JP6615021B2 - Hydraulic control device - Google Patents

Description

  The present invention relates to a hydraulic control device.

  Generally, a transmission for a vehicle is provided with a hydraulically driven engagement device, and the hydraulic pressure supplied to the engagement device is controlled by a hydraulic control device. The hydraulic control device adjusts the oil discharged from the oil pump to a predetermined hydraulic pressure using, for example, a regulator valve, and further adjusts the hydraulic pressure using a pressure regulating valve, and then supplies the oil to the corresponding engagement device. Such a hydraulic control device is disclosed in, for example, Japanese Patent Application Laid-Open No. 2013-253653 (Patent Document 1).

  While the oil pump is stopped or while the hydraulic pressure supply from the pressure regulating valve to the engagement device is stopped, air may enter the hydraulic circuit from the part of the oil pump or pressure regulating valve that communicates with the atmosphere. is there. In such a case, when the engagement device is engaged next, the rise of the hydraulic pressure in the hydraulic circuit becomes unstable, and the responsiveness of the engagement control of the engagement device is lowered. For this reason, as shown in FIG. 10 schematically showing the internal hydraulic circuit of the hydraulic control device of Patent Document 1, for example, an air relief hole is provided in the hydraulic control device, and the air remaining in the hydraulic circuit is discharged into the air. It is conceivable that air drains from the escape hole.

  However, by performing such atmospheric drain, the discharge amount of the oil pump for securing the necessary oil amount is increased as compared with the case where the atmospheric drain is not performed. As a result, there has been a problem that the fuel consumption rate of a vehicle equipped with a transmission and a hydraulic control device is reduced.

JP 2013-253653 A

  It is desired to realize a hydraulic control device that can maintain high responsiveness of engagement control of an engagement device provided in a transmission for a vehicle without increasing the load of the oil pump.

The hydraulic control device according to the present disclosure is:
A hydraulic control device that controls the hydraulic pressure supplied to a hydraulically driven engagement device provided in a transmission for a vehicle,
The main oil passage that connects the oil pump and the pressure regulating valve that adjusts the hydraulic pressure supplied to the engagement device has an upper passage portion that passes through a position that is vertically above the pressure regulating valve, and
A sub oil passage branched from the main oil passage is provided upstream of the pressure regulating valve.

  According to this configuration, since the sub oil passage is provided on the upstream side (oil pump side) from the pressure regulating valve, even if air is mixed into the hydraulic circuit, the mixed air is led to the sub oil passage. Thus, it is possible to avoid air from reaching the pressure regulating valve arranged on the downstream side. In addition, since the main oil passage provided on the upstream side of the pressure regulating valve has an upper passage portion, even if the mixed air cannot be sufficiently guided to the sub oil passage, the remaining mixed air is captured by the upper passage portion. be able to. By these double air traps, it is possible to effectively avoid the air from reaching the pressure regulating valve disposed downstream and vertically below the upper passage portion. Therefore, the rising of the hydraulic pressure in the hydraulic circuit can be stabilized, and the responsiveness of the engagement control of the engagement device can be maintained high. At this time, since atmospheric draining is not performed, the responsiveness of the engagement control of the engagement device can be maintained high without increasing the load of the oil pump.

  Further features and advantages of the technology according to the present disclosure will become more apparent from the following description of exemplary and non-limiting embodiments described with reference to the drawings.

Schematic diagram of the transmission according to the embodiment Side view of hydraulic control device Schematic diagram of hydraulic control device Schematic diagram of the upper passage part of the main oil passage Schematic diagram of the upper passage part of the main oil passage of another aspect Schematic diagram of the upper passage part of the main oil passage of another aspect Schematic diagram of the upper passage part of the main oil passage of another aspect Schematic diagram of the upper passage part of the main oil passage of another aspect Schematic diagram of another aspect of hydraulic control device Schematic diagram of hydraulic control device according to background art

  An embodiment of a hydraulic control device will be described with reference to the drawings. In the present embodiment, the hydraulic control device 1 provided in the vehicle transmission 100 will be described as an example. The hydraulic control device 1 of the present embodiment is provided to control the hydraulic pressure supplied to the hydraulically driven engagement device CL provided in the transmission 100 (specifically, the automatic transmission mechanism TM).

