil pump 50 and the hydraulic control assembly 20, and a second supply oil passage 13 that connects the first supply oil passage 12 and the hydraulic control module 30. . The drain oil passage 14a connects the hydraulic control module 30 and the oil tank OT. The drain oil passage 14b connects the hydraulic control assembly 20 and the oil tank OT.

  The hydraulic control module 30 has one first hydraulic control body 30 a and a first housing 31. The hydraulic control assembly 20 includes a plurality of second hydraulic control bodies 20 a, a pressure reducing circuit 22, and a second housing 21. That is, the hydraulic control system 10 includes a first hydraulic control body 30a and a second hydraulic control body 20a. In FIG. 1, the hydraulic control assembly 20 includes, for example, three second hydraulic control bodies 20a.

  The first hydraulic control body 30a and the second hydraulic control body 20a control the hydraulic pressure of the oil O supplied from the oil pump 50 and supply it to the actuator. As shown in FIG. 3, the first hydraulic control body 30 a and the second hydraulic control body 20 a include an import 32, an outport 33, a control device 63, an electromagnetic valve 66, and a flow rate control valve 68.

  Oil O flows into the import 32. Oil O flows from the second supply oil passage 13 into the import 32 of the first hydraulic control body 30a. Oil O flows from the decompression circuit 22 into the import 32 of the second hydraulic control body 20a.

  The out port 33 is connected to the actuator, and supplies the oil O introduced from the import 32 to the actuator. The out port 33 of the first hydraulic control body 30a is connected to the first actuator AC1. The out port 33 of the second hydraulic control body 20a is connected to the second actuator AC2.

  The control device 63 controls the electromagnetic valve 66. The electromagnetic valve 66 controls the oil O supplied from the out port 33 to the actuator. In the present embodiment, the electromagnetic valve 66 controls the flow rate of the oil O supplied from the out port 33 to the actuator via the flow rate control valve 68.

  The decompression circuit 22 shown in FIG. 1 decompresses the oil pressure of the oil O supplied from the oil pump 50, distributes it, and supplies it to each second hydraulic control body 20a. In FIG. 1, the decompression circuit 22 includes a decompression block 40. That is, the hydraulic control system 10 includes a pressure reducing block 40. The decompression block 40 is attached to the hydraulic control assembly 20.

  The decompression block 40 is connected to the oil pump 50 through the first supply oil passage 12. The decompression block 40 reduces the oil pressure of the oil O. Thereby, the oil O decompressed by the decompression block 40 is supplied to the import 32 of each second hydraulic control body 20a.

  The decompression block 40 preferably has, for example, a decompression valve. This is because the oil pressure of the oil O flowing into the decompression block 40 can be suitably and simply reduced. The configuration of the pressure reducing valve is not particularly limited, and any known pressure reducing valve may be used. The configuration of the decompression block 40 is not particularly limited as long as the oil O can be decompressed.

  The first housing 31 houses the first hydraulic control body 30a. The second housing 21 houses a plurality of second hydraulic control bodies 20a and a pressure reducing circuit 22. The first casing 31 of the first hydraulic control body 30a and the second casing 21 of the second hydraulic control body 20a are separate members.

  Therefore, the oil O from the oil pump 50 can be separately supplied to the first hydraulic control body 30a and the second hydraulic control body 20a. As a result, relatively high pressure oil O pressurized by the oil pump 50 is supplied to the first hydraulic control body 30a through the second supply oil passage 13, while the second hydraulic control body 20a is reduced in pressure. Oil O decompressed by the block 40 can be supplied.

  Therefore, for example, when the hydraulic pressure required to drive the second actuator AC2 is lower than the hydraulic pressure required to drive the first actuator AC1, the pressure resistance performance of the second hydraulic control body 20a is increased more than necessary. There is no need. Thereby, the pressure resistance performance of the second hydraulic control body 20a can be set to the pressure resistance performance corresponding to the relatively low hydraulic pressure required to drive the second actuator AC2. Therefore, the sealing structure of the second hydraulic control body 20a and the second casing 21 can be simplified, and the second hydraulic control body 20a and the second casing 21 can be reduced in size.

  In addition, since the first casing 31 and the second casing 21 are separate members, the size of the first casing 31 depends on the first hydraulic control body 30a and the second hydraulic control body 20a that are housed in each. It is easy to optimize the height and arrangement and the size and arrangement of the second housing 21. As a result, the first housing 31 and the second housing 21 can be easily downsized.

  As described above, according to the present embodiment, the hydraulic control system 10 having a structure that can be reduced in size can be obtained.

  For example, when the distance between the outport and the actuator is long, the oil pressure of the oil O adjusted by the hydraulic control body may be reduced before reaching the actuator from the outport. Moreover, when the sealing performance of the oil path connecting from the out port to the actuator is not sufficient, there is a possibility that the oil O leaks and the oil amount decreases. As a result, the responsiveness of the actuator may be reduced. In particular, this problem becomes more prominent as the oil pressure and amount of oil O required to drive the actuator are larger.

  On the other hand, by using the first casing 31 and the second casing 21 as separate members, the first hydraulic control body 30a (hydraulic control module 30) requires a relatively high hydraulic pressure and oil amount. It can be arranged in the vicinity of the first actuator AC1. Thereby, it can suppress that the oil_pressure | hydraulic and oil quantity of the oil O supplied to 1st actuator AC1 fall, and can improve the responsiveness of 1st actuator AC1.

  In addition, in this specification, the 1st housing | casing 31 and the 2nd housing | casing 21 are mutually separate members, if the 1st housing | casing 31 and the 2nd housing | casing 21 are not a single member, The first housing 31 and the second housing 21 may be disposed at positions separated from each other, or the first housing 31 and the second housing 21 may be in direct or indirect contact. .

  The case where the first casing 31 and the second casing 21 are in indirect contact with each other is, for example, the case where the first casing 31 and the second casing 21 are attached to the same member such as a plate. Including. In this embodiment, the 1st housing | casing 31 and the 2nd housing | casing 21 are arrange | positioned in the position which left | separated, for example.

  Further, in this specification, the first casing 31 and the second casing 21 contain the hydraulic control body in the first casing 31 and the second casing 21 at least a part of the hydraulic control body. And the hydraulic control body may be held by the first casing 31 and the second casing 21.

  A hydraulic control assembly 20 having a plurality of second hydraulic control bodies 20 a is accommodated in one second housing 21. Therefore, when a plurality of second actuators AC2 that are driven at a relatively low oil pressure are provided, a plurality of second hydraulic control bodies 20a can be arranged in one place. Thereby, the arrangement of the first hydraulic control body 30a and the plurality of second hydraulic control bodies 20a can be easily optimized, and the hydraulic control system 10 can be further downsized.

  Further, since the pressure-reducing block 40 is attached to the hydraulic control assembly 20, the oil O decompressed by the pressure-reducing block 40 can be easily supplied to each second hydraulic control body 20a. Further, by attaching the pressure reducing block 40 to the hydraulic control assembly 20, it is easier to reduce the size of the hydraulic control module 30 than when the pressure reducing block 40 is attached to the hydraulic control module 30. Thereby, it is easy to arrange the hydraulic control module 30 closer to the first actuator AC1. Therefore, the responsiveness of the first actuator AC1 can be further improved.

  Further, in the continuously variable transmission, driving of the pulley driving actuator that drives the pulleys PL1 and PL2 requires a particularly high hydraulic pressure as compared with other actuators. Therefore, in a continuously variable transmission, if a hydraulic control body that supplies oil O to the pulley drive actuator that drives the pulleys PL1 and PL2 is provided together with other hydraulic control bodies, the pressure resistance performance of the entire hydraulic control body must be particularly increased. As a result, the hydraulic control system tends to be particularly large. Further, since the distance between the hydraulic control body and the pulley drive actuator is increased, the oil O is depressurized and it is difficult to obtain the hydraulic pressure necessary for driving the pulley drive actuator.