  As shown in FIG. 1, the transmission 100 includes an input member I, a fluid coupling TC, an automatic transmission mechanism TM, and an output member O. These are accommodated in a case (drive device case) CS.

  The input member I is connected to the internal combustion engine EG so as to be able to transmit a driving force (hereinafter simply referred to as “drive connection”). The fluid coupling TC is drivingly connected to the input member I and the automatic transmission mechanism TM. The fluid coupling TC of the present embodiment is a torque converter that includes, for example, a pump impeller that is drivingly connected to the input member I, a turbine runner that is drivingly connected to the automatic transmission mechanism TM, and a stator disposed therebetween. . A torus part TR is constituted by the pump impeller and the turbine runner. The fluid coupling TC can transmit a driving force via oil (working oil, ATF: Automatic transmission fluid) circulating inside the torus part TR.

  The fluid coupling TC may be a fluid coupling including only a pump impeller and a turbine runner. The transmission 100 may further include a lockup clutch that integrally rotates the input member I and the turbine runner in the engaged state.

  The transmission 100 includes a mechanical oil pump OP that is drivingly connected to the input member I and the pump impeller. The oil pump OP is driven by the torque of the internal combustion engine EG that is drivingly connected to the input member I, and sucks oil (hydraulic oil, ATF) from an oil pan provided vertically downward in the case CS to obtain a predetermined pressure. Dispense it to a high level.

  The automatic transmission mechanism TM is configured as a stepped automatic transmission mechanism in the present embodiment. The automatic transmission mechanism TM of the present embodiment includes a plurality of planetary gear mechanisms (not shown) and a plurality of engagement devices CL. In the present embodiment, the planetary gear mechanism includes a single pinion type (or double pinion type) first planetary gear device and a Ravigneaux type second planetary gear device. The engagement device CL is a friction engagement device that transmits a driving force by pressing the friction plates between two rotating members. The engagement device CL includes a clutch (for example, a wet multi-plate clutch) and a brake. (For example, wet multi-plate brakes). In the present embodiment, the automatic transmission mechanism TM includes three clutches (first clutch, second clutch, third clutch) and two brakes (first brake, second brake) as the engagement device CL. Note that the automatic transmission mechanism TM may include one or more one-way clutches.

  As is well known, the automatic speed change mechanism TM has, for example, two engagement states among a plurality of engagement devices CL, and changes the gear position according to the combination of the engagement devices CL to be engaged. Form. The automatic transmission mechanism TM shifts the rotation input from the fluid coupling TC in accordance with the speed ratio of the formed gear (the ratio of the input rotation speed to the output rotation speed) and transmits the rotation to the output member O.

  The output member O is drivably coupled to a pair of left and right wheels via a counter gear mechanism and an output differential gear device (not shown).

  The hydraulic control device 1 is used to individually control the engagement state of a plurality of engagement devices CL provided in the automatic transmission mechanism TM to form a specific shift speed (target shift speed). The hydraulic control device 1 adjusts the oil discharged from the oil pump OP to a predetermined hydraulic pressure, and supplies the adjusted hydraulic pressure to the engagement device CL corresponding to the target shift stage. Further, the hydraulic control device 1 supplies oil discharged from the oil pump OP to a lubrication target portion such as a meshing portion between gears or a bearing, or to a cooling target portion such as a friction plate provided in the engagement device CL. Or supply. In the present embodiment, the hydraulic control device 1 is arranged side by side in the axial direction L with the input member I, the fluid coupling TC, and the automatic transmission mechanism TM in a standing posture along the vertical direction V (see FIG. 2). Yes. The hydraulic control device 1 is disposed on the side opposite to the internal combustion engine EG with respect to the automatic transmission mechanism TM.