  In addition, the pulley drive actuator has a particularly large flow rate of the oil O required for driving as compared with other actuators. Therefore, if the distance from the hydraulic control body to the pulley drive actuator increases and the flow rate of the oil O decreases, the responsiveness of the pulley drive actuator is particularly likely to decrease.

  According to the present embodiment, these problems can be solved by using the first actuator AC1 to which the first hydraulic control body 30a is connected as a pulley drive actuator. Therefore, the effect obtained by the hydraulic control system 10 of the present embodiment is particularly large when the controlled body CB is a continuously variable transmission and the first actuator AC1 is a pulley drive actuator.

  As shown in FIGS. 3 and 4, the first hydraulic control body 30a and the second hydraulic control body 20a include an oil passage member 61, a first cavity portion 61a, a second cavity portion 61b, a drain port 34, The connecting oil path 35, the pressure sensor 62a, the position sensor 62b, the communication device 64, and the connector 65 are included.

  As shown in FIG. 3, the oil passage member 61 is a member having an oil passage through which oil O passes. The oil passage member 61 is provided with a first cavity portion 61a, a second cavity portion 61b, an import 32, an out port 33, a drain port 34, and a connection oil passage 35.

  The first cavity portion 61a and the second cavity portion 61b are holes that open at one end and extend in one direction (left-right direction in FIG. 3). The import 32 is connected to both the first cavity portion 61a and the second cavity portion 61b.

  The electromagnetic valve 66 includes a first spool 67a, a first cavity portion 61a, and a solenoid 60. The first spool 67a has a columnar shape having an oil passage inside. The first spool 67a is disposed so as to be movable in the longitudinal direction (left-right direction in FIG. 3) in the first cavity portion 61a.

  The solenoid 60 is attached to the oil passage member 61. The solenoid 60 applies a force in the longitudinal direction (left-right direction in FIG. 3) to the first spool 67a when supplied with current. Although not shown, a spring that applies a longitudinal force to the first spool 67a is disposed in the first cavity 61a.

  When the magnitude of the current supplied to the solenoid 60 is changed, the force applied from the solenoid 60 to the first spool 67a changes, and the first spool 67a stops at a position that balances with the spring force. Thereby, the position of the longitudinal direction (left-right direction in FIG. 3) of the 1st spool 67a can be changed by changing the magnitude | size of the electric current supplied to the solenoid 60. FIG.

  The flow rate control valve 68 has a second spool 67b and a second cavity portion 61b. The second spool 67b has a columnar shape having an oil passage inside. The second spool 67b is disposed in the second cavity portion 61b so as to be movable in the longitudinal direction (left-right direction in FIG. 3).

  The drain port 34 connects the first cavity portion 61a and the second cavity portion 61b to the discharge oil passages 14a and 14b. The connection oil passage 35 connects the first cavity portion 61a and the second cavity portion 61b.

  The pressure sensor 62a shown in FIG. 4 detects the pressure of the oil O supplied from the out port 33 to the first actuator AC1 or the second actuator AC2. The configuration of the pressure sensor 62a is not particularly limited. The position sensor 62b detects the position of the flow control valve 68. More specifically, the position sensor 62b detects the position of the second spool 67b shown in FIG. 3 in the longitudinal direction (left-right direction in FIG. 3). The configuration of the position sensor 62b is not particularly limited.

  As shown in FIG. 4, the output signal of the pressure sensor 62 a and the output signal of the position sensor 62 b are input to the control device 63. The control device 63 calculates the flow rate of the oil O supplied from the outport 33 to the first actuator AC1 or the second actuator AC2 based on the output signal of the pressure sensor 62a and the output signal of the position sensor 62b.

  Therefore, it is easy to detect a change in the flow rate of the oil O supplied to the actuator. Thereby, it is easy to appropriately control the flow rate of the oil O supplied to the first actuator AC1 and the second actuator AC2, and the responsiveness of the first actuator AC1 and the second actuator AC2 can be further improved.