  As shown in FIG. 2, the hydraulic control device 1 includes a valve body 20 and a plurality of linear solenoid valves SL1 to S15 that individually control the hydraulic pressure supplied to the plurality of engagement devices CL. A plurality of oil passages constituting a hydraulic circuit are formed in the valve body 20. In the present embodiment, the valve body 20 includes a first body 21, a second body 22, and a third body 23 that are arranged to overlap each other in the axial direction L. Further, the valve body 20 includes a first plate 24 disposed at a facing portion between the first body 21 and the second body 22, and a second plate disposed at a facing portion between the second body 22 and the third body 23. 25. The oil passages formed in the first body 21, the second body 22, and the third body 23 communicate with each other through openings formed in the first plate 24 and the second plate 25.

  The first body 21 disposed on the opposite side to the automatic transmission mechanism TM in the axial direction L with respect to the second body 22 and the third body 23 has an outer side in the axial direction L (on the opposite side to the automatic transmission mechanism TM). A raised portion 21 </ b> A that protrudes toward the surface is formed. A plurality (the same number as the engagement device CL; five in this example) of linear solenoid valves SL1 to SL5 are inserted into the raised portion 21A.

  The first linear solenoid valve SL1 adjusts, for example, a line pressure as a source pressure in accordance with a current applied to the solenoid unit, and generates a supply hydraulic pressure to the first clutch. The line pressure is generated by a regulator valve (not shown) constituted by, for example, a relief type pressure reducing valve. The second linear solenoid valve SL2 adjusts the line pressure as the original pressure to generate the hydraulic pressure supplied to the second clutch. The third linear solenoid valve SL3 adjusts the line pressure as the original pressure to generate the supply hydraulic pressure to the third clutch. The fourth linear solenoid valve SL4 adjusts the line pressure as the original pressure to generate the supply hydraulic pressure to the first brake. The fifth linear solenoid valve SL5 regulates the line pressure as the original pressure to generate the supply hydraulic pressure to the second brake. The plurality of linear solenoid valves SL1 to SL5 are arranged so as to be aligned along the vertical direction V while the positions in the axial direction L are slightly different. In the present embodiment, the linear solenoid valves SL1 to SL5 correspond to “pressure regulating valves”.

  As shown in FIG. 3, a main oil passage 30 that connects the oil pump OP and the linear solenoid valves SL <b> 1 to SL <b> 5 is formed inside the valve body 20. A plurality of linear solenoid valves SL1 to SL5 are connected to the main oil passage 30 in parallel with each other. Such a main oil passage 30 is formed so that the length from the oil pump OP to each of the linear solenoid valves SL1 to SL5 is the shortest or close to it (the volume is the minimum or close to it). It is common. On the other hand, the main oil passage 30 of the present embodiment is formed so as to pass a route different from the shortest route from the oil pump OP to each of the linear solenoid valves SL1 to SL5 or a route close thereto (see FIG. 10). ing.

  More specifically, the main oil passage 30 of the present embodiment temporarily supplies the oil supplied from the oil pump OP to the vertically lower side (downward in the vertical direction V) of the hydraulic control device 1 once to the linear solenoid valves SL1 to SL5. It is formed so as to pass vertically upward (upward in the vertical direction V). The main oil passage 30 has a lower passage portion 31, a first side passage portion 32, an upper passage portion 33, and a second side passage portion 38.

  The lower passage portion 31 is a portion passing through a position in the main oil passage 30 that is vertically lower than the linear solenoid valves SL1 to SL5. In the present embodiment, the lower passage portion 31 is disposed across the third body 23 and the second body 22. The lower passage portion 31 is disposed along a horizontal plane.

  The first side passage portion 32 is a first portion of the main oil passage 30 that is on the side of the linear solenoid valves SL1 to SL5 and passes through the same region in the vertical direction V as the linear solenoid valves SL1 to SL5. . The first side passage portion 32 is disposed inside the second body 22. The first side passage portion 32 is disposed in a state along the vertical plane.