  The communication device 64 receives an electrical signal from the control unit 70 via the connector 65 and transmits it to the control device 63. Further, the communication device 64 transmits an electrical signal from the control device 63 to the control unit 70 via the connector 65. The electrical signal from the control device 63 is, for example, an output signal of the pressure sensor 62a, an output signal of the position sensor 62b, and a signal indicating the flow rate of the oil O supplied to the first actuator AC1 or the second actuator AC2. is there.

  As shown in FIG. 3, when receiving an electrical signal from the control unit 70, the control device 63 supplies a current to the electromagnetic valve 66 based on the electrical signal. The position of the first spool 67a in the longitudinal direction changes in accordance with the electrical signal, and the opening between the connection oil passage 35 and the flow path of the first spool 67a and the opening between the import 32 and the first spool 67a are controlled.

  Thereby, the pressure of the oil O flowing from the connection oil passage 35 to the second cavity 61b is controlled, and as a result, the position of the second spool 67b is controlled. Thus, the electromagnetic valve 66 converts the electrical signal input from the control device 63 into a hydraulic signal, and the flow control valve 68 having the second spool 67b is controlled based on the hydraulic signal.

  As described above, the flow rate of the oil O supplied to the first actuator AC1 or the second actuator AC2 is controlled by the electromagnetic valve 66 and the flow rate control valve 68. An example of the opening / closing operation of the flow control valve 68 is shown in FIGS. 5 (A) to 5 (C). 5A to 5C show the case of the first hydraulic control body 30a.

  When the current is not supplied to the solenoid valve 66 or the current supplied to the solenoid valve 66 is small, as shown in FIG. 5A, in the flow control valve 68, the import 32 and the out port 33 are connected. It is. As a result, the oil O that has flowed in from the second supply oil passage 13 via the import 32 passes through the oil passage in the second spool 67b and is supplied to the first actuator AC1 via the outport 33. As a result, the first actuator AC1 is driven.

  When the current supplied to the solenoid valve 66 increases, the oil O flows from the connection oil passage 35 into the second cavity 61b, and as shown in FIG. 5B, the second spool 67b is on one side in the longitudinal direction (see FIG. Move to the right in 5 (B). As a result, the import 32 is closed. When the state shown in FIG. 5A is shifted to the state shown in FIG. 5B, the amount of oil O supplied to the actuator increases as the current supplied to the electromagnetic valve 66 increases. Becomes a linear function. In this state, since the oil pressure of the oil O in the first actuator AC1 is kept constant, the first actuator AC1 remains driven.

  When the current supplied to the solenoid valve 66 is further increased, the amount of oil O flowing into the second cavity 61b from the connection oil passage 35 is further increased, and the second spool 67b is further moved to one side in the longitudinal direction (FIG. 5 ( In C), move to the right). Thereby, the out port 33 and the drain port 34 are connected, and the oil O supplied to the first actuator AC1 is discharged to the oil tank OT via the drain port 34 and the discharge oil passage 14a. As a result, the driving of the first actuator AC1 is stopped.

  When the first actuator AC1 is driven again, the current supplied to the electromagnetic valve 66 is reduced, and the second spool 67b is moved to the other side in the longitudinal direction (the left side in FIG. 5C). The state shown in A) is set. As a result, the oil O is supplied again to the first actuator AC1, and the first actuator AC1 is driven.

  When returning from the state of FIG. 5C to the state of FIG. 5A again, the flow path in the first spool 67 a shown in FIG. 3 connects the connection oil path 35 and the drain port 34. As a result, the oil O that has flowed into the second cavity portion 61b from the connection oil passage 35 is discharged to the oil tank OT via the drain port 34 and the discharge oil passage 14a.

  The relationship between the magnitude of the current supplied to the solenoid valve 66 and the amount of oil O supplied to the actuator may change due to deterioration of the hydraulic control body over time. In such a case, for example, the relationship between the output of the position sensor 62b and the amount of oil O supplied to the actuator is stored, and the relationship between the sensor output and the amount of oil in the initial stage is referred to, so that the solenoid valve 66 is stored. The magnitude of the current supplied to can be corrected.