  The upper passage portion 33 is a portion passing through a position in the main oil passage 30 that is vertically above the linear solenoid valves SL1 to SL5. The upper passage portion 33 is disposed across the second body 22 and the first body 21.

  The second side passage portion 38 is a second portion of the main oil passage 30 that is lateral to the linear solenoid valves SL1 to SL5 and passes through the same region in the vertical direction V as the linear solenoid valves SL1 to SL5. . The second side passage portion 38 is disposed inside the first body 21. The second side passage portion 38 is disposed in a state along the vertical plane. The second side passage portion 38 is disposed so that at least a part thereof passes through the same region in the vertical direction V as the first side passage portion 32.

  The oil supplied from the oil pump OP and regulated to the line pressure flows in the valve body 20 from the third body 23 toward the second body 22 through the lower passage portion 31 on the vertically lower side, In the second body 22, it flows vertically upward through the first side passage portion 32. The oil flows from the second body 22 toward the first body 21 through the upper passage portion 33 at a position vertically above the linear solenoid valves SL1 to SL5. It flows downwardly through the direction passage portion 38. Thereafter, the oil branches from the second side passage portion 38 at the vertical position V of each of the plurality of linear solenoid valves SL1 to SL5 and is supplied to the corresponding linear solenoid valves SL1 to SL5. The oil adjusted to a predetermined hydraulic pressure by each of the linear solenoid valves SL1 to SL5 is supplied to the hydraulic servo of the corresponding engagement device CL via the oil passage.

  Note that the main oil passage 30 of the present embodiment is different from the first side passage portion 32 in comparison with the shortest route from the oil pump OP to each of the linear solenoid valves SL1 to SL5 or a route close thereto (see FIG. 10). It can be said that the upper passage portion 33 is additionally provided.

  Further, as shown in FIG. 4, the upper passage portion 33 unique to the present embodiment is a rising oil passage that goes upward from the upstream side (oil pump OP side) toward the downstream side (linear solenoid valves SL1 to SL5 side). 34 and a descending oil passage 36 that goes downward from the upstream side toward the downstream side. In this example, the rising oil passage 34 is disposed so as to be directed vertically upward, and the descending oil passage 36 is disposed so as to be directed vertically downward. In the present embodiment, the upper passage portion 33 further includes a connection oil passage 35 that connects the ascending oil passage 34 and the descending oil passage 36. In this example, the connection oil passage 35 is arranged in a state along the horizontal plane.

  By the way, while the oil pump OP is stopped or while the hydraulic pressure supply from each linear solenoid valve SL1 to SL5 to the corresponding engagement device CL is stopped, the oil pump OP and the linear solenoid valves SL1 to SL5 Air may enter the hydraulic circuit from a portion communicating with the atmosphere. If air is mixed in the hydraulic circuit, the rise of the hydraulic pressure in the hydraulic circuit becomes unstable the next time the engaging device CL is engaged, and the responsiveness of the engagement control of the engaging device CL may be reduced. Concerned.

  Therefore, the hydraulic control device 1 of the present embodiment includes a sub oil passage 40 that branches from the main oil passage 30 on the upstream side of the linear solenoid valves SL1 to SL5. The sub oil passage 40 is an oil passage (air venting) that allows air that may remain in the hydraulic circuit to escape to other parts in the transmission 100 without being directed to the linear solenoid valves SL1 to SL5. Air relief oil passage). The flow rate of the oil flowing through the sub oil passage 40 is larger than the flow rate of the oil flowing downstream from the branch portion B with the sub oil passage 40 in the main oil passage 30. In the present embodiment, the sub oil passage 40 is connected to a non-servo system oil passage. The “non-servo system oil passage” is an oil passage other than the oil passage connected to the hydraulic servo provided in the transmission 100. If the connection destination of the sub oil passage 40 is a non-servo system oil passage, even if air is mixed in the hydraulic circuit, the mixed air will not reach the hydraulic servo. There is no impact.

  The non-servo system oil path to which the sub oil path 40 is connected may be, for example, an oil path connected to a lubrication target portion in the transmission 100. In the transmission 100, there are many meshing portions of gears for transmitting driving force, bearings for rotatably supporting various rotating members, and the like. In order to ensure a smooth rotational drive and prevent wear, it is necessary to originally supply oil to the meshing portions of the gears and the bearings to lubricate them. In addition, a large amount of air in the transmission 100 originally remains around these. Therefore, lubricate the lubrication target part appropriately by supplying oil through the sub oil path 40 and the non-servo system oil path to the lubrication target part that is hardly affected even if air is mixed. Can do.

  The non-servo system oil path to which the sub oil path 40 is connected may be, for example, an oil path connected to a portion to be cooled in the transmission 100. The engagement device CL transmits the driving force via the friction plates that are in pressure contact with each other. For example, the engagement device CL may transmit the driving force in a state where the respective friction plates are in sliding contact (slip). In such a slip engagement state of the engagement device CL, the friction plate generates heat due to the dynamic friction force. In order to avoid deterioration due to overheating, it is originally necessary to supply oil to the friction plate of the engagement device CL to cool the friction plate. In addition, there are many cases where a large amount of air in the transmission 100 originally remains around the friction plate. Therefore, supply the oil through the sub oil passage 40 and the non-servo system oil passage to the portion to be cooled that is hardly affected even if air is mixed, and appropriately cool the portion to be cooled. Can do.

  The non-servo system oil path to which the sub oil path 40 is connected is an oil path connected to the torus portion TR of the fluid coupling TC when the transmission 100 includes the fluid coupling TC as in the present embodiment. There may be. In a state where the pump impeller and the turbine runner of the fluid coupling TC are stopped, there is a case where a small amount of oil and a large amount of air remain inside the torus portion TR. When the pump impeller and the turbine runner rotate from this state, the amount of oil increases while air escapes inside the torus portion TR, and power is transmitted via the oil. Thus, in the torus part TR of the fluid coupling TC, air can originally increase or decrease inside the torus part TR. Therefore, oil is supplied to the torus part TR which is hardly affected even if air is mixed through the sub oil passage 40 and the non-servo system oil passage, and the power via the oil in the fluid coupling TC is supplied. Communication can be performed appropriately.

  In the present embodiment, as shown in FIG. 4, the sub oil passage 40 branches from the main oil passage 30 in the upper passage portion 33 among the upstream portions of the linear solenoid valves SL1 to SL5. In other words, the branch portion B between the main oil passage 30 and the sub oil passage 40 is provided in the upper passage portion 33. More specifically, a branch portion B between the main oil passage 30 and the sub oil passage 40 is provided in the connection oil passage 35 in the upper passage portion 33. Further, in the present embodiment, a branch portion B between the main oil passage 30 and the sub oil passage 40 is provided at a most upstream side portion of the connection oil passage 35 (a boundary portion between the connection oil passage 35 and the rising oil passage 34). Yes. 4 shows an example in which the sub oil passage 40 is connected to the torus portion TR. However, as described above, the sub oil passage 40 is connected to the lubrication target portion or the cooling target portion in the transmission 100. Also good.

  As described above, even if air is mixed into the hydraulic circuit by branching the main oil passage 30 from the connection oil passage 35 of the upper passage portion 33 on the upstream side of the linear solenoid valves SL1 to SL5. The mixed air can be easily guided to the sub oil passage 40 while being captured by the upper passage portion 33. Therefore, it is possible to effectively avoid the air from reaching the linear solenoid valves SL1 to SL5 disposed downstream of the upper passage portion 33 and below the vertical direction V. Thereby, the rise of the hydraulic pressure in the hydraulic circuit can be stabilized, and the responsiveness of the engagement control of the engagement device CL can be maintained high. At that time, since the atmospheric air is not drained, the responsiveness of the engagement control of the engagement device CL can be maintained high without increasing the load of the oil pump OP.