  For example, when controlling the flow rate of oil O supplied to the actuator only by opening and closing the solenoid valve, an actuator that requires a relatively high hydraulic pressure, such as a pulley drive actuator, requires a large force to move the spool of the solenoid valve. It becomes. Therefore, it is necessary to enlarge the solenoid, and there is a problem that the hydraulic control body is enlarged. There is also a problem that the manufacturing cost of the hydraulic control body increases.

  On the other hand, when the flow rate of the oil O supplied to the actuator is controlled by the electromagnetic valve 66 and the flow rate control valve 68, the electrical signal is converted into a hydraulic signal by the electromagnetic valve 66, and the flow rate control valve 68 is controlled by the hydraulic pressure. The second spool 67b can be moved. Therefore, even if the solenoid 60 of the electromagnetic valve 66 is small, the amount of oil O supplied to the actuator that requires a relatively high hydraulic pressure can be controlled. Therefore, it is possible to reduce the size of the hydraulic control body and suppress an increase in the manufacturing cost of the hydraulic control body.

  For example, when the hydraulic control body is provided in the vicinity of the oil tank OT, the oil O supplied to the first actuator AC1 and the oil O supplied to the second cavity 61b from the connection oil path 35 are supplied to the second cavity. It is also easy to spill directly from the part 61b and the first cavity part 61a to the oil tank OT and discharge.

  However, when the hydraulic control body is arranged at a position relatively distant from the oil tank OT as in the first hydraulic control body 30a, if the oil O is directly dropped from the first cavity portion 61a and the second cavity portion 61b. The oil O may not be properly discharged to the oil tank OT.

  On the other hand, according to the present embodiment, since the drain port 34 connected to the first cavity portion 61a and the second cavity portion 61b is provided, the inside of the first cavity portion 61a and the inside of the second cavity portion 61b. The oil O after use can be discharged efficiently. Therefore, the oil O can be discharged appropriately and smoothly.

  The present invention is not limited to the above-described embodiment, and other configurations can be employed. In the following description, the same configurations as those described above may be omitted by appropriately attaching the same reference numerals.

  The hydraulic control system 10 may have a configuration like the hydraulic control system 110 shown in FIG. As shown in FIG. 6, the hydraulic control module 130 includes a pressure reducing circuit 22. In this configuration, the decompression block 40 is attached to the first hydraulic control body 30a.

  The oil pump 150 supplies oil O to the decompression circuit 22 through the first supply oil passage 112. The oil O supplied to the pressure reducing circuit 22 is distributed to the oil O supplied to the first hydraulic control body 30a and the oil O supplied to the pressure reducing block 40. The oil O supplied to the decompression block 40 is decompressed and supplied to each second hydraulic control body 20a of the hydraulic control assembly 120 via the second supply oil passage 113. Unlike the hydraulic control assembly 20 described above, the hydraulic control assembly 120 is not provided with a pressure reducing circuit 22.

  In the hydraulic control system 110, the position of the oil pump 150 is different from that of the hydraulic control system 10 described above. The oil pump 150 is disposed at a position close to the hydraulic control module 130 in the hydraulic control module 130 and the hydraulic control assembly 120. That is, the first hydraulic control body 30a is disposed closer to the oil pump 150 than the position of the second hydraulic control body 20a.

  Therefore, it is easy to directly supply the oil O pressurized by the oil pump 150 to the first hydraulic control body 30a that supplies the oil O to the first actuator AC1 that requires a relatively high oil pressure, and the responsiveness of the first actuator AC1. Can be improved more.

  Further, by attaching the decompression block 40 to the first hydraulic control body 30a, the hydraulic pressure in the second supply oil passage 113 that sends the oil O to the second hydraulic control body 20a can be lowered. Therefore, the pressure resistance performance of the second supply oil passage 113 that is longer than the first supply oil passage 112 that connects the oil pump 150 and the first hydraulic control body 30a can be reduced. As a result, the configuration of the second supply oil passage 113 can be simplified, and the entire hydraulic control system 110 can be easily downsized.

  The number of actuators of the controlled body CB may be two, three, or five or more. The number of hydraulic control bodies that supply oil O to the actuator may be two, three, or five or more in accordance with the number of actuators.

  There may be two or more first hydraulic control bodies 30a. There may be one second hydraulic control body 20a. For example, one first hydraulic control body 30a and one second hydraulic control body 20a may be provided. In this case, two hydraulic control modules are configured. For example, a plurality of first hydraulic control bodies 30a and a plurality of second hydraulic control bodies 20a may be provided. In this case, two hydraulic control assemblies are configured.

  The flow rate control valve 68 may not be provided. In this case, only the operation of the electromagnetic valve 66 controls the flow rate of the oil O supplied to the actuator.

  The controlled body CB that is a control target of the hydraulic control system 10 is not particularly limited as long as it is mounted on a vehicle and includes a plurality of actuators. The controlled body CB may be an automatic transmission (AT) or a parking brake.

  The above-described configurations can be appropriately combined within a range that does not contradict each other.

  DESCRIPTION OF SYMBOLS 10,110 ... Hydraulic control system, 20, 120 ... Hydraulic control assembly, 20a ... Second hydraulic control body, 21 ... Second housing, 30a ... First hydraulic control body, 31 ... First housing, 32 ... Import , 33: Out port, 40: Pressure reducing block, 50, 150 ... Oil pump, 62a ... Pressure sensor, 62b ... Position sensor, 63 ... Control device, 66 ... Solenoid valve, 68 ... Flow control valve, AC1 ... First actuator, AC2 ... second actuator, BE ... belt, CB ... controlled body, O ... oil, PL1, PL2 ... pulley

Claims (9)

A hydraulic control system for controlling a controlled body mounted on a vehicle and having a plurality of actuators by hydraulic pressure,
An oil pump,
A first hydraulic control body and a second hydraulic control body that control oil pressure supplied from the oil pump and supply the oil to the actuator;
A decompression block connected to the oil pump and depressurizing the oil pressure;
With
The first hydraulic control body and the second hydraulic control body are:
The import into which the oil flows,
An outport for supplying the oil flowing from the import to the actuator;
A solenoid valve for controlling the oil supplied to the actuator from the outport;
A control device for controlling the solenoid valve;
Have
The actuator includes a first actuator and a second actuator,
The outport of the first hydraulic control body is connected to the first actuator;
The outport of the second hydraulic control body is connected to the second actuator;
The oil decompressed by the decompression block is supplied to the import of the second hydraulic control body,
The hydraulic control system, wherein the first casing of the first hydraulic control body and the second casing of the second hydraulic control body are separate members. A hydraulic control assembly having a plurality of the second hydraulic control bodies;
2. The hydraulic control system according to claim 1, wherein the hydraulic control assembly includes the second casing that houses a plurality of the second hydraulic control bodies.   The hydraulic control system according to claim 2, wherein the decompression block is attached to the hydraulic control assembly.   The hydraulic control system according to claim 1, wherein the pressure reducing block is attached to the first hydraulic control body. The controlled body is a continuously variable transmission having two pulleys, a belt connecting the two pulleys, and a pulley drive actuator that changes a groove width of the pulley.
The hydraulic control system according to any one of claims 1 to 4, wherein the first actuator is the pulley drive actuator.   6. The hydraulic control system according to claim 1, wherein the first hydraulic control body is disposed closer to the oil pump than a position of the second hydraulic control body. 7.   The hydraulic control system according to any one of claims 1 to 6, wherein the pressure reducing block includes a pressure reducing valve. The first hydraulic control body and the second hydraulic control body have a flow rate control valve that controls a flow rate of the oil supplied from the out port to the actuator,
The solenoid valve converts an electrical signal input from the control device into a hydraulic signal,
The hydraulic control system according to claim 1, wherein the flow control valve is controlled based on the hydraulic signal. The first hydraulic control body and the second hydraulic control body are:
A pressure sensor for detecting the pressure of the oil supplied to the actuator from the outport;
A position sensor for detecting the position of the flow control valve;
Have
The hydraulic control system according to claim 8, wherein the control device calculates a flow rate of the oil supplied from the outport to the actuator based on an output signal of the pressure sensor and an output signal of the position sensor. .

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