  According to the verification experiment, for example, when the air is vented by the atmospheric drain (see FIG. 10), it is confirmed that the discharge amount of the oil pump OP for securing the necessary oil amount increases by about 20%. . Such an increase in the discharge amount of the oil pump OP is not preferable because it leads to a decrease in the fuel consumption rate of the vehicle. On the other hand, when air bleeding is performed using the sub oil passage 40 communicating with a predetermined portion inside the transmission 100 as in the present embodiment, an increase in the load of the oil pump OP is hardly confirmed. It was. Therefore, by using the hydraulic control device 1 of the present embodiment, the responsiveness of the engagement control of the engagement device CL can be maintained high while maintaining the fuel consumption rate of the vehicle.

[Other Embodiments]
(1) In the above-described embodiment, the configuration in which the branch portion B between the main oil passage 30 and the sub oil passage 40 is provided at the most upstream portion of the connection oil passage 35 has been described as an example. However, without being limited to such a configuration, for example, as shown in FIG. 5, a branch portion B between the main oil passage 30 and the sub oil passage 40 may be provided at the center of the connection oil passage 35. In this case, for example, as shown in FIG. 6, the connection oil passage 35 is provided with an air reservoir portion 37 having a shape that is recessed vertically upward. The branch part B may be provided.

(2) In the above-described embodiment, the configuration in which the branch portion B between the main oil passage 30 and the sub oil passage 40 is provided in the connection oil passage 35 has been described as an example. However, the present invention is not limited to such a configuration. For example, as shown in FIG. May be provided. In addition, as shown to this figure, the raising oil path 34 may be formed so that it may go diagonally upward toward the downstream from the upstream. Similarly, the descending oil passage 36 may be formed so as to go obliquely downward from the upstream side toward the downstream side.

(3) In the above embodiment, the configuration in which the branch portion B between the main oil passage 30 and the sub oil passage 40 is provided between the ascending oil passage 34 and the descending oil passage 36 has been described as an example. However, without being limited to such a configuration, for example, as shown in FIG. 8, a branch portion B between the main oil passage 30 and the sub oil passage 40 may be provided in the rising oil passage 34. Or although illustration is abbreviate | omitted, the branch part B of the main oil path 30 and the sub oil path 40 may be provided in the descending oil path 36.

(4) In the above embodiment, the configuration in which the branch portion B between the main oil passage 30 and the sub oil passage 40 is provided in the upper passage portion 33 has been described as an example. However, without being limited to such a configuration, for example, as shown in FIG. 9, a branch portion B between the main oil passage 30 and the sub oil passage 40 may be provided in the first side passage portion 32. Or although illustration is abbreviate | omitted, the branch part B of the main oil path 30 and the sub oil path 40 may be provided in the downward passage part 31. FIG.

(5) In the above embodiment, the configuration in which the hydraulic control device 1 controls the hydraulic pressure supplied to the shift engagement device CL provided in the automatic transmission mechanism TM has been described as an example. However, without being limited to such a configuration, for example, when the transmission 100 includes a lockup clutch, the hydraulic control device 1 controls the hydraulic pressure supplied to the lockup clutch. May be. In this case, the hydraulic control device 1 may be provided with a lockup linear solenoid valve that adjusts the hydraulic pressure supplied to the lockup clutch as a “pressure regulating valve”. The sub oil passage 40 for releasing air is provided so as to branch from the main oil passage 30 upstream of the lockup linear solenoid valve.

(6) In the above embodiment, the configuration in which the line pressure is supplied as the original pressure to the linear solenoid valves SL1 to SL5 has been described as an example. However, without being limited to such a configuration, for example, a modulator pressure lower than the line pressure may be supplied as a source pressure to the linear solenoid valves SL1 to SL5. In this case, the hydraulic control device 1 may be provided with a modulator valve formed of, for example, a relief type pressure reducing valve on the downstream side of the regulator valve that generates the line pressure.

(7) The configurations disclosed in each of the above-described embodiments (including the above-described embodiments and other embodiments; the same applies hereinafter) are applied in combination with the configurations disclosed in the other embodiments unless a contradiction arises. It is also possible to do. Regarding other configurations as well, the embodiments disclosed in the present specification are examples in all respects, and can be appropriately modified without departing from the gist of the present disclosure.

[Outline of Embodiment]
In summary, the hydraulic control device according to the present disclosure preferably includes the following configurations.

A hydraulic control device (1) for controlling hydraulic pressure supplied to a hydraulically driven engagement device (CL) provided in a transmission (100) for a vehicle,
The main oil passage (30) connecting the oil pump (OP) and the pressure regulating valves (SL1 to SL5) for adjusting the hydraulic pressure supplied to the engagement device (CL) is more than the pressure regulating valves (SL1 to SL5). While having an upper passage portion (33) passing through a position that is vertically above,
A sub oil passage (40) branched from the main oil passage (30) is provided upstream of the pressure regulating valves (SL1 to SL5).

  According to this configuration, since the sub oil passage (40) is provided on the upstream side (oil pump (OP) side) of the pressure regulating valves (SL1 to SL5), even if air is mixed into the hydraulic circuit, The mixed air is guided to the sub oil passage (40), and air can be prevented from reaching the pressure regulating valves (SL1 to SL5) arranged on the downstream side of the sub oil passage (40). Further, since the main oil passage (30) provided on the upstream side of the pressure regulating valves (SL1 to SL5) has the upper passage portion (33), the mixed air cannot be sufficiently led to the sub oil passage (40). However, the remaining mixed air can be captured by the upper passage portion (33). With these double air traps, it is possible to effectively avoid the air from reaching the pressure regulating valves (SL1 to SL5) disposed downstream and vertically below the upper passage portion (33). Therefore, the rising of the hydraulic pressure in the hydraulic circuit can be stabilized, and the responsiveness of the engagement control of the engagement device (CL) can be kept high. At that time, since atmospheric draining is not performed, the responsiveness of the engagement control of the engagement device (CL) can be maintained high without increasing the load of the oil pump (OP).

As one aspect,
It is preferable that a branch portion (B) between the main oil passage (30) and the sub oil passage (40) is provided in the upper passage portion (33).

  According to this configuration, if air is mixed in the hydraulic circuit, the mixed air is easily captured by the upper passage portion (33) and the captured mixed air is easily passed to the sub oil passage (40). Can lead. Therefore, the air mixed in the hydraulic circuit can be effectively avoided from reaching the pressure regulating valves (SL1 to SL5), and the responsiveness of the engagement control of the engagement device (CL) can be kept high. it can.

As one aspect,
The upper passage portion (33) has an upward oil passage (34) directed upward and a downward oil passage (36) directed downward from the upstream side toward the downstream side,
The said branch part (B) is provided in the connection part (35A) or connection oil path (35) which connects the said rising oil path (34) and the said falling oil path (36) in the said upper passage part (33). It is preferable.

  According to this configuration, it is possible to more effectively avoid the air mixed in the hydraulic circuit from reaching the pressure regulating valves (SL1 to SL5), and the responsiveness of the engagement control of the engagement device (CL). Can be kept high.

As one aspect,
It is preferable that the sub oil passage (40) is connected to a non-servo system oil passage which is an oil passage other than an oil passage connected to a hydraulic servo provided in the transmission (100).

  According to this configuration, the air guided from the main oil passage (30) to the sub oil passage (40) without going to the pressure regulating valves (SL1 to SL5) passes through the non-servo system oil passage, and the transmission Supplied to elements other than the hydraulic servo in (100). If it is an element other than the hydraulic servo, even if air from the sub oil passage (40) is mixed, the air is mixed into the hydraulic servo of the pressure regulating valve (SL1 to SL5) or the corresponding engagement device (CL). Unlike the case, the control responsiveness is hardly affected. Therefore, the responsiveness of the engagement control of the engagement device (CL) can be maintained high without affecting other elements other than the engagement device (CL) provided in the transmission (100).

As one aspect,
When the non-servo system oil passage is connected to a lubrication target site or a cooling target site in the transmission (100), or the transmission (100) includes a fluid coupling (TC). It is preferable that it is an oil path connected to the torus part (TR) of the fluid coupling (TC).

  According to this configuration, the lubrication target portion in the transmission (100) is appropriately lubricated or the cooling target in the transmission (100) is hardly affected by the air contamination from the sub oil passage (40). The site can be properly cooled. Alternatively, the power transmission via the oil in the fluid coupling (TC) can be appropriately performed without being substantially affected by the mixing of air from the sub oil passage (40).

  The hydraulic control device according to the present disclosure only needs to exhibit at least one of the effects described above.

DESCRIPTION OF SYMBOLS 1 Hydraulic control apparatus 30 Main oil path 33 Upper passage part 34 Ascending oil path 35 Connection oil path 35A Connection part 36 Lowering oil path 40 Sub oil path 100 Transmission device TC Fluid coupling TR Torus part OP Oil pump CL Engaging device SL1 1st Linear solenoid valve (pressure regulator)
SL2 Second linear solenoid valve (pressure regulating valve)
SL3 Third linear solenoid valve (pressure regulating valve)
SL4 Fourth linear solenoid valve (pressure regulating valve)
SL5 Fifth linear solenoid valve (pressure regulating valve)
B branch

Claims (7)

A hydraulic control device for controlling hydraulic pressure supplied to a plurality of hydraulically driven engagement devices provided in a transmission for a vehicle,
The valve body is provided with a plurality of pressure regulating valves that individually adjust the hydraulic pressure supplied to the plurality of engaging devices, and the plurality of pressure regulating valves are arranged along the vertical direction,
An oil supply unit from an oil pump is provided on the lower side of the valve body,
The main oil passage which connects the feed portion and a plurality of said pressure regulating valve comprises first reaches the vertical above the all of the pressure regulating valve by increasing the same vertical direction of a region with a plurality of said regulating valve from said supply unit One side passage portion, an upper passage portion passing through a position vertically above all the pressure regulating valves continuously from the first side passage portion, and the same vertical direction as the plurality of pressure regulating valves from the upper passage portion And a second side passage portion that descends the region and reaches each of the plurality of pressure regulating valves ,
A hydraulic control apparatus comprising a sub oil passage that branches from the main oil passage at the upper passage portion . The upper passage part has an upward oil passage that goes upward and a downward oil passage that goes downward from the upstream side toward the downstream side,
The branch portion of the main oil passage and the sub oil passage, according to claim 1 provided in the connection or connecting oil passage for connecting the descending fluid path and the rising oil passage in said upper passage portion hydraulic Control device. The upper passage part has an upward oil passage that goes upward and a downward oil passage that goes downward from the upstream side toward the downstream side,
The hydraulic control device according to claim 1, wherein a branch portion between the main oil passage and the sub oil passage is provided in the rising oil passage. The valve body includes a first body and a second body joined together in a horizontal direction,
The first lateral passage portion is disposed inside the second body;
The upper passage portion is disposed across the second body and the first body;
The hydraulic control device according to any one of claims 1 to 3, wherein the second side passage portion is disposed inside the first body. The flow rate of the oil which flows through the said sub oil path is set so that it may become larger than the flow volume of the oil which flows downstream from the branch part with the said sub oil path in the said main oil path. The hydraulic control device according to claim 1. The sub oil passage, according to any one of the transmission from claim 1, which is connected to the non-servo system oil passage is an oil passage other than the oil path connected to the hydraulic servo is provided on the 5 Hydraulic control device. The non-servo system oil passage is connected to an oil passage connected to a lubrication target site or a cooling target site in the transmission, or to a torus portion of the fluid coupling when the transmission has a fluid coupling. The hydraulic control device according to claim 6 , wherein the hydraulic control device is an oil passage.

